201109132 四、指定代表圖： (一） 本案指定代表圖為：第（2)圖。 (二） 本代表圖之元件符號簡單說明： 5- -驅動器； 6〜 活塞； 6a 〜活塞本體； 6b〜驅動器夾具； 16 〜活塞環； 17- -環狀溝； 18 〜嵌合溝； 19〜插銷孔； 20 〜嵌合部； 21- “固定插銷； 22- 〜插銷安裝孔； 23、 -凸緣部； 24' 〜墊圈（調整部）； 0〜 中心線。 五、本案若有化學式時，請揭示最能顯示發明特徵的化風 無。 六、發明說明： 【發明所屬之技術領域】 本發明是關於一種在敲釘機中被打入驅動之活塞和與 此活塞結合為一體之敲釘用驅動器的安裝構造。 【先前技術】 在一般用來打入暗釘（終飾釘）及釘書釘之敲釘機中， 配合打入這些釘子時所導引之射出口形狀，設置板狀之驅 動器。另一方面，為了與活塞結合’在驅動器上形成公螺 絲，在活塞上形成母螺絲，將這些以螺絲結合起來的構造 201109132 =般=見之構造。此結合構造在強度方面也有报高的可 *…、'而，為了採用此結合構造，需要將公螺絲外徑之 ==削成板狀’藉此，製造出板狀之驅動器。如此，為了 “反狀之驅動器’就必須花費加工時間、材料成本及加 工成本等。 、因此’專利文獻1揭示一種構造，其在活塞上形成嵌合 溝在此嵌合溝上，整體敌合至板狀之驅動器之上端部， 使插銷貫通設於活塞與驅動器上之插銷孔，藉由插銷接合 活塞與驅動器。 此外，在敲釘機中，當活塞受到驅動時，活塞碰撞到 汽缸下部之緩衝器’相對於此，驅動器上有慣性力作用。 因此’在專利文獻1之插銷結合構造中，插銷與插銷孔之結 合部上有應力集中。特別是’插銷孔部之強度並不充分： 所以’驅動器、活塞等之更換頻率提高。因此，專利文獻i 之插銷結合構造過去主要使用於小型之敲釘機。 作為用來減低應力的其中一個對策，可加大插銷孔部 J面積不過’為了加大插銷孔之面積，驅動器夾具也 、、/頁加大因此’加大插銷孔之面積這個方法因為活塞和 緩衝器的關係，有其限制…驅動器之下部之厚度由針 子來決定’所以，僅增厚驅動器上部來提高強度的方法終 究會增加製造成本。 、 [先前技術文獻] [專利文獻] [專利文獻1]曰本特開平9_1 09056號公報 201109132 【發明内容】 種敲釘機，其可減 力’提而驅動器與 本發明一個以上之實施例在提供— 低慣性力所產生之驅動器插銷孔部的應 活塞之間的結合強度，並且壓低成本。 根據本發明-個以上之實施例，—種敲釘機包括以自 由滑動之方式配置於汽缸4内的活塞6、與設置於活塞6之驅 動器夾具6b結合的板狀之驅動器5、貫通形成於上述驅動器 5之上部的插銷安裝孔22、突出形成於插銷安|孔22之周緣 部位的凸緣部23、孔形成於上述驅動器失具此且受上述 驅動器5嵌合的嵌合溝18、以橫跨之姿態形成於上述驅動器 夾具6b上的插銷孔19及為連接上述插銷孔19與上述插銷安 裝孔22而被插通且將驅動器5結合至上述驅動器夾具讣上 的固定插鎖21。 根據此構造，當為打入釘子而驅動活塞時，活塞與汽 缸下部之緩衝器碰撞，_於此，驅動器有慣性力作用: 上，所以，在作為固定插銷與驅動器之結合部的驅動器之 插銷安裝孔上’應力集中，但插銷安裝孔在凸緣部受到增 5金。於是，可使插銷安裝孔之應力減低，$高驅動器^ 塞之間的結合強度。 此外，上述構造之敲釘機可進一步包括調整部（24，μ 29)，其設置於上述驅動器夾具6b之嵌合溝18與上述驅動器 5之間，埋入上述嵌合溝18之内面與上述驅動器之凸緣部u 那側之表面之間的間隙。 4 201109132 根據此構造，在上述驅動器夾具之嵌合溝與上述驅動 器之間，設有調整部，其埋入上述嵌合溝之内面與上述驅 動器之凸緣部那側之表面之間的間隙，所以，活塞6與驅動 器5之接觸面得以充分確保，可穩定驅動器5之安裝狀態。 此外’上述調整部24，28可嵌合至上述凸緣部23。 根據此構造’上述調整部嵌合至凸緣部，所以，凸緣 部受到調整部増強，可進一步提高驅動器與活塞之間的結 合強度。於是，施加於插銷安裝孔之應力可藉由調整部所 增強之ib緣部得到進一步的減低。 此外，上述活塞6可由具有大徑之活塞本體6&與設置於 其下部且具有小徑之驅動器夾具6b所構成。 此外，上述活塞6可由環狀之活塞本體6a與螺合至活塞 本體6a之内側的圓柱狀驅動器夾具6b所構成。 此外，上述凸緣部23可突出形成於上述驅動器5之其中 一側面。或者，上述凸緣部23可突出形成於上述驅動器$ 之兩側面。 根據此構造， 器之間的結合強度 可根據敲釘機之用途來選擇活塞與驅動 其他特徵及效果可冑由實施例< t己載及附加之申請專 利範圍來得到理解。 ％ 【實施方式】 第1圖為本發明之典型實施例之氣壓式敲釘機的垂直 剖面圖。本發明之敲釘機用來打入暗釘、釘書釘等。符號i 201109132 代表本體，2代表抓取部，3代表儲存送料裝置。在本體丄 之内部，配置有汽缸4、在汽缸4内以自由滑動之方式收納 於其中且與驅動器5結合為一體的活塞6、在汽缸4内供給排 出空氣室7(與壓縮空氣供給源連接）内之壓縮空氣以驅動 控制活塞6的頂置閥8及控制頂置閥8之作動的觸發閥9。在 本體1之先端，設有鼻部10，上述驅動器5以滑動方式導引 鼻部1 〇。在鼻部1 〇上，儲存送料裝置3之先端產生開口，儲 存送料裝置3内之釘子（未圖示）為預備供給至鼻部1〇的構 造。又，觸發閥9配置於抓取部2之基部，觸發閥9之閥桿j i 之先端與觸發槓桿12相向配置。 在上述敲釘機之非作動期間，觸發閥9連接至空氣室 7。從空氣室7取入之壓縮空氣透過未圖示之空氣流道，供 給至頂置閥8。藉此，頂置閥8如第丨圖所示，關閉汽缸4之 上端。备進行打入動作時，若操作觸發槓桿丨2以壓入觸發 閥9之閥柃11，觸發閥9會開始作動，使頂置閥8連接至大 氣。另外，汽缸4之上端開啟（未圖示），空氣室7内之壓縮 空虱瞬間供給至汽缸4内。結果，驅動器5伴隨活塞6受到驅 動，鼻部10内之釘子被打擊且被打入被打入材料内。之後， 若釋放觸發槓桿12，再度地，觸發閥9如第1圖所示，將頂 置閥8連接至空氣室7。汽缸4對空氣室7關閉，同時，汽缸4 連接至大氣而進行排氣n，活塞6恢復至初始位置為 下一次之打入釘子的動作作準備。此外，上述觸發閥9、頂 置間8之作動所產生的敲釘機之打入控制機構和一般習知 的相同。 201109132 然而，如第2(a)圖及第2(b)圖所示，上述活塞6由具有 大徑之活塞本體6a與其下部之具有小徑之驅動器夾具叻一 體成形。活塞本體6a形成圓柱狀，在其外周面，圍繞設置 著用來嵌合活塞環16的環狀溝π。驅動器夾具讥形成圓柱 狀，在其中央部位，形成下方具有開口且為狹縫狀的嵌合 溝18。又，在驅動器夾具6b上，以與活塞6之中心線〇垂直 且橫跨嵌合溝18之姿態，形成插銷孔丨9。 另外，驅動器5形成板狀，嵌合至驅動器夾具6b之嵌合 溝18並產生固定作用。 如第3(a)圖及第3(b)圖所示，在上述驅動器5之上部， 形成方形板狀之嵌合部20。嵌合部20之大小形成得與活塞6 之飲合溝1 8約略相同。又，在嵌合部2 〇上，形成用來插通 固定插銷21的插銷安裝孔2 2。在此插銷安裝孔2 2之周緣部 位，環狀之凸緣部2 3突出形成肋狀。凸緣部2 3可藉由毛邊 加工來形成。又’在驅動器5之上部之凸緣部23那側的面， 重合設置有金屬製之墊圈24，作為埋入嵌合溝18之内面與 驅動器5之凸緣部2 3那側之表面之間之間隙的調整部。 墊圈24形成與驅動器5之嵌合部2〇約略相同的大小，並 且’形成與上述凸緣部23嵌合之嵌合孔25。此外，墊圈24 之厚度形成得大於凸緣部23之高度。 接著’當結合活塞6與驅動器5時，使驅動器5與墊圈24 重合（也可不重合），嵌合至活塞6之驅動器夾具此之嵌合溝 18。此時，插銷孔19與驅動器5之插銷安裝孔2 2整合在一 起’所以’固定插銷21從插銷孔19之其中一邊插通，從驅 201109132 動器5之插銷安裝孔22貫通至插銷孔19之另r邊，再者，藉 由緊固固定插銷21之端部，或者，藉由壓接固定插銷以與 插銷孔19，不拔出也可以。藉此，驅動器夾具扑與驅動器5 以如第2(a)圖及第2(b)圖所示之方式結合。 根據上述活塞6與驅動器5之安裝構造，當為打入釘子 而驅動活塞6時，活塞6碰撞到汽缸下部之緩衝器26，相對 於此，驅動器5上有慣性力作用，所以，固定插銷21與驅動 器5之間的結合部上有應力集中。上述結合部為驅動器5之 插銷安裝孔22與其周緣部位之凸緣部23，但可藉由凸緣部 23提高驅動器與活塞之間的結合強度。此外，墊圈與凸 緣部23為嵌合狀態，藉此，墊圈24與驅動器5一體化，埋入 嵌合溝18之内面與驅動器5之凸緣部23那側之表面之間的 間隙’所以，驅動器5之安裝狀態很穩定。 如此，應力集中會產生之地方為插銷安裝孔22之邊緣 (周緣部位）’為了防止慣性力在孔之邊緣產生微小變形， 在驅動器5之插銷安裝孔22之周緣部位形成凸緣部“，藉 此使其具有之剛性產生效果。又，驅動器5使墊圈24與凸 緣部23嵌合’藉此’嵌合至活塞6之嵌合溝以，所以，活塞 6與一驅動器5之間的接觸面得以充分確#，可穩定驅動器5 t裝狀釔並且，其厚度形成得大於凸緣部23之高度， 於是凸緣部23不與嵌合溝之18之内面接觸，所以，可對作 為驅動器5之插銷安裝孔22之邊緣的周緣部位賦予充分之 剛性。 又’在塾圈24上，形成與驅動器5之凸緣部_合之嵌 8 201109132 合孔25 ’所以’藉由嵌合’確實進行定位，可抑制組合至 活塞6時所發出的聲響。 此外’塾圈24若為嵌合至嵌合溝18的大小，其厚度如 第4(a)圖所示’可和凸緣部23之高度約略相同。塾圈24與 凸緣部23可分別形成之後，使凸緣部23與嵌合孔25嵌合在 一起’再嵌合至嵌合溝18’亦可藉由壓毛邊加工，在形成 凸緣部23時’將墊圈24插入模具中再加工。當採用後者時， 沿著墊圈24之嵌合孔25之内面形成凸緣部23，墊圈24與驅 動器5進行命強度之壓接，結合在一起。 又，凸緣部23不限定為突出形成於驅動器5之嵌合部2〇 之單側的型態。如第4(b)圖所示，可藉由鍛造形成於嵌合 部20之兩側。在此情況下，墊圏24也配置於嵌合部別之兩 側。如此，凸緣部23可根據敲釘機之用途突出形成於驅動 器5之其中一側面或兩個側面。 再者，驅動器之插銷安裝孔不限於採用正圓形，亦可 為橢圓、長孔狀或多角形狀。 又，活塞本體6a與驅動器夾具6b不一定要形成一體。 亦可為結合兩個分體的構造。 凸緣部23可不為環狀。其亦可僅形成於會在打入時產 =應力之插銷安裝孔之上部。又，凸緣部23亦可與驅動器5 刀别構成。例如，如第5圖所示，可使由外徑較小之嵌合部 26與較大之凸緣部23所組成的筒狀凸緣元件u藉由摩擦熔 接等技術與驅動器5結合為一體。 匕外驅動器夾具6b也不限於圓柱狀，亦可為橢圓型、 201109132 多角形狀等。 又，在驅動器夾具上之上述驅動器5之凸緣部23之周 圍，設有墊圈24，作為用來保持並安裝活塞6之嵌合溝 之内面與驅動器5之間隔的調整部，但調整部可形成和驅動 器夾具6b分開的元件，例如，如第6(a)圖及第6(b)圖所示’ 亦可在驅動器夾具6b上，以設置於驅動器5之凸緣部23之周 圍的狀態，固定中間元件28。 不過，若凸緣部23在插銷安裝孔22之邊緣確保了充分 之剛性，就不需要墊圈24、中間元件28這種兼具增強功能 的調整部。在此情況下，如第7(a)圖及第7(b)圖所示，可 在凸緣部23之周圍，形成僅僅用來保持並安裝與活塞6之嵌 合溝1 8之内面之間之間隔的凸部2 9。 再者，驅動器夾具之構造不限定為上述之型態。例如， 亦可如第8(a)圖所示，活塞本體6&之下部有同徑之驅動器 夾具6b與其形成為一體，在此驅動器夾具吒上，形成具有 開口之嵌合溝18，並且，在上述驅動器5之上部，形成插銷 安裝孔22，在此插銷安裝孔22之周緣部位，突出形成肋狀 之凸緣部23，在上述驅動器5之凸緣部23那側，設有包括了 與該凸緣部23嵌合之嵌合孔25的墊圈24，且，使驅動器5 與墊圈24嵌合至活塞6之嵌合溝丨8，藉由連續插通以橫跨上 述活塞6之姿態而形成的插銷孔丨9與驅動器5之插銷安裝孔 22的固定插銷21來產生結合。 第8(b)圖為另一型態之驅動器夾具的垂直剖面圖，在 活塞6之内部形成驅動器夾具，活塞6由環狀之活塞本體6a 10 201109132 與螺合至其内側之圓柱狀驅動器夾具6b構成，在此驅動器 夾具6b之中央下部’形成具有開口之嵌合溝1 8，並且，使 驅動器5與墊圈24嵌合至活塞6之嵌合溝18，藉由連續插通 以橫跨驅動器夾具6b之姿態而形成的插銷孔1 9與驅動器5 之插銷安裝孔22的固定插銷21來產生結合。 根據上述構造’固定插銷21面對活塞本體6 a之内周面 而無法拔出，所以，不需要設置具有緊固作用等的卡止裝 置。 在第8(a)圖及第8(b)圖之情況下，亦可得到與第i圖至 第4(b)圖所示之型態相同的作用效果，並且，墊圈24、凸 緣部23之形狀及驅動器5之插銷安裝孔22等不受圖示限定 的意義和第1圖至第4(b)之情況相同。 【產業上可利性】 本發明可應用力敲钉冑中之驅動器與活塞的結 造。 。σ 【圖式簡單說明】 第1圖為本發明之典型實施例之氣壓式敲釘機的垂直 剖面側面圖。 第2 (a )圖為結合驅動φ ^ m心 動益後之活塞的正面圖。第2(b)圖 為>。者A-A線切開第2(a)圖的剖面圖。 第3(a)圖為驅動 "線切門第二 圖。第3(b)圖為沿著 Y Y綠切開第3(a)圖的剖面圖。 11 201109132 第4(a)圖及第4(b)圖為分別表示驅動器與活塞之其他 結合狀態的剖面圖。 第5圖為表示凸緣部之其他實施型態的剖面圖。 第6(a)圖為表示調整部之其他實施型態的正面圖。第 6(b)圖為沿著C-C線切開第6(a)圖 第7(a)圖為表示調整部之另 7(b)圖為沿著D-D線切開第7(a)圖 第8(a)圖及第8(b)圖為分別 直剖面圖。 的剖面圖。 —實施型態的正面圖。第 的剖面圖。 表示活塞之其他型態的垂 【主要元件符號說明】 1〜 本體； 2〜 抓取部； 3〜 儲存送料裝置； 4 汽紅； 5〜 驅動器； 6〜 活塞； 6a〜活塞本體； 6b' 〜驅動器夾具 7〜 空氣室； 頂置閥； 〇 9〜 觸發閥； 10' 〜鼻部； 11' 〜閥桿； 12' 〜觸發槓桿； 16' -活塞環； 17' 〜環狀溝； 18, ^嵌合溝； 19' 〜插銷孔； 2(l· ^谈合部； 21' 〜固定插銷； 22' 〜插銷安裝孔； 23' 〜凸緣部； 24' 〜墊圈（調整部）； 25' 〜嵌合孔； 26' -嵌合部； 27' 〜凸緣元件； 12 201109132 28〜中間元件（調整部）；29〜凸部（調整部 13201109132 IV. Designated representative map: (1) The representative representative of the case is: (2). (2) A brief description of the component symbols of this representative diagram: 5--driver; 6~ piston; 6a~piston body; 6b~driver clamp; 16~piston ring; 17--annular groove; 18~fitting groove; ~ Pin hole; 20 ~ fitting part; 21- "fixed pin; 22- ~ pin mounting hole; 23, - flange part; 24' ~ washer (adjustment part); 0~ center line. 5. If there is a chemical formula In the case of the invention, the present invention relates to a piston that is driven into a nailing machine and integrated with the piston. The mounting structure of the driver for the nailing. [Prior Art] In the nailing machine generally used for inserting the studs (finish studs) and staples, the shape of the ejection opening guided by the driving of the nails is set. Plate-shaped drive. On the other hand, in order to combine with the piston, a male screw is formed on the drive, a female screw is formed on the piston, and the structure is assembled by screws. The construction is in the form of a screw. This combination is constructed in terms of strength. In addition, in order to adopt this combination structure, it is necessary to cut the outer diameter of the male screw == into a plate shape, thereby manufacturing a plate-shaped actuator. Thus, in order to "reverse drive" It takes time, processing costs, processing costs, etc. Therefore, Patent Document 1 discloses a structure in which a fitting groove is formed in a piston on the fitting groove, and the upper end is integrally coupled to the upper end portion of the plate-shaped driver, so that the pin passes through the pin hole provided in the piston and the driver. The piston and the actuator are engaged by a pin. Further, in the nailer, when the piston is driven, the piston collides with the damper of the lower portion of the cylinder. In contrast, the actuator has an inertial force. Therefore, in the plug coupling structure of Patent Document 1, stress is concentrated on the joint portion between the plug and the pin hole. In particular, the strength of the pin hole portion is not sufficient: Therefore, the frequency of replacement of the actuator, the piston, and the like is increased. Therefore, the pin coupling structure of Patent Document i has been mainly used in a small nailing machine in the past. As one of the countermeasures for reducing the stress, the area of the pin hole portion J can be increased. However, in order to increase the area of the pin hole, the driver jig is also enlarged, and the / page is enlarged. Therefore, the method of increasing the area of the pin hole is because the piston and the The relationship of the damper has its limitations... The thickness of the lower part of the driver is determined by the needle. Therefore, only thickening the upper part of the driver to increase the strength will eventually increase the manufacturing cost. [Prior Art Document] [Patent Document 1] [Patent Document 1] Japanese Patent Laid-Open Publication No. Hei 9-9 09056 No. 201109132 [Claim of the Invention] A nailing machine capable of reducing the force of the driver and one or more embodiments of the present invention Provided - the strength of the bond between the pistons of the driver pin holes generated by the low inertia force, and low pressure. According to one or more embodiments of the present invention, the nailer includes a piston 6 that is slidably disposed in the cylinder 4, and a plate-shaped actuator 5 that is coupled to the driver clamp 6b provided in the piston 6, and is formed through a latch mounting hole 22 at an upper portion of the driver 5, a flange portion 23 projecting from a peripheral portion of the latch body|hole 22, and a hole formed in the fitting groove 18 in which the driver is disengaged and fitted by the driver 5, A pin hole 19 formed in the above-described driver jig 6b and a fixed latch 21 that is inserted into the pin hole 19 and the pin mounting hole 22 and that couples the driver 5 to the driver jig. According to this configuration, when the piston is driven to drive the nail, the piston collides with the damper at the lower portion of the cylinder, and the driver has an inertial force: upper, so, the latch of the driver as a joint of the fixed pin and the driver The stress on the mounting hole is concentrated, but the pin mounting hole is increased by 5 gold in the flange portion. Thus, the stress in the pin mounting hole can be reduced, and the bonding strength between the high driver plugs can be made. Further, the nailer of the above configuration may further include an adjusting portion (24, μ 29) provided between the fitting groove 18 of the driver jig 6b and the driver 5, embedded in the inner surface of the fitting groove 18, and the above The gap between the surfaces of the flange portion u of the driver. According to this configuration, an adjustment portion is provided between the fitting groove of the driver jig and the driver, and the gap between the inner surface of the fitting groove and the surface of the flange portion of the driver is buried. Therefore, the contact surface of the piston 6 and the driver 5 is sufficiently ensured, and the mounting state of the driver 5 can be stabilized. Further, the adjustment portions 24, 28 may be fitted to the flange portion 23. According to this configuration, since the adjustment portion is fitted to the flange portion, the flange portion is weakened by the adjustment portion, and the joint strength between the driver and the piston can be further improved. Thus, the stress applied to the pin mounting hole can be further reduced by the edge portion of the ib which is reinforced by the adjusting portion. Further, the piston 6 may be constituted by a piston body 6& having a large diameter and a driver jig 6b provided at a lower portion thereof and having a small diameter. Further, the piston 6 may be constituted by an annular piston body 6a and a cylindrical driver jig 6b screwed to the inside of the piston body 6a. Further, the flange portion 23 may be formed to protrude from one of the side faces of the driver 5. Alternatively, the flange portion 23 may be formed to protrude from both side faces of the driver $. According to this configuration, the bonding strength between the devices can be selected according to the use of the nailer. Other features and effects can be understood from the embodiment <t> [Embodiment] Fig. 1 is a vertical sectional view showing a pneumatic nailer of an exemplary embodiment of the invention. The nailing machine of the present invention is used to insert a stud, a staple, and the like. Symbol i 201109132 represents the body, 2 represents the gripping unit, and 3 represents the storage feeder. Inside the body ,, a cylinder 4, a piston 6 housed therein in a freely slidable manner and integrated with the driver 5, and a discharge air chamber 7 (connected to a compressed air supply source) are disposed in the cylinder 4. The compressed air therein drives the overhead valve 8 of the control piston 6 and the trigger valve 9 that controls the actuation of the overhead valve 8. At the apex of the body 1, a nose 10 is provided, and the driver 5 guides the nose 1 slidably. On the nose 1 ,, an opening is formed at the tip end of the storage feeder 3, and a nail (not shown) stored in the feeder 3 is prepared to be supplied to the nose 1〇. Further, the trigger valve 9 is disposed at the base of the gripping portion 2, and the tip end of the valve stem j i of the trigger valve 9 is disposed to face the trigger lever 12. The trigger valve 9 is connected to the air chamber 7 during the non-actuation of the above-mentioned nailer. The compressed air taken in from the air chamber 7 is supplied to the overhead valve 8 through an air flow path (not shown). Thereby, the overhead valve 8 closes the upper end of the cylinder 4 as shown in the figure. When the driving operation is performed, if the trigger lever 丨2 is operated to press the valve 柃 11 of the trigger valve 9, the trigger valve 9 starts to actuate, and the overhead valve 8 is connected to the atmosphere. Further, the upper end of the cylinder 4 is opened (not shown), and the compression space in the air chamber 7 is instantaneously supplied into the cylinder 4. As a result, the driver 5 is driven with the piston 6, and the nails in the nose 10 are struck and driven into the material to be driven. Thereafter, if the trigger lever 12 is released, again, the trigger valve 9 connects the top valve 8 to the air chamber 7 as shown in Fig. 1. The cylinder 4 is closed to the air chamber 7, and at the same time, the cylinder 4 is connected to the atmosphere to perform the exhausting n, and the piston 6 is returned to the initial position in preparation for the next action of driving the nail. Further, the driving control mechanism of the nailer which is generated by the above-described actuation of the trigger valve 9 and the inter-stage 8 is the same as that conventionally known. 201109132 However, as shown in Figs. 2(a) and 2(b), the piston 6 is integrally formed by a piston holder 6a having a large diameter and a driver jig having a small diameter at a lower portion thereof. The piston body 6a is formed in a cylindrical shape, and an annular groove π for fitting the piston ring 16 is provided around the outer peripheral surface thereof. The driver jig 讥 is formed in a cylindrical shape, and a fitting groove 18 having an opening and having a slit shape is formed at a central portion thereof. Further, the driver jig 6b is formed with a pin hole 9 in a posture perpendicular to the center line 〇 of the piston 6 and spanning the fitting groove 18. Further, the driver 5 is formed in a plate shape and fitted to the fitting groove 18 of the driver jig 6b to provide a fixing action. As shown in Figs. 3(a) and 3(b), a fitting portion 20 having a square plate shape is formed in the upper portion of the actuator 5. The fitting portion 20 is sized to be approximately the same as the drinking groove 1 8 of the piston 6. Further, a pin attachment hole 22 for inserting the fixing pin 21 is formed in the fitting portion 2''. At the peripheral portion of the pin mounting hole 2 2, the annular flange portion 23 protrudes into a rib shape. The flange portion 23 can be formed by burr processing. Further, a metal gasket 24 is superposed on the surface on the side of the flange portion 23 of the upper portion of the actuator 5 as the inner surface of the embedding fitting groove 18 and the surface on the side of the flange portion 23 of the actuator 5. The adjustment portion of the gap. The washer 24 is formed to have a size approximately the same as that of the fitting portion 2 of the driver 5, and a fitting hole 25 fitted to the flange portion 23 is formed. Further, the thickness of the gasket 24 is formed larger than the height of the flange portion 23. Then, when the piston 6 and the driver 5 are combined, the driver 5 and the washer 24 are superposed (or not coincident), and fitted to the fitting groove 18 of the driver jig of the piston 6. At this time, the pin hole 19 is integrated with the pin mounting hole 22 of the driver 5. Therefore, the fixing pin 21 is inserted from one side of the pin hole 19, and penetrates from the pin mounting hole 22 of the drive 201109132 5 to the pin hole 19. Further, the r side may be fixed by fixing the end of the pin 21 or by fixing the pin to the pin hole 19 by crimping. Thereby, the driver jig and the driver 5 are combined as shown in Figs. 2(a) and 2(b). According to the mounting structure of the piston 6 and the driver 5, when the piston 6 is driven to drive the piston 6, the piston 6 collides with the damper 26 at the lower portion of the cylinder. In contrast, the driver 5 has an inertial force, so the pin 21 is fixed. There is stress concentration on the joint between the driver and the driver 5. The joint portion is the flange mounting portion 22 of the driver 5 and the flange portion 23 of the peripheral portion thereof, but the joint strength between the driver and the piston can be improved by the flange portion 23. Further, the washer and the flange portion 23 are fitted to each other, whereby the washer 24 is integrated with the driver 5, and is buried in the gap between the inner surface of the fitting groove 18 and the surface on the side of the flange portion 23 of the actuator 5. The installation state of the drive 5 is stable. In this way, the stress concentration is generated at the edge (peripheral portion) of the pin mounting hole 22. In order to prevent the inertial force from being slightly deformed at the edge of the hole, a flange portion is formed at the peripheral portion of the pin mounting hole 22 of the driver 5. This has the effect of rigidity. Further, the driver 5 fits the washer 24 to the flange portion 23 to thereby fit into the fitting groove of the piston 6, so that the contact between the piston 6 and a driver 5 is achieved. The surface is sufficiently ok to stabilize the actuator 5 t and the thickness thereof is formed larger than the height of the flange portion 23, so that the flange portion 23 does not contact the inner surface of the fitting groove 18, so that it can be used as a driver The peripheral portion of the edge of the pin mounting hole 22 of 5 is sufficiently rigid. Further, 'the ring portion 24 is formed with the flange portion of the driver 5 _ 8 201109132 hole 25 ' so that 'by fitting' Positioning can suppress the sound emitted when combined with the piston 6. Further, if the ring 24 is fitted to the size of the fitting groove 18, the thickness can be as shown in Fig. 4(a) and the flange portion 23 can be formed. The height is about the same. The ring 24 and the flange After being formed separately, the flange portion 23 and the fitting hole 25 are fitted together. 'Re-fitting to the fitting groove 18' can also be processed by crimping, and the gasket 24 can be inserted when the flange portion 23 is formed. When the latter is used, the flange portion 23 is formed along the inner surface of the fitting hole 25 of the gasket 24, and the gasket 24 is pressed and joined with the driver 5 for strength, and the flange portion 23 is not It is limited to a shape that protrudes on one side of the fitting portion 2〇 of the driver 5. As shown in Fig. 4(b), it can be formed on both sides of the fitting portion 20 by forging. In this case, the pad The cymbal 24 is also disposed on both sides of the fitting portion. Thus, the flange portion 23 can be formed on one side or both sides of the driver 5 according to the use of the nailer. Further, the pin mounting hole of the driver is not limited The circular shape may be an elliptical shape, a long hole shape or a polygonal shape. Further, the piston body 6a and the driver jig 6b do not have to be integrated. It may also be a structure in which two separate bodies are combined. The flange portion 23 may not be a ring. It may also be formed only on the upper part of the pin mounting hole which will be produced when the drive is made. Further, the flange portion 23 may be formed separately from the driver 5. For example, as shown in Fig. 5, a cylindrical convex portion composed of a fitting portion 26 having a small outer diameter and a large flange portion 23 may be used. The edge element u is integrated with the driver 5 by a technique such as friction welding. The outer driver jig 6b is not limited to a cylindrical shape, and may be an elliptical type, a 201109132 polygonal shape, etc. Further, the above-described driver 5 is convex on the driver jig. Around the edge portion 23, a gasket 24 is provided as an adjusting portion for holding and mounting the inner surface of the fitting groove of the piston 6 and the driver 5, but the adjusting portion can form an element separate from the driver jig 6b, for example, In the sixth (a) and sixth (b) views, the intermediate member 28 may be fixed to the driver jig 6b in a state of being provided around the flange portion 23 of the driver 5. However, if the flange portion 23 ensures sufficient rigidity at the edge of the pin mounting hole 22, the adjusting portion having the reinforcing function such as the gasket 24 and the intermediate member 28 is not required. In this case, as shown in Figs. 7(a) and 7(b), the inner surface of the fitting groove 18 which is only for holding and mounting the piston 6 can be formed around the flange portion 23. The convex portion 2 9 is spaced apart. Furthermore, the configuration of the driver jig is not limited to the above-described type. For example, as shown in Fig. 8(a), a driver jig 6b having the same diameter is formed integrally with the piston body 6& and a fitting groove 18 having an opening is formed on the driver jig. A latch mounting hole 22 is formed in an upper portion of the driver 5, and a rib-shaped flange portion 23 is formed at a peripheral portion of the latch mounting hole 22, and is provided on the side of the flange portion 23 of the driver 5 The flange portion 23 is fitted into the gasket 24 of the fitting hole 25, and the driver 5 and the washer 24 are fitted to the fitting groove 8 of the piston 6, and the posture of the piston 6 is continuously inserted. The formed pin hole 9 is combined with the fixing pin 21 of the pin mounting hole 22 of the driver 5. Figure 8(b) is a vertical sectional view of another type of driver clamp, in which a driver clamp is formed inside the piston 6, and the piston 6 is screwed to the cylindrical driver fixture of the annular piston body 6a 10 201109132 and to the inner side thereof. 6b is configured to form a fitting groove 18 having an opening in the lower central portion of the driver jig 6b, and fitting the driver 5 and the gasket 24 to the fitting groove 18 of the piston 6, by continuously inserting across the driver The pin hole 19 formed by the posture of the jig 6b is coupled with the fixing pin 21 of the pin mounting hole 22 of the driver 5. According to the above configuration, the fixing pin 21 faces the inner peripheral surface of the piston main body 6a and cannot be pulled out. Therefore, it is not necessary to provide a locking device having a fastening action or the like. In the case of Fig. 8(a) and Fig. 8(b), the same effects as those shown in Figs. i to 4(b) can be obtained, and the gasket 24 and the flange portion can be obtained. The shape of 23 and the pin mounting hole 22 of the actuator 5 and the like are not limited to the ones shown in Figs. 1 to 4(b). [Industrial Applicability] The present invention can be applied to the construction of a driver and a piston in a hammer. . σ [Simplified description of the drawings] Fig. 1 is a vertical sectional side view showing a pneumatic nailer of an exemplary embodiment of the present invention. Figure 2 (a) is a front view of the piston combined with the drive of φ ^ m. Figure 2(b) is >. The A-A line cuts the cross-sectional view of Fig. 2(a). Figure 3(a) shows the second diagram of the drive "line cut door. Figure 3(b) is a cross-sectional view of the third (a) cut along Y Y green. 11 201109132 Figures 4(a) and 4(b) are cross-sectional views showing the other states of engagement of the actuator and the piston, respectively. Fig. 5 is a cross-sectional view showing another embodiment of the flange portion. Fig. 6(a) is a front elevational view showing another embodiment of the adjustment unit. Fig. 6(b) is a view taken along line CC of Fig. 6(a) and Fig. 7(a) is a view showing another 7(b) of the adjustment portion, which is cut along the DD line and is cut along the DD line (Fig. 7(a) and Fig. 8 ( a) Figure and Figure 8(b) are respectively straight cross-sectional views. Sectional view. - Front view of the implementation type. Sectional view of the first. Indicates other types of pistons. [Main component symbol description] 1~ Body; 2~ Grab; 3~ Storage feeder; 4 Steam red; 5~ Drive; 6~ Piston; 6a~ Piston body; 6b'~ Drive clamp 7~ air chamber; overhead valve; 〇9~ trigger valve; 10' ~ nose; 11' ~ valve stem; 12' ~ trigger lever; 16' - piston ring; 17' ~ annular groove; ^Fixed groove; 19' ~ pin hole; 2 (l· ^ talks; 21' ~ fixed pin; 22' ~ pin mounting hole; 23' ~ flange part; 24' ~ washer (adjustment); ' ~ fitting hole; 26' - fitting portion; 27' ~ flange member; 12 201109132 28 ~ intermediate member (adjustment portion); 29 to convex portion (adjustment portion 13