554101 五、發明說明（1 ) 【發明之技術領域】 本發明係關於由投緯泵將水壓送至投緯噴嘴而從投緯噴 嘴噴射水，藉上述投緯噴嘴之水噴射作用投緯緯紗之噴水 投緯織機（water jet loom)之水噴射裝置。 【發明之背景】 第1 0圖係表示習知噴水投緯織機之水噴射裝置，第1 1圖係表示構成習知水噴射裝置之投緯泵11之內部構造 。在投緯泵1 1之筒形狀之泵殼1 2內，收容固定有貯水 室形成壓缸1 3。在貯水室形成壓缸1 3筒內可滑動地收 容有柱塞1 4。在柱塞1 4安裝有彈簧板1 5。在圓筒狀 之泵殼1 2內周面，螺合有彈簧帽蓋1 6。彈簧帽蓋1 6 係藉鎖固螺帽1 7之栓緊固定於泵殼1 2。彈簧板1 5之 座部1 5 1與彈簧帽蓋1 6之座部1 6 1之間，具有螺旋 彈簧1 8。 泵殻12形成有吸入口 121及排出口 122，在吸入 口 1 2 1與排出口 1 2 2之間，形成有貯水室1 2 3。貯 水室1 2 3與吸入口 1 2 1之間，及貯水室1 2 3與排出 口 123之間，分別裝設有止回閥19，20。如第1〇 圖所示，連接於吸入口 1 2 1之吸入管2 4，係連通於浮 筒（float box) 25，連接於排出口 122之排出管26 爲連接於投緯噴嘴2 7。 柱塞2 4係經由接頭2 1連結於凸輪桿2 2。凸輪桿2 2係經由凸輪從動件2 2 1可接離凸輪2 3。凸輪桿2 2 554101 五、發明說明（2 ) 係同步於織機之迴轉以一定之角速度向第10圖之箭頭Z 方向迴轉之凸輪2 3，與螺旋彈簧1 8之供動往復擺動。 柱塞1 4及彈簧板1 5，係藉凸輪桿2 2之往復擺動而一 體地往復運動。於第1 0圖，凸輪桿2 2爲由於凸輪2 3 之迴轉力將支軸2 2 2爲中心向左轉動時，柱塞1 4及彈 簧板15係抗衡螺旋彈簧之彈簧力進行往動（於第11圖 從右側向左側之移動）。彈簧板1 5之往動動作將壓縮螺 旋彈簧1 8。柱塞1 4之往動動作，係從浮筒2 5經由沿 入管2 4向貯水室1 2 3內，吸入一定水量。打開止回閥 1 9吸水於貯水室1 2 3內之時段，止回閥2 0係關閉， 排出管2 6內之水不至於逆流到貯水室1 2 3側。 當凸輪從動件2 2 1超越凸輪2 3之凸輪面2 3 1之最 大徑位置Ma時，凸輪從動件2 2 1就離開凸輪2 3之凸 輪面2 3 1，受到螺旋彈簧1 8之復原力之柱塞1 4將加 壓貯水室1 2 3內之水。貯水室1 2 3內之水被加壓時， 不僅止回閥1 9就關閉，並且，止回閥2 0就打開，貯水 室1 2 3內之被加壓之水，係經由排出管2 6壓送至投緯 噴嘴2 7。被壓送到投緯噴嘴2 7之水，係從投緯噴嘴2 7噴射，緯紗Y就被投緯至經紗開口內。從凸輪2 3之凸 輪面2 3 1離開之凸輪從動件2 2 1就抵接於凸輪面2 3 1或另設之噴射水量限制用之擋止器2 8，而結束1循環 之水噴射。 擋止器2 8係由不動地所配置之陰螺旋體2 8 1，與螺 554101 五、發明說明（3 ) 合於陰螺旋體2 8 1之陽螺旋體2 8 2，與螺著於陽螺旋 體2 8 2之鎖固螺帽2 8 3所構成。陽螺旋體2 8 2係由 於鎖固螺帽283之栓緊，而被固定於陰螺旋體281。 鎖固螺帽2 8 3係由於鎖固螺帽2 8 3之栓緊，而被固定 於陰螺旋體2 8 1。藉變更對於陰螺旋體2 8 1之陽螺旋 體2 8 2之螺入位置，就變更凸輪桿2 2之復動方向之最 終端位置。 第13圖之圖表之曲線K係表示織機迴轉角度與凸輪升 程量（亦即，從凸輪2 3之凸輪面2 3 1之最小徑位置向 半徑方向之凸輪從動件2 2 1之位移量）之關係。織機迴 轉角度0 1〜0 2，係凸輪升程量約略以等速度增加之水 吸入行程，織機迴轉角度03〜04，係凸輪升程量從最 大値快速地減少之水噴射行程。 若認爲水之慣性力或管路摩擦阻力爲小加以忽視時，從 投緯噴嘴2 7之水噴射時，就成立以下之式（1 )所示之 運動方程式。 m · d x2/ d t2=(F — k*x) + (Pa — Ρο)Αρ· · · · (1) 於式（1 )， m係凸輪桿22，柱塞14，螺旋彈簧18，彈簧板 16等之動力傳達系之可動體之等値質量合計， X係柱塞14之移位， d X 2/ d t 2係柱塞之加速度， k係螺旋彈簧18之彈簧常數， 554101 五、發明說明（4 ) F係開始噴射水時之螺旋彈簧18之壓縮負荷， P 〇係貯水室1 2 3之壓力， P a係大氣壓， A p係柱塞1 4之剖面積。 第12圖之圖表之直線f係表示螺旋彈簧18之長度與 彈簧負荷之關係。h 〇所示範圍係作爲柱塞1 4之動作範 圍所使用之螺旋彈簧18之長度之移位範圍之一例。 貯水室1 2 3之壓力P 〇，亦即，關於水噴射壓力整理 式（1 )時，就可得到以下之式（2 )。554101 V. Description of the invention (1) [Technical field of the invention] The present invention relates to the weft-feeding pump feeding water to the weft-injection nozzle and spraying water from the weft-injection nozzle. Water jet loom water jet loom. [Background of the Invention] FIG. 10 shows the water injection device of the conventional water injection weaving loom, and FIG. 11 shows the internal structure of the weft injection pump 11 constituting the conventional water injection device. In the cylinder-shaped pump housing 12 of the weft feeding pump 11, a water storage chamber 13 is formed and fixed. A plunger 14 is slidably contained in a cylinder 13 formed in the water storage chamber. A spring plate 15 is attached to the plunger 14. A spring cap 16 is screwed onto the inner peripheral surface of the cylindrical pump casing 12. The spring cap 16 is fastened to the pump casing 12 by the bolts of the lock nut 17. A coil spring 18 is provided between the seat portion 15 of the spring plate 15 and the seat portion 16 of the spring cap 16. The pump casing 12 is formed with a suction port 121 and a discharge port 122, and a water storage chamber 1 2 3 is formed between the suction port 1 2 1 and the discharge port 1 2 2. Between the water storage chamber 1 2 3 and the suction port 1 2 1 and between the water storage chamber 1 2 3 and the discharge port 123, check valves 19 and 20 are respectively installed. As shown in Fig. 10, the suction pipe 24 connected to the suction port 1 21 is connected to a float box 25, and the discharge pipe 26 connected to the discharge port 122 is connected to the weft injection nozzle 27. The plunger 24 is connected to the cam lever 22 via a joint 21. The cam lever 2 2 can be detached from the cam 23 via a cam follower 2 2 1. Cam lever 2 2 554101 V. Description of the invention (2) The cam 2 3 is synchronized with the rotation of the loom and rotates at a certain angular speed in the direction of the arrow Z in FIG. 10, and reciprocates with the supply of the coil spring 18. The plunger 14 and the spring plate 15 are integrally reciprocated by the reciprocating swing of the cam lever 22. In Fig. 10, when the lever 2 2 is turned to the left due to the pivoting force of the cam 2 3, the plunger 14 and the spring plate 15 are moved counter to the spring force of the coil spring ( (From left to right in Figure 11). The forward movement of the spring plate 15 will compress the coil spring 18. The forward movement of the plunger 14 is to suck a certain amount of water from the buoy 25 through the inlet pipe 24 into the water storage chamber 1 2 3. During the period when the check valve 19 is opened to absorb water in the water storage chamber 1 2 3, the check valve 20 is closed, and the water in the discharge pipe 26 cannot flow back to the water storage chamber 1 2 3 side. When the cam follower 2 2 1 exceeds the maximum diameter position Ma of the cam surface 2 3 1 of the cam 2 3, the cam follower 2 2 1 leaves the cam surface 2 3 1 of the cam 2 3 and is subject to the coil spring 1 8 The resilience plunger 14 will pressurize the water in the water storage chamber 1 2 3. When the water in the water storage chamber 1 2 3 is pressurized, not only the check valve 19 is closed, but also the check valve 20 is opened. The pressurized water in the water storage chamber 1 2 3 is passed through the discharge pipe 2 6 pressure feed to the weft injection nozzle 27. The water pressed to the weft-feeding nozzle 27 is sprayed from the weft-feeding nozzle 27, and the weft Y is thrown into the opening of the warp yarn. The cam follower 2 2 1 leaving from the cam surface 2 3 1 of the cam 2 3 abuts on the cam surface 2 3 1 or the stopper 2 8 for the water spraying limiter, and ends the water spraying of 1 cycle. . The stopper 2 8 is a female spiral body 2 8 1 which is arranged immovably, and the screw 554101. 5. Description of the invention (3) The male spiral body 2 8 2 is connected to the female spiral body 2 8 1 and is screwed to the male spiral body 2 8 It is composed of 2 lock nuts 2 8 3. The male spiral body 2 8 2 is fixed to the female spiral body 281 due to the locking of the locking nut 283. The locking nut 2 8 3 is fixed to the female spiral body 2 8 1 due to the locking of the locking nut 2 8 3. By changing the screw-in position of the male spiral body 2 8 1 and the male spiral body 2 8 2, the end position of the re-moving direction of the cam lever 2 2 can be changed. The curve K in the graph in FIG. 13 represents the rotation angle of the loom and the cam lift amount (that is, the displacement amount from the minimum diameter position of the cam surface 2 3 1 of the cam 2 3 to the cam follower 2 2 1 in the radial direction. ) Relationship. The rotation angle of the loom is 0 1 ~ 0 2, the cam lift amount is increased by water at a constant speed. The suction stroke of the loom, the rotation angle of the loom is 03 ~ 04, the water jet stroke of the cam lift amount is rapidly reduced from the maximum. If the inertial force of water or the frictional resistance of the pipeline is considered to be small and ignored, when the water is ejected from the weft-injection nozzle 27, the motion equation shown in the following formula (1) is established. m · d x2 / d t2 = (F — k * x) + (Pa — Ρο) Αρ · · · · (1) In the formula (1), m system cam rod 22, plunger 14, coil spring 18, spring The total mass of the movable body of the power transmission system such as the plate 16 is total, X is the displacement of the plunger 14, d X 2 / dt 2 is the acceleration of the plunger, k is the spring constant of the coil spring 18, 554101 V. Invention Explanation (4) F is the compressive load of the coil spring 18 at the beginning of water injection, P 0 is the pressure in the water storage chamber 1 2 3, P a is the atmospheric pressure, and A p is the cross-sectional area of the plunger 14. The straight line f in the graph of Fig. 12 represents the relationship between the length of the coil spring 18 and the spring load. The range indicated by h o is an example of the shift range of the length of the coil spring 18 used as the operating range of the plunger 14. The pressure P 0 of the water storage chamber 1 2 3, that is, when formula (1) is adjusted with respect to the water jet pressure, the following formula (2) can be obtained.
Po=Pa+(F — k.x—m.dx2/dt2)/A· · · · (2) 於式（2 )，在噴射開始水階段，首先，質量m由彈簧 力F快速地被加速。接著，當加速結束時，亦即，慣性力 m· dx2/dt2接近於零時，彈簧力（F — k · X) 與壓力P 〇就邊平衡進行水之噴射。於水噴射進行過程， 當水噴射初期之移位X爲小時，水噴射壓力爲高。另者， 水之噴射進行復原螺旋彈簧1 8時，亦即，隨著移位X之 增加，水噴射壓力P 〇，就逐漸降低。於水噴射結束即前 ，水噴射壓力P 〇係取水噴射期間中之最低値。並且，將 吸入於貯水室1 2 3之水全部噴射結束時，凸輪從動件2 2 1係衝突於擋止器2 8或凸輪2 3，水噴射壓力P 〇將 降低到大氣壓。這種水噴射壓力P 〇之減壓波形，係很適 合於緯紗Y之投緯。 亦即，依據上述水噴射壓力P 〇之減壓波形從投緯噴嘴 554101 五、發明說明（5) 2 7噴射水時，在投緯初期一下子加速緯紗Y，隨著投緯 之經過水噴射速度之降低，緯紗速度將降低。因此，可防 止於水噴射過程之緯紗鬆緩，就可實現緯紗Y之姿勢保持 筆直狀態進行安定之投緯。 具有如上述特性之螺旋彈簧方式之水噴射裝置，係自從 噴水投緯裝置織機之開發以來重新地經過改良。因此，螺 旋彈簧方式之水噴射裝置，被認定其可靠性，一貫被採用 到今日。 然而，於螺旋彈簧發生所謂突激波（surging)之諧振 現象（resonance phenomena)爲人所知曉，螺旋彈簧1 8 之突激波振動將對於緯紗之投緯發生不良影響。亦即，螺 旋彈簧1 8爲在水噴射過程發生突激波振動時，螺旋彈簧 1 8之突激波振動就傳達於貯水室1 2 3內之水，水噴射 壓力P 〇之波形將如打浪般發生變動。起因於螺旋彈簧 1 8之突激波振動之水噴射壓力P 〇之波形變動將打亂緯 紗Y之投緯。緯紗Y之投緯紊亂，將降低織物品質。 似此之螺旋彈簧1 8之突激波現象，係水噴射壓力P 〇 之時間性變化愈大，換言之，織機之轉數愈高愈顯著。 又，水噴射周期（=6 Osec/每一分鐘之織機轉數）爲與 突激波振動之周期整數倍相符時，突激波就有規則地被激 起’致使螺旋彈簧1 8之振動就更加變成激烈。 爲了緩和螺旋彈簧1 8之突激波振動之目的，嘗試對於 螺旋彈簧1 8附加衰減機構，或日本專利特開平1 〇 一 554101 五、發明說明（6) 2 9 9 6 4 3 號公報（Japanese Patent-open No.10-29 9 643 )所揭示，作爲螺旋彈簧1 8使用非線型彈簧 (non-linear spring)等之對策。但是，對於螺旋彈簧1 8附加衰減機構之對策’將使構造變成複雜化，而具有成 本偏高之問題。作爲螺旋彈簧1 8使用非線型彈簧之對 策，有欲製作有效地抑制突激波振動之發生較佳之非線型 彈簧爲困難之問題。 欲使織機高速化時，就必須提高緯紗Y之投緯速度，亦 即，需要提高水噴射壓力P 〇。欲提高水噴射壓力P 〇 時，增加螺旋彈簧1 8之壓縮量加以因應。但是，只增加 螺旋彈簧1 8之壓縮量，只提高彈簧負荷時，螺旋彈簧 1 8或凸輪桿2 2等之動力傳達系之強度將變成不足。於 是，若增大螺旋彈簧1 8或凸輪桿2 2等之動力傳達系之 尺寸時，將變成增加式（1 )之質量m，致使柱塞1 4之 建立速度就降低，因此，水噴射壓力P 〇之建立速度就降 低。若水噴射壓力P 〇之建立速度低時，因會發生先出來 之速度慢之水因後面出來之速度快之水所趕過之現象（以 下，稱爲「趕過現象」），噴水先端部之噴霧形狀之紊亂 就容易發生。其結果，高速之水滴就衝突於經紗而受傷經 紗，在織物製品將出現叫做分經路（warp streak)之缺 點。這種缺點將降低織物品質。 【發明槪要】 本發明之目的係提供一種水噴射裝置，其係不至於降低 554101 五、發明說明（7 ) 織物品質之降低，可更加高速化噴水投緯織機。 因此，本發明係藉投緯泵壓送水到投緯噴嘴而從投緯噴 嘴噴射水，藉上述投緯噴嘴之水噴射作用投緯緯紗之噴水 投緯織機之水噴射裝置作爲其對象。 並且，本發明之主要層面，係作爲關於本發明之水噴射 裝置，其特徵爲；將上述投緯泵之水噴射產生用驅動源， 使用將可壓縮之氣體狀之流體壓力作爲彈簧力之流體彈簧 裝置。 又，上述流體彈簧裝置，係將空氣之壓力作爲彈簧力之 空氣彈簧裝置較佳。 於如上之構成，將可壓縮之流體壓力作爲彈簧力之流體 彈簧裝置，因突激波振動爲少，所以起因於突激波振動之 水噴射壓如打波浪之變動爲少。因此，可改善緯紗之投緯 由於突激波振動所打亂之狀態。又，因無以往之螺旋彈簧 之分量，於上述式（1 )之質量m就減少，而可提高水噴 射壓之建立速度。 並且，上述投緯泵，係具有；泵殼，與在上述泵殼內被 收容於往復運動所收容之柱塞，與將上述柱塞向往動方向 驅動之凸輪機構，與將上述柱塞向復動方向施壓之上述流 體彈簧裝置，與藉上述柱塞之往復動如變化容積在上述泵 殼內所區隔之貯水室，藉上述柱塞之往動動作，吸入水於 上述貯水室，由於上述柱塞之復動動作，上.述貯水室內之 水爲被壓送至上述投緯噴嘴較佳。 554101 五、發明說明（8 ) 因這種構成，當凸輪機構將柱塞向往動方向驅動時，水 就被吸入於貯水室。當凸輪機構容許柱塞之復動方向之移 動時，柱塞由流體彈簧裝置之流體壓力所復動。以往之螺 旋彈簧式投緯泵，係將其螺旋彈簧以流體彈簧裝置替換些 許零件之變更與追加，就可改造爲本發明之投緯泵。 並且又，上述流體彈簧裝置，係具有：可變化容積形成 壓力室之壓力室形成殼，與將上述壓力室內之壓力傳達於 上述柱塞之壓力傳達裝置，上述壓力室之容積係藉帶來上 述柱塞之往動動作之上述凸輪機構之往動動作就可減少。 似此地，壓力室之容積由於流體壓力之增大時，柱塞就 復動，貯水室內之水將被壓送至投緯噴嘴。 又，上述壓力傳達裝置，係結合於上述柱塞之活塞，上 述壓力室形成殼，係在上述泵殼內收容可往復動上述活塞 之壓缸較佳。 於這種構成，在壓缸內區隔壓力室之活塞爲由於流體之 壓力移動時，柱塞爲復動，貯水室內之水將被壓送至投緯 噴嘴。 並且，將上述壓力室隨伴著上述柱塞之往動壓縮流體之 壓縮室較佳。 由於這種構成，在壓縮室內所壓縮之流體之壓縮反作用 將使用於柱塞之復動。 並且，又備有爲了設定於上述流體彈簧裝置之準初期壓 力所需之準初期壓力設定裝置，由上述準初期壓力，就可 -10- 554101 五、發明說明（9) 將上述壓縮室內之流體成爲開始壓縮時之上述壓縮室內之 壓力。 藉這種構成，壓縮室內之壓力係由於從準初期壓力裝置 所設定之準初期壓力之狀態開始壓縮。水噴射過程之壓縮 室內之壓力，將變成準初期壓力以上。柱塞之行程因係每 一投緯爲一定，所以，將壓縮室內之流體壓縮爲最大時之 壓力爲一定，水噴射係依據壓縮室內之流體壓縮至最大時 之壓力之狀態開始。 又，具有爲了設定上述流體彈簧裝置之初期壓力所需之 初期壓力，將上述初期壓力成爲開始噴射水時之上述壓力 室內之壓力較佳。 若依據這種構成時，壓力室內之流體壓力，係每一投緯 重設爲初期壓力，水噴射係壓縮室內之流體壓縮從初期壓 力狀態開始。水噴射過程之壓縮室內之壓力將變成初期壓 力以下。 並且，上述初期壓力裝置係備有：對於流體彈簧裝置供 給流體所需之流體壓力源，設定供給於上述流體彈簧裝置 之流體壓力之壓力設定裝置，將由上述壓力設定裝置所設 定之壓力之流體切換爲可供給於上述流體彈簧裝置之狀態 與不能供給狀態之供給切換裝置，上述切換裝置係水噴射 行程前，且在吸入水行程後之期間可成爲可供給之狀態。 水噴射行程前，且吸入水行程後之期間，將壓力室內之 流體壓力，每投緯時，作爲在初期壓力正確地重設期間爲 -11- 554101 五、發明說明（1 〇) 最佳。 並且，又將上述壓力室形成殼，作爲經由移位傳達體連 結於上述凸輪機構之隔膜，該隔膜內之上述壓力室之壓力 爲經由上述移位傳達體及上述凸輪機構傳達於上述柱塞較 佳。因構成變成單純，投緯泵之耐久性將可大幅度地提 又，在上述柱塞之上述凸輪機構側螺著向該柱塞之軸向 可往復動之位置調整體，安裝在該位置調整體可相對轉動 但是向軸向之移動受到阻止之上述活塞，因上述位置調整 體之螺著位置之變更，以變更上述壓力室之初期容積也較 佳。 藉這種構成，就可容易變更於水噴射裝置之水噴射壓之 梯度。 又，在上述隔膜固定陰螺絲，將上述位移傳達體作爲螺 著於上述陰螺旋體之陽螺絲，因對於上述陰螺旋體之上述 陽螺旋體之螺著位置之變更，也可變更上述壓力室之初期 容積。 藉這種構成，就可容易變更於水噴射裝置之水噴射壓之 梯度。 並且，形成於上述壓力室形成殻內之上述壓力室內，也 可收容螺旋彈簧。 藉這種構成，雖然突激波振動之抑制效果稍爲減少，但 是具有空氣壓力源之原壓可低壓化之益處。 •12- 554101 五、發明說明（11) 【發明之實施形態】 第1實施形態 茲依據第1圖〜第5圖說明本發明具體化之第1實施形 態如下。 對於第1 0圖及第1 1圖之習知裝置相同構成部，使用 相同符號，而省略其詳細說明。 如第1 B圖所示，構成投緯泵2 9之泵殻1 2螺合有壓 缸3 0。壓缸3 0係因鎖固螺帽3 1之栓緊固定於泵殻 1 2。在壓缸3 0有活塞3 2如包圍貯水室形成壓缸1 3 被收容成可滑動。活塞3 2係結合固定於柱塞1 4。活塞 3 2與柱塞1 4係在壓缸3 0，1 3之軸線方向可一體地 移動。 在壓缸3 0有密封環3 3被安裝成可與活塞3 2外周面 滑接。在活塞3 2有密封環3 4被安裝成可與壓缸3 0之 內周面滑接。壓缸3 0內周面與活塞3 2外周面之間，且 密封環33，34間，形成有壓縮室35。 在壓縮室3 5，經由空氣管路3 7連接於空氣壓力源 3 6。在空氣管路3 7上裝有備有釋放機能之壓力調整閥 3 8及止回閥3 9。在壓力調整閥3 8與壓縮室3 5之 間，並聯地裝設有節流通路4 0與止回閥3 9。壓力調整 閥3 8與止回閥3 9間之空氣管路3 7連接有壓力計 4 1。壓力計4 1係用來量測壓力調整閥3 8與止回閥 3 9間之空氣壓力者。壓力調整閥3 8與止回閥3 9間之 -13- 554101 五、發明說明（12) 空氣壓力，係邊觀看壓力計4 1藉操作調整壓力調整閥 3 8加以設定。具有釋放（relief)機能之壓力調整閥 3 8係將壓力調整閥3 8與止回閥3 9間之空氣管路3 7 之壓力，經常維持由壓力調整閥3 8所設定之壓力。由壓 力調整閥38所設定之壓縮室35內之壓力Pi (準初期 壓力），係壓縮室3 5內之活塞3 2爲如第2 B圖所示位 於最右側時之壓力。 凸輪桿2 2將支軸2 2 2爲中心向右轉動時，柱塞1 4 及活塞3 2，係如第1 A，B之箭頭Q所示向往動方向移 動。當柱塞1 4向箭頭Q所示方向之往動方向移動時，貯 水室1 2 3內之容積就增大，浮筒2 5內之水就被吸入於 貯水室1 2 3內。當柱塞3 2向箭頭Q所示之往動方向移 動時，壓縮室3 5之容積就減少，壓縮室3 5內之壓力就 從準初期壓力p i開始上升。於壓縮室3 5內之壓力之上 升開始，將關閉止回閥39。其後，壓縮室35內之壓 力，係隨著活塞3 2之往動而上升，在活塞3 2之往動結 束時，壓縮室3 5內之壓力將變成最大。壓縮室3 5之空 氣壓縮開始時之壓力，係由於止回閥3 9之存在，將被規 定於由壓力調整閥3 8所設定之準初期壓力P i。亦即， 壓縮室3 5之壓力將被保持於由壓力調整閥3 8所設定之 準初期壓力P i以上之位準。於第3圖之圖表之曲線P b 係表示壓縮室3 5之容積與壓縮室3 5內之壓力關係。 將第3圖之曲線P b所示壓力變化以式表示時，將變成 -14- 554101 五、發明說明（13) 如下。一般，在空氣壓縮機之中空氣爲壓縮•膨脹時之實 際壓力P之變化，係作爲多變變化（polytropic change) 以下式（3 )表示。 Ρ·Υη= — 定..........（3) 於式（3 )之η係多變指數（polytropic index)，通 常係η = 1 · 2。若壓縮室3 5之容積爲從初期容積V 〇 減少到（Vo — s.Aa)時，將成立下式（4)。 P (Vo-s - Aa)n=Pi ·ν〇η · · (4) 於式（4)之s，係活塞32之位移量（壓縮開始時爲 s=0) ，Aa係壓縮室35之剖面積。 因此，壓縮室35之容積爲（Vo — s .Aa)時之壓 縮室3 5內之壓力P係以下式（5)表示。 P = Pi ·ν〇η/(ν〇-8 *Aa)n· · (5) 亦即’第3圖之曲線Pb ’係以式（5)表示。移位量 s增大，亦即壓縮室3 5之容積減少時，壓縮室3 5內之 壓力P，係如第3圖之箭頭U 1所示，如沿著曲線p b增 大。第3圖之壓力Pm係壓縮室35之容積（Vo — s · Aa)爲最小時之壓力。 當凸輪從動件2 2 1通過凸輪2 3之凸輪面2 3 1之最 大徑位置Ma時，凸輪桿2 2就將支軸2 2 2爲中心向右 轉動柱塞1 4及活塞3 2係由於壓縮室3 5內之被壓縮空 氣之壓力Pm，向第2A，B之箭頭R所示復動方向移動 。若柱塞1 4向箭頭R所示復動方向移動時，貯水室1 2 -15- 554101 五、發明說明（14 ) 3內之水就受到加壓。貯水室1 2 3內之被加壓之水係向 投緯噴嘴2 7壓送。被壓送於投緯噴嘴2 7之水，就從投 緯噴嘴2 7噴射。 另一方面，移位量s減少，亦即壓縮室3 5之容積增大 時’壓縮室3 5內之壓力P就如第3圖之箭頭U 2所示， 如沿著曲線P b而減壓。如第3圖之箭頭U 2所示，如沿 著曲線P b之壓縮室3 5內之空氣壓係於投緯噴嘴2 7之 水噴射壓。 於第1實施形態可得到如下之效果。 (1 — 1 )於第5A圖，第5C圖及第5E圖圖表之曲線 Cl，C2，C3係表示使用習知螺旋彈簧之水噴射裝置 之水噴射壓之變化之量測結果。於第5 B圖，第5 D圖及 第5F圖圖表之曲線El，E2，E3係表示使用從壓缸 30，活塞32，密封環33，34及壓縮室35所構成 之空氣彈簧裝置之本實施形態於水噴射裝置之水噴射壓之 變化之量測結果。第5 A圖及第5 B圖係將織機轉數成爲 7 0 0 r pm之情形，第5 C圖及第5D圖係將織機轉數 成爲800 r pm之情形，第5 E圖及第5F圖係將織機 轉數成爲lOOOrpm之情形。 織機轉數爲7 0 0 r p m時，即使於投緯泵作爲水噴射 壓產生用驅動源使用螺旋彈簧之習知水噴射裝置，及於投 緯泵作爲水噴射壓產生用驅動源使用空氣彈簧裝置之本實 施形態之水噴射裝置，觀察不到起因於突激波振動之大爲 -16- 五、發明說明（15) 引起波浪之變動。織機轉數變成8 0 0 r pm時，就如第 5 D圖所示，於本實施形態之水噴射裝置，雖然觀察不到 起因於突激波振動之大爲引起波浪之變動，但是，如第 5 C圖所示，於習知之水噴射裝置，起因於突激波振動所 引起波浪之變動將變成顯著。 織機轉數變成1 000 r pm時，就如第5E圖所示， 於習知之水噴射裝置，起因於突激波振動所引起波浪之變 動將變成更加顯著。但是，如第5 F圖所示，於本實施形 態之水噴射裝置，即使轉數變成1 0 0 0 r pm也觀察不 到起因於突激波振動所引起大波浪之變動。 於將可壓縮流體之空氣壓力作爲彈簧之空氣彈簧裝置時 ，其突激波振動爲較螺旋彈簧非常地少。因此，起因於突 激波振動之水噴射壓之引起大波浪之變動爲少。使用螺旋 彈簧時所發生之突激波振動，雖然織機轉數愈高變成愈顯 著，但是使用空氣彈簧裝置之本實施形態之水噴射裝置時 ，即使織機轉數變成如1 0 0 0 r pm之高速轉數，也未 發生突激波振動。因此，即使於如1 0 0 0 r pm之高速 迴轉狀態時，也可進行安定之緯紗Y之投緯作業。於織機 之高速運轉之緯紗Y之安定投緯，係不至於損及織物品質 可進行織機之局速運轉。 (1 — 2)於上述式（1 )之質量m，係動力傳達系之可 動體之等値質量之合計。因此，質量m愈小，柱塞1 4之 復動時之初期速度，亦即水噴射壓之升起速度會變高。於 -17- 554101 五、發明說明（16) 未使用螺旋彈簧之本實施形態之水噴射裝置，係較習知使 用螺旋彈簧之水噴射裝置，上述式（1 )之質量m將變小 。因未使用螺旋彈簧導致之質量m之降低，將提高水噴射 壓之升起速度，而可抑制水噴射之「追趕現象」之發生。 因此，可抑制起因於水噴射之「追趕現象」之水噴射先端 部噴霧形狀之紊亂。其結果，就可避免對於經紗衝突高速 水滴，損及經紗之情形，而可避免發生分經路（warp str eaks)引起之織物品質之降低。 (1 一 3)投緯泵2 9係備有：具有貯水室1 2 3之泵殼 12 ;柱塞14 ;與貯水室形成壓缸13 ;空氣彈簧裝 置；與鎖固螺帽17;接頭21 ，凸輪23及凸輪桿 2 2所成之凸輪機構。第1 0圖及第1 1圖之習知投緯泵 11 ，係備有：具有貯水室123之泵殼12;柱塞 1 4 ;貯水室形成壓缸1 3 ;彈簧板1 5 ;彈簧帽蓋 16;鎖固螺帽17;接頭21 ，凸輪23及凸輪桿 2 2所成之凸輪機構。 投緯泵2 9之空氣彈簧裝置，係由壓缸3 0，與密封環 33，34所構成。構成投緯泵11之彈簧板15係可轉 用構成投緯泵2 9之活塞3 2。又，構成習知之投緯泵1 1之泵殻12，柱塞14，貯水室形成壓缸13，鎖固螺 帽1 7及凸輪機構，係仍舊可作爲投緯泵2 9之構成零件 利用。 亦即，習知之螺旋彈簧式之投緯泵1 1，係將彈簧帽蓋 -18- 554101 五、發明說明（17 ) 1 6變更爲壓缸3 0，而追加密封環3 3，3 4之些許零 件之變更與追加，就可改造爲本發明之投緯泵2 9。 (1 - 4 )於本實施形態之水噴射裝置所得到之水噴射壓 之變化，雖然如第3圖所示，但是於水噴射行程中之時間 變化之壓力坡度，係可由下式（6 )表示。 dP/dt=(dP/ds) (ds/dt) · · · (6) 於使用螺旋彈簧1 8之習知水噴射裝置之壓力坡度d P /d t ’係倘右無突激波之擾亂時’就顯不較爲直線性變 化。另者，於使用空氣彈簧裝置之本實施形態之壓力坡度 dP/dt，係dP/ds爲考慮將式（5)以移位量s 微分所得到之曲線時，依據壓縮室3 5之設計如何，也可 實現從直線大爲離開之變化。 其結果，於空氣彈簧泵，藉變更空氣壓力或空氣室之容 積’就以空氣彈簧之非線性特性，就可變化彈簧力或彈簧 力之坡度，藉此就可對應種種製織條件（例如，織寬，緯 紗種類，織機轉數等），而可實現寬廣條件之水噴射壓。 (1 一 5)於第4圖之圖表之曲線Pbl，Pb2， Pb3，Pb4，Pb5係將封入於壓縮室35之空氣重 量爲參數，表示壓縮室3 5之軸線方向長度Η (圖示於第 1Β圖及第2Β圖），與其時之活塞32之負荷（亦即柱 塞14之推力）之關係。於曲線Pbl，Pb2，Pb 3，P b 4，P b 5之空氣重量，係依此順序減少。亦 即，於壓縮室3 5之初期空氣封入壓力（由壓力調整閥 -19- 554101 五、發明說明（18) 3 8所設定之準初期壓力P i )係依曲線Pb 1， Pb2，Pb3，Pb4，Pb5 之順序變低。 在封入於壓縮室3 5之空氣重量爲一定之下（圖示之例 係曲線Pb4)，取壓縮室35之軸線方向長度Η爲短者 ，選擇活塞3 2之動作範圍，亦即柱塞1 4之動作範圍（ 圖示之例爲h 1 )時，柱塞1 4之推力與對於其變化之坡 度將變大。相反地，取壓縮室3 5之軸線方向長度Η爲長 者，選擇柱塞14之動作範圍（圖示之例爲h2)時，柱 塞1 4之推力與對於其變化之坡度將變小。若增加封入於 壓縮室3 5之空氣重量時，柱塞1 4之推力水平，將整體 性地增加。又，增加被封入於壓縮室3 5之空氣重量時， 對於柱塞1 4推力變化之坡度將變大。此係例如於圖示之 動作範圍h2，比較各曲線Pbl，Pb2，Pb3， Pb4，Pb5之坡度就可淸楚。 這種柱塞1 4之推力大小或推力坡度之選擇，係可依於 空氣彈簧裝置空氣彈簧之非線性特性來選擇。亦即，使用 空氣彈簧裝置之本實施形態之水噴射裝置，係可對應於種 種製織條件（例如，織寬，緯紗種類，織機轉數等）而可 實現極寬廣條件之水噴射壓。 (1 一 6 )使用螺旋彈簧1 8之習知水噴射裝置，係如第 1 2圖所示，螺旋彈簧1 8之負荷，亦即可變更水噴射壓 。爲此調整對於泵殼1 2之彈簧帽蓋1 6之螺入位置，必 須調整初期壓縮量。於此調整，將緯紗之投緯狀況，例如 -20- 554101 五、發明說明（19) 使用頻閃觀測器（stroboscope )加以觀測，必須反覆 進行因應其觀測狀況調整彈簧帽蓋16之螺入位置之作 業。調整彈簧帽蓋1 6之螺入位置之作業係必須接受螺旋 彈簧1 8之強力彈簧負荷進行之麻煩作業。 於本實施形態之水噴射裝置，欲變更水噴射壓時，只要 操作壓力調整閥3 8以調整壓縮室3 5內之準初期壓力P i即可，此壓力調整作業爲容易。 (1 — 7 )止回閥3 9係具有：壓縮壓縮室3 5內之空氣 時遮斷壓力調整閥3 8與壓縮室3 5之連通之功能，與限 制壓縮室3 5之最低壓（亦即，由壓力調整閥3 8所設定 之準初期壓力P i )之功能，與從壓縮室3 5洩漏空氣時 補充洩漏空氣分量之功能。 設若依密封環3 3，3 4之密封機能爲完全，從壓縮室 3 5無洩漏空氣時，除非操作壓力調整閥3 8，就無織機 運轉中在止回閥3 9之空氣出入，止回閥3 9只不過是作 爲停止閥之作用而已。 若從壓縮室3 5無洩漏空氣時，壓縮室3 5內之壓力， 即使由壓力調整閥3 8之操作可升壓，不能由止回閥3 9 之作用而減壓。節流通路4 0係將壓縮室3 5內之空氣對 於壓力調整閥3 8側，積極地使其洩漏些許。與止回閥 3 9並聯地裝設節流通路4 0之構成，係若由密封環 3 3，3 4之密封機能完全發揮作用時，就可減壓壓縮室 3 5內。此可減壓之構成係可設定於壓縮室3 5之準初期 -21 - 554101 五、發明說明（2〇) 壓力Pi。空氣壓力源36，壓力調整閥38，止回閥3 9及節流通路4 0係構成於流體彈簧裝置設定之初期壓力 所用之準初期壓力設定裝置。 壓縮室3 5內之空氣係由準初期壓力設定裝置所設定之 準初期壓力P i狀態開始壓縮。水噴射過程中之壓縮室 3 5內之壓力，將變成準初期壓力P i以上。柱塞1 4之 行程因依每投緯爲一定，所以，將壓縮室3 5內之空氣壓 縮爲最大時之壓力，經常保持爲一定。因此，水噴射，係 在將壓縮室3 5內之空氣壓縮到最大時之壓力Pm狀態下 開始。水噴射初期之水噴射壓力係經常符合於較由壓力調 整閥3 8所設定之準初期壓力P i爲高之壓力Pm，於水 噴射過程之水噴射壓，將變成壓力Pm以下且P i以上之 範圍。因此，可間接地控制依投緯來說爲重要要素之水噴 射開始初期之壓力，可做到精度良好之水噴射壓調整。 (1 - 8 )於其原理類似於噴水投緯織機之噴空氣投緯織 機，依因應緯紗之投緯狀況，對於投緯用空氣壓力施加回 饋控制，可達成緯紗之投緯良好地控制之自動化。這種自 動化，係從麻煩之壓力調整解放作業者之工作，可大幅度 地改善作業效率。此係於噴空氣投緯織機，採用原本將投 緯用空氣之噴射壓力使用壓力調整閥直接調整之方法，此 係因將壓力調整閥電氣控制化爲比較容易所致。即使於本 實施形態，也將壓力調整閥3 8藉進行電氣控制化，因應 緯紗之投緯狀況，就可施加回饋控制。 -22- 554101 五、發明說明（21) 第2實施形態 茲說明第6圖及第7圖之實施形態說明如下。關於第1 實施形態相同構成部，使用相同符號而省略其詳細說明。 如第6圖所示，在空氣彈簧調整座4 2，安裝有橡膠製 之隔膜（diaphragm ) 4 3。在隔膜4 3及凸輪桿2 2 固定有移位傳達體45，46。移位傳達體45，46係 互相抵接，隔膜4 3內之壓力室4 3 1之壓力係經由移位 傳達體45，46，凸輪桿22及接頭21傳達於柱塞 1 4。於第2實施形態之投緯泵4 7係除去構成於第1實 施形態之投緯泵2 9之壓缸3 0及活塞3 2。 隔膜4 3內之壓力室4 3 1，係經由空氣管路3 7連接 於空氣壓力源3 6。在空氣管路3 7上，安裝有壓力調整 閥3 8及電磁開閉閥4 4。在壓力調整閥3 8與電磁開閉 閥4 4間之空氣管路3 7連接有壓力計4 1。隔膜4 3係 將成爲構成空氣彈簧裝置之壓力室形成殻。 電磁開閉閥4 4係於水噴射開始即前之些許期間（於第 1 3圖以T所示期間），藉激磁變成開狀態，由壓力調整 閥3 8所設定之初期壓力P k將供給於隔膜4 3內之壓力 室4 3 1。電磁開閉閥4 4係將屬於壓力設定裝置之壓力 調整閥3 8所設定之壓力空氣，成爲可供給於流體彈簧裝 置之狀態與切換成不能供給狀態之供給切換裝置。屬於切 換裝置之電磁開閉閥4 4，係水噴射行程前，經水吸入行 程後之期間，由激磁變成可供給之狀態。 -23- 554101 五、發明說明（22 ) 第2實施形態係可得到以下效果。 (2 - 1 )水噴射初期之水噴射壓，係經常符合於由壓力 調整閥3 8所設定之初期壓力P k，於水噴射過程之水噴 射壓，將變成初期壓力p k以下之範圍。因此，可直接控 制由投緯來說爲重要因素之水噴射開始初期壓力。可做到 精度非常良好之水噴射壓調整。按，將於流體壓力源之空 氣壓力源3 6，具有洩壓機能之壓力調整閥3 8及電磁開 閉閥4 4，係構成設定水噴射每一次之噴射開始之流體彈 簧裝置之初期壓力之初期壓力設定裝置。 (2 — 2)因不需要第1實施形態之密封環33，34， 所以，投緯栗4 7之耐久性係較第1實施形態之投緯栗 29可大幅度地提升。 (2-3)於第7圖之圖表之曲線Pci，Pc2， P c 3，P c 4係對於柱塞1 4之負荷爲零之狀態（亦即 凸輪從動件2 2 1爲處於凸輪面2 3 1之最大徑位置Ma 之狀態）將封入於隔膜4 3之空氣壓力作爲參數，表示隔 膜43之長度L (圖示於第6圖），與其時之活塞32之 負荷（亦即柱塞1 4之推力）之關係。於曲線P c 1， P c 2，P c 3，P c 4之空氣壓力位準，係依據此順序 減少。亦即，於隔膜4 3之初期空氣封入壓力（由壓力調 整閥38所設定之初期壓力Pk)，係依曲線Pel， Pc2，Pc3，Pc4之順序變低。 在封入於隔膜4 3內之空氣壓力爲一定下（圖示之例爲 -24- 554101 五、發明說明（23) 曲線Pc3)，取短之隔膜43長度L，選擇柱塞14之 動作範圍時（圖示例爲h 3)，不僅柱塞14之推力變大 ，並且，對其變化之梯度將變小。相反地，取長之隔膜4 3長度L，選擇柱塞1 4之動作範圍時（圖示例爲h4) ，不僅柱塞1 4之推力變小，並且，對其變化之坡度將變 大。若增加供給於隔膜4 3內之壓力室4 3 1之初期壓力 P k時，柱塞1 4之推力水平就全體地增加。又，若增加 供給於隔膜4 3之初期壓力P k時，對於柱塞1 4推力之 變化之坡度將變大。此係例如於圖示之動作範圍h 4，比 較各曲線Pci，Pc2，Pc3，Pc4之梯度就可淸 楚。 像這種柱塞1 4之推力大小或推力梯度之選擇，係依供 給於構成空氣彈簧裝置之隔膜4 3內之壓力室4 3 1之空 氣彈簧之非線性特性就變成可能。亦即，即使於第2實施 形態之水噴射裝置，就可實現得以對應種種製織條件之極 寬廣條件之水噴射壓。 (2 — 4 )開始噴射水即前之些許期間T，係水噴射行程 前，且水吸入行程後之期間。此期間T係壓力室4 3 1內 之容積最小時，壓力室4 3 1內之容積最小時之壓力室 4 3 1內之空氣壓力每當投緯時重設爲初期壓力P k。因 此，噴射水行程前，且水吸入行程後之期間，將壓力室 4 3 1內之空氣壓力作爲正確地重設爲水噴射開始時之初 期壓力P k期間爲最佳時期。 -25- 554101 五、發明說明（24 ) C 2 — 5 )可得到與第]_實施形態之（χ _ 8 )項之相同 效果。 第3實施形態 茲說明第6圖及第7圖之實施形態說明如下。相關於第 1實施形態相同構成部，使用相同符號而省略其詳細說 明。 在柱塞1 4螺合有螺帽式之位置調整體4 8。在位置調 整體48，相對可轉動地支持活塞32。對於位置調整體 4 8之活塞3 2向軸向之移動，係由一對扣環（snap ring) 49 ’ 5 0所阻止。位置調整體48係藉螺著於柱塞1 4之鎖固螺帽5 1之栓緊，固定於柱塞1 4。 於第4圖之圖表，若欲將柱塞1 4之動作範圍從h 2變 更爲h 1時，就將位置調整體4 8之螺著位置，如鏈線所 示，靠近接頭2 1側即可。藉此螺著位置之變更，密封環 3 4將靠近於密封環3 3。其結果，活塞3 2位於復動終 端位置時之壓縮室3 5之長度Η，將變成較第8圖之實線 位置爲短。 水噴射壓及其梯度（對應於彈簧常數），係具有因應上 述製織條件之最佳値。於習知之水噴射裝置，若變更製織 條件時，能夠適合其所變更之製織條件，必須選擇螺旋彈 簧。但是，螺旋彈簧也有製造上之制約，其長度及彈簧常 數自然就有制約，經常選擇最佳螺旋彈簧係困難之事。又 ，爲了對應種種製織條件，必須準備多種類之螺旋彈簧， -26- 五、發明說明（25) 在成本上及管理上爲不經濟。 於第3實施形態之水噴射裝置，水噴射壓之變更，係如 第1實施形態進行，欲變更水噴射壓之坡度時變更對於柱 塞1 4之位置調整體4 8之螺著位置即可。位置調整體 4 8之螺著位置之變更，係將壓縮室3 5內之壓力減壓到 大氣壓就可容易進行。 第4實施形態 茲說明第9圖之第4實施形態說明如下。相關於第2實 施形態相同構成部，使用相同符號而省略其詳細說明。 在隔膜4 3固定有陰螺旋體5 2，在陰螺旋體5 2螺合 有陽螺旋體5 3。陽螺旋體5 3係藉螺合於陽螺旋體5 3 之鎖固螺帽5 4之栓緊，固定於陰螺旋體5 2。陽螺旋體 5 3係抵接於凸輪桿2 2側之移位傳達體4 6。 於第7圖之圖表，將柱塞1 4之動作範圍從h 4變更爲 h 3時，如陰螺旋體5 2以鏈線所示如能夠靠近空氣彈簧 調整座4 2，只要變更對於陰螺旋體5 2之陽螺旋體5 3 之螺著位置即可。藉此螺著位置之變更，柱塞1 4爲位於 復動終端位置時之隔膜4 3之長度L，將變成較第9圖之 實線位置時爲短。 於第4實施形態之水噴射裝置，欲變更水射壓之梯度時 只要變更對於陰螺旋體5 2之陽螺旋體5 3之螺著位置即 可。陽螺旋體5 3之螺著位置之變更，係將隔膜4 3之壓 力由於減壓到大氣壓程度就可容易進行。 -27- 五、發明說明（26) 按’於本發明也可爲如下之實施形態。例如， (1 )將於第2實施形態之壓力調整閥3 8及電磁開閉閥 4 4所成之初期壓力設定裝置使用於第1實施形態。 (2 )於第1實施形態及第4實施形態，在壓力室4 3 1 內收容螺旋彈簧，發生柱塞1 4之推力由空氣彈簧與螺旋 彈簧分擔。 (3 )於第2實施形態及第4實施形態，在壓力室4 3 1 內收容螺旋彈簧，發生柱塞1 4之推力由空氣彈簧與螺旋 彈簧分擔。於（2 )項及（3 )項，突激波振動之抑制效 果雖然稍爲減少，但是將空氣壓力源3 6之原壓具有低壓 化之益處。 (4 )替代電磁開閉閥4 4，使用同步於織機迴轉而開閉 之機械式開閉閥，以及， (5 )空氣以外之可壓縮之氣體狀之流體，例如使用將鈍 氣（氮氣，二氧化碳等）之壓力作爲彈簧力之流體彈簧裝 置。 圖式之簡單說明 第1 A圖係於第1實施形態之水吸入行程結束即前之水 噴射等裝置之全體圖，第1 B圖係水吸入行程結束即前之 投緯栗之側剖面圖。 第2 A圖係水噴射行程結束即前之水噴射裝置之全體 圖，第2 B圖係水噴射行程結束即前之投緯泵之側剖面 圖。 -28- 554101 五、發明說明（27) 第3圖係表示壓縮室之容積與壓縮室內之壓力關係之圖 表。 第4圖係將封入於壓縮室之空氣重量取爲參數’表示壓 縮室之軸線方向之長度，與其閥之柱塞之推力關係之圖 表。 第5 A圖，第5 C圖及第5 E圖係表示使用習知螺旋彈 簧之水噴射裝置之水噴射壓之變化之量測結果之圖表’第 5 B圖，第5 D圖及第5 F圖係表示使用螺旋彈簧之實施 形態之水噴射裝置之水噴射壓之變化之量測結果之圖表。 第6圖係表示第2實施形態之水噴射裝置之全體圖。 第7圖係表示隔膜之長度，與其閥之柱塞之推力關係之 圖表。 第8圖係表示第3實施形態之投緯泵之側剖面圖。 第9圖係表示第4實施形態之水噴射裝置之要部側剖面 圖。 第10圖係習知之水噴射裝置之全體圖。 第1 1圖係投緯泵1 1之側剖面圖。 第12圖係表示螺旋彈簧之長度與彈簧負荷關係之圖 表。 第13圖係表示織機迴轉角度與凸輪升程量關係之圖 表。 符號簡單說明： 11、29、47…投緯泵 -29- 554101 五、發明說明（28) 12…泵殼 13…貯水室形成壓缸 14…柱塞 15…彈簧板 16…彈簧螺帽 18…螺旋彈簧 17、31、54、283…鎖固螺帽 19、20、39···止回閥 21…接頭 22…凸輪桿 23…凸輪 24···吸入管 25…浮筒 26…排出管 27…投緯噴嘴 28…檔止器 30…壓缸 32…活塞 33、34···密封環 35…壓縮室 36…空氣壓力源 37···空氣管路 38…壓力調整閥 -30- 554101 五、發明說明（29) 40…節流通路 41…壓力計 42···空氣彈簧調整座 43…隔膜 4 4…電磁開閉閥 45、46…移位傳達體 48···位置調整體 49、50…扣環 52、 281…陰螺旋體 53、 282…陽螺旋體 121…吸入口 122…排出口 123…貯水室 151…座部 221…凸輪從動件 222…支軸 23 1…凸輪面 Q1〜Q4…織機回轉角度 -31 -Po = Pa + (F — k. x-m. dx2 / dt2) / A ···· (2) In equation (2), at the beginning of the water injection phase, first, the mass m is rapidly accelerated by the spring force F. Then, when the acceleration is completed, that is, when the inertial force m · dx2 / dt2 is close to zero, the spring force (F — k · X) and the pressure P 0 are sprayed with water while being balanced. During the water spraying process, when the initial displacement X of the water spraying is small, the water spraying pressure is high. On the other hand, when the water jet is restored to the coil spring 18, that is, as the displacement X increases, the water jet pressure P0 gradually decreases. Immediately before the end of the water injection, the water injection pressure P 0 is the lowest value during the water injection period. In addition, when all the water sucked into the water storage chamber 1 2 3 is ejected, the cam follower 2 2 1 collides with the stopper 2 8 or the cam 2 3, and the water ejection pressure P 0 is reduced to atmospheric pressure. This decompression waveform of the water jet pressure P 0 is very suitable for weft insertion of the weft yarn Y. That is, according to the above-mentioned decompression waveform of the water injection pressure P 0 from the weft insertion nozzle 554101 V. Description of the invention (5) 2 7 When water is sprayed, the weft yarn Y is suddenly accelerated at the initial stage of weft insertion, and water is sprayed as the weft passes As the speed decreases, the weft speed will decrease. Therefore, it is possible to prevent the weft yarn from loosening during the water spraying process, and to achieve a stable weft insertion by keeping the posture of the weft yarn Y straight. The water-jet device of the coil spring method having the above-mentioned characteristics has been improved again since the development of the water-jet weft insertion device loom. Therefore, the water-jet device of the coil spring method has been recognized for its reliability and has been adopted to this day. However, it is known that resonance phenomenon called surging occurs in the coil spring, and the sudden shock vibration of the coil spring 18 will adversely affect the weft insertion. That is, when the sudden spring vibration of the coil spring 18 occurs during the water spraying process, the sudden shock vibration of the coil spring 18 is transmitted to the water in the water storage chamber 1 2 3, and the waveform of the water injection pressure P 0 will be as such. The waves changed. The fluctuation of the water jet pressure P 0 caused by the sudden shock vibration of the coil spring 18 will disturb the weft insertion of the weft yarn Y. Distortion of weft yarn Y will reduce fabric quality. Similar to the sudden shock phenomenon of the coil spring 18, the larger the temporal change of the water jet pressure P0, in other words, the higher the number of revolutions of the loom, the more significant. In addition, when the water jet period (= 6 Osec / revolution of loom per minute) is consistent with an integer multiple of the period of the sudden shock vibration, the sudden shock will be excited regularly, causing the vibration of the coil spring 18 It becomes more intense. In order to reduce the sudden shock vibration of the coil spring 18, an attempt is made to attach an attenuation mechanism to the coil spring 18, or Japanese Patent Laid-Open Publication No. Hei 10-554101 5. Invention Description (6) 2 9 9 6 4 3 (Japanese Patent-open No. 10-29 9 643), the use of non-linear springs and the like as the coil spring 18 measures. However, the countermeasure of adding a damping mechanism to the coil spring 18 will complicate the structure and have a problem of high cost. As a countermeasure against the use of a non-linear spring as the coil spring 18, it is difficult to produce a non-linear spring which is effective in suppressing the occurrence of sudden shock vibration. In order to increase the speed of the loom, it is necessary to increase the weft insertion speed of the weft yarn Y, that is, it is necessary to increase the water jet pressure P 0. When the water injection pressure P 0 is to be increased, the compression amount of the coil spring 18 is increased to cope with it. However, if only the compression amount of the coil spring 18 is increased and only the spring load is increased, the strength of the power transmission system such as the coil spring 18 or the cam lever 22 will become insufficient. Therefore, if the size of the power transmission system such as the coil spring 18 or the cam rod 22 is increased, the mass m of the formula (1) will be increased, which will cause the establishment speed of the plunger 14 to decrease. Therefore, the water injection pressure The establishment speed of P0 decreases. If the establishment speed of the water injection pressure P 0 is low, the phenomenon that the water coming out slower first will be overtaken by the water coming out faster later (hereinafter referred to as the "crashing phenomenon"). Disturbances in spray shape are prone to occur. As a result, high-speed water droplets collide with the warp yarns and cause injuries to the warp yarns, and a defect called a warp streak will appear in fabric products. This disadvantage will reduce fabric quality. [Summary of the invention] The object of the present invention is to provide a water jet device that does not reduce 554101. V. Description of the invention (7) The quality of the fabric is reduced, and the water jet weaving loom can be further accelerated. Therefore, the present invention sprays water from the weft-feeding nozzle by feeding water to the weft-feeding nozzle by using a weft-feeding pump, and uses the water-jetting action of the weft-feeding nozzle to spray water from the weft-feeding weft to the weft-jetting device. In addition, the main aspect of the present invention is a water jet device according to the present invention, which is characterized in that the driving source for water jet generation of the weft feeding pump is a fluid using a compressible gas-like fluid pressure as a spring force. Spring device. The fluid spring device is preferably an air spring device in which the pressure of air is used as the spring force. In the above structure, the fluid spring device using the compressible fluid pressure as the spring force has less sudden shock vibration, so the fluctuation of the water jet pressure caused by the sudden shock vibration such as hitting a wave is small. Therefore, the state where the weft insertion of the weft yarn is disturbed by the shock of the shock wave can be improved. In addition, since there is no component of the conventional coil spring, the mass m in the above formula (1) is reduced, and the establishment speed of the water injection pressure can be increased. The weft feeding pump includes a pump casing, a plunger accommodated in the pump casing accommodated in a reciprocating motion, a cam mechanism for driving the plunger in a forward direction, and a plunger for returning The fluid spring device that presses in the moving direction and the water storage chamber separated by the reciprocating movement of the plunger in the pump casing by changing the volume, draw water into the water storage chamber by the movement of the plunger. The repetitive action of the plunger mentioned above. It is preferable that the water in the water storage chamber is pressure-fed to the above-mentioned weft injection nozzle. 554101 V. Description of the invention (8) Because of this structure, when the cam mechanism drives the plunger in the moving direction, water is sucked into the water storage chamber. When the cam mechanism allows the plunger to move in the direction of the double movement, the plunger is doubled by the fluid pressure of the fluid spring device. The conventional spiral spring type weft feeding pump can be transformed into a weft feeding pump according to the present invention by changing and adding a coil spring with a fluid spring device to replace some parts. In addition, the fluid spring device includes a pressure chamber forming shell having a variable volume to form a pressure chamber, and a pressure transmitting device for transmitting the pressure in the pressure chamber to the plunger. The volume of the pressure chamber is provided by the above. The forward motion of the cam mechanism described above can be reduced. Similarly, when the volume of the pressure chamber is increased due to the pressure of the fluid, the plunger will re-operate, and the water in the water storage chamber will be sent to the weft injection nozzle. The pressure transmitting device is a piston coupled to the plunger, and the pressure chamber forms a casing, and it is preferable that a pressure cylinder capable of reciprocating the piston is accommodated in the pump casing. With this configuration, when the piston that separates the pressure chamber in the pressure cylinder moves due to the pressure of the fluid, the plunger moves repeatedly, and the water in the water storage chamber is pressure-fed to the weft injection nozzle. Further, a compression chamber that compresses the fluid with the pressure of the plunger along with the plunger is preferable. Due to this structure, the compression reaction of the fluid compressed in the compression chamber will be used for the double action of the plunger. In addition, there is a quasi-initial pressure setting device required to set the quasi-initial pressure of the fluid spring device. From the quasi-initial pressure, it can be -10- 554101. 5. Description of the invention (9) The fluid in the compression chamber This is the pressure in the compression chamber at the start of compression. With this configuration, the pressure in the compression chamber is compressed from the state of the quasi-initial pressure set by the quasi-initial pressure device. The pressure in the compression chamber of the water jet process will become above the quasi-initial pressure. The stroke of the plunger is constant for each weft insertion. Therefore, the pressure when the fluid in the compression chamber is compressed to the maximum is constant, and the water jet is started according to the state when the fluid in the compression chamber is compressed to the maximum. Moreover, it is preferable to have an initial pressure necessary for setting the initial pressure of the fluid spring device, and it is preferable to set the initial pressure to the pressure in the pressure chamber at the time when water injection is started. According to this configuration, the fluid pressure in the pressure chamber is reset to the initial pressure for each weft insertion, and the fluid compression in the water jet compression chamber starts from the initial pressure state. The pressure in the compression chamber of the water spraying process will be lower than the initial pressure. In addition, the initial pressure device is provided with a pressure setting device for setting a fluid pressure to be supplied to the fluid spring device for a fluid pressure source required for fluid supply by the fluid spring device, and switching a fluid having a pressure set by the pressure setting device. It is a supply switching device that can be supplied to the fluid spring device and cannot be supplied. The switching device can be supplied before the water injection stroke and after the intake water stroke. Before the water ejection stroke and after the water intake stroke, the pressure of the fluid in the pressure chamber is set to -11-554101 as the initial pressure is correctly reset each time we insert the weft. 5. Description of the invention (10) is the best. In addition, the pressure chamber is formed into a shell as a diaphragm connected to the cam mechanism via a displacement transmitting body, and the pressure of the pressure chamber in the diaphragm is transmitted to the plunger through the displacement transmitting body and the cam mechanism. good. Because the structure becomes simple, the durability of the weft-feeding pump can be greatly improved. The cam mechanism side of the plunger is screwed to a position adjustment body that can reciprocate in the axial direction of the plunger, and is installed at the position adjustment. It is also preferable that the above-mentioned piston whose body is relatively rotatable but whose movement in the axial direction is prevented is changed due to a change in the screwing position of the above-mentioned position adjusting body. With this configuration, it is possible to easily change the gradient of the water injection pressure of the water injection device. In addition, the female screw is fixed to the diaphragm, and the displacement transmitting body is used as the male screw screwed to the female spiral body. The initial volume of the pressure chamber can also be changed due to the change in the screwing position of the male spiral body of the female spiral body. . With this configuration, it is possible to easily change the gradient of the water injection pressure of the water injection device. In addition, the pressure chamber formed in the pressure chamber forming case may also accommodate a coil spring. With this configuration, although the suppression effect of the shock wave is slightly reduced, it has the benefit of reducing the original pressure of the air pressure source. • 12- 554101 V. Description of the invention (11) [Embodiments of the invention] The first embodiment The first embodiment of the present invention will be described with reference to Figs. 1 to 5 as follows. The same components of the conventional devices of Fig. 10 and Fig. 11 are designated by the same reference numerals, and detailed descriptions thereof are omitted. As shown in Fig. 1B, a cylinder 30 is screwed into the pump casing 12 constituting the weft feeding pump 29. The pressure cylinder 3 0 is fixed to the pump casing 1 2 by the bolt of the lock nut 31. The cylinder 30 is provided with a piston 32, and the cylinder 13 is housed so as to be slidable if it surrounds the water storage chamber. The piston 3 2 is fixedly connected to the plunger 1 4. The piston 32 and the plunger 14 are integrally movable in the axial direction of the cylinders 30 and 13. A seal ring 3 3 is mounted on the cylinder 30 to be in sliding contact with the outer peripheral surface of the piston 32. A seal ring 34 is attached to the piston 32 to be in sliding contact with the inner peripheral surface of the pressure cylinder 30. A compression chamber 35 is formed between the inner peripheral surface of the cylinder 30 and the outer peripheral surface of the piston 32 and between the seal rings 33 and 34. The compression chamber 35 is connected to an air pressure source 36 via an air pipe 37. The air line 37 is provided with a pressure regulating valve 38 and a check valve 39 which are provided with a release function. Between the pressure regulating valve 38 and the compression chamber 35, a throttle passage 40 and a check valve 39 are provided in parallel. A pressure gauge 41 is connected to the air line 37 between the pressure regulating valve 38 and the check valve 39. The pressure gauge 41 is used to measure the air pressure between the pressure regulating valve 38 and the check valve 39. Between the pressure regulating valve 3 8 and the non-return valve 3 9 -13-554101 V. Description of the invention (12) Air pressure, look at the pressure gauge 4 1 Set the pressure regulating valve 3 8 by operating. The pressure regulating valve 38 having a relief function is the pressure of the air line 37 between the pressure regulating valve 38 and the check valve 39, and the pressure set by the pressure regulating valve 38 is often maintained. The pressure Pi (quasi-initial pressure) in the compression chamber 35 set by the pressure adjustment valve 38 is the pressure when the piston 32 in the compression chamber 35 is positioned on the far right as shown in Fig. 2B. When the cam lever 22 rotates the support shaft 2 2 2 as the center to the right, the plunger 14 and the piston 32 are moved in the forward direction as shown by the arrow Q of the first A and B. When the plunger 14 is moved in the direction of the direction indicated by the arrow Q, the volume in the water storage chamber 1 2 3 increases, and the water in the buoy 25 is sucked into the water storage chamber 1 2 3. When the plunger 32 is moved in the forward direction shown by the arrow Q, the volume of the compression chamber 35 is reduced, and the pressure in the compression chamber 35 is increased from the quasi-initial pressure p i. Starting above the pressure in the compression chamber 35, the check valve 39 will be closed. Thereafter, the pressure in the compression chamber 35 rises as the piston 32 moves forward. When the piston 32 moves forward, the pressure in the compression chamber 35 becomes maximum. The pressure at the beginning of the air compression in the compression chamber 35 is due to the presence of the check valve 39, and is set to the quasi-initial pressure P i set by the pressure regulating valve 38. That is, the pressure in the compression chamber 35 will be maintained at a level higher than the quasi-initial pressure P i set by the pressure regulating valve 38. The curve P b in the graph of FIG. 3 represents the relationship between the volume of the compression chamber 35 and the pressure in the compression chamber 35. When the pressure change shown by the curve Pb in Fig. 3 is expressed by the formula, it will become -14-554101. 5. Description of the invention (13) is as follows. Generally, the change in the actual pressure P when the air is compressed and expanded in an air compressor is expressed as a polytropic change by the following formula (3). Ρ · Υη = — fixed. . . . . . . . . . (3) η in the formula (3) is a polytropic index, and usually η = 1 · 2. If the volume of the compression chamber 35 is reduced from the initial volume V 0 to (Vo — s. Aa), the following formula (4) is established. P (Vo-s-Aa) n = Pi · ν〇η · · (4) In the formula (4), s is the displacement of the piston 32 (s = 0 at the beginning of compression), and Aa is the compression chamber 35. Sectional area. Therefore, the volume of the compression chamber 35 is (Vo — s. The pressure P in the compression chamber 35 at Aa) is represented by the following formula (5). P = Pi · ν〇η / (ν〇-8 * Aa) n · (5) That is, the curve "Pb" of Fig. 3 is expressed by the formula (5). When the displacement amount s increases, that is, when the volume of the compression chamber 35 decreases, the pressure P in the compression chamber 35 is as shown by the arrow U 1 in FIG. 3 and increases along the curve p b. The pressure Pm in FIG. 3 is the pressure when the volume (Vo — s · Aa) of the compression chamber 35 is the minimum. When the cam follower 2 2 1 passes the maximum diameter position Ma of the cam surface 2 3 1 of the cam 2 3, the cam lever 2 2 rotates the plunger 14 and the piston 3 2 to the right with the support shaft 2 2 2 as the center. Due to the pressure Pm of the compressed air in the compression chamber 35, it moves in the direction of the double movement indicated by the arrow R of 2A and B. If the plunger 14 is moved in the direction of the double movement indicated by the arrow R, the water in the water storage chamber 1 2 -15- 554101 V. Description of the invention (14) 3 will be pressurized. The pressurized water in the water storage chamber 1 2 3 is pressure fed to the weft insertion nozzle 27. The water that is pressure-fed to the weft injection nozzle 27 is ejected from the weft injection nozzle 27. On the other hand, the displacement amount s decreases, that is, when the volume of the compression chamber 35 increases, the pressure P in the compression chamber 35 is as shown by the arrow U 2 in FIG. 3 and decreases as shown along the curve P b Pressure. As shown by the arrow U 2 in Fig. 3, the air pressure in the compression chamber 35 along the curve P b is the water injection pressure of the weft injection nozzle 27. The following effects can be obtained in the first embodiment. (1-1) The curves Cl, C2, and C3 in the graphs of Figs. 5A, 5C, and 5E show the measurement results of the changes in the water injection pressure of the water injection device using a conventional coil spring. The curves El, E2, and E3 in the graphs of Figures 5B, 5D, and 5F show the use of the air spring device composed of the cylinder 30, the piston 32, the seal rings 33, 34, and the compression chamber 35. The measurement results of the water jetting pressure of the water jetting device according to the embodiment. Figures 5A and 5B show the situation where the number of revolutions of the loom is 7 0 0 r pm, Figures 5 C and 5D show the situation where the number of revolutions of the loom is 800 r pm, Figures 5 E and 5F The picture shows the case where the number of revolutions of the loom is 1000 rpm. When the weaving machine speed is 700 rpm, the conventional water jet device using a coil spring as a driving source for generating water jet pressure is used for the weft feeding pump, and the air spring device is used as a driving source for generating water jet pressure when the weft feeding pump is used. In the water spraying device of this embodiment, it is not observed that the magnitude of the vibration caused by the sudden shock is -16- V. Description of the invention (15) Wave changes caused. When the number of loom revolutions is 8 0 0 r pm, as shown in Fig. 5D, in the water spraying device of this embodiment, although the wave caused by the sudden shock vibration is not observed to cause the wave to change greatly, however, if As shown in Fig. 5C, in the conventional water spray device, the wave variation caused by the sudden shock vibration will become significant. When the number of revolutions of the loom becomes 1 000 r pm, as shown in Fig. 5E, in the conventional water jet device, the wave change caused by the sudden shock vibration will become more significant. However, as shown in Fig. 5F, in the water spraying device of this embodiment, even if the number of revolutions is 100 rpm, no large wave variation due to sudden shock vibration is observed. When the air pressure of a compressible fluid is used as a spring air spring device, its sudden shock vibration is much less than that of a coil spring. Therefore, the fluctuation of large waves caused by the water jet pressure due to the shock of the shock wave is small. The sudden shock vibration that occurs when a coil spring is used, although the higher the number of revolutions of the loom becomes, the more significant it becomes. However, when the water jet device of this embodiment of the air spring device is used, even if the number of revolutions of the loom becomes 1 0 0 0 r pm At high speeds, no sudden shock vibration occurred. Therefore, even in a high-speed turning state such as 1 00 r pm, the weft insertion operation of the stable weft yarn Y can be performed. The stable weft insertion of the weft Y running at high speed on the loom will not impair the quality of the fabric. (1-2) The mass m in the above formula (1) is the total mass of the equal mass of the movable body of the power transmission system. Therefore, the smaller the mass m is, the higher the initial speed of the plunger 14 during the double movement, that is, the rising speed of the water jet pressure. In -17- 554101 V. Description of the invention (16) The water spraying device of this embodiment without a coil spring is a water spraying device using a coil spring, and the mass m of the above formula (1) will be smaller. The decrease in mass m due to the absence of a coil spring will increase the raising speed of the water jet pressure and suppress the occurrence of the "catching-up phenomenon" of the water jet. Therefore, disturbance of the spray shape of the water jet apex caused by the "catching phenomenon" of the water jet can be suppressed. As a result, it is possible to avoid high-speed water droplets conflicting with warp yarns and damaging the warp yarns, and it is possible to avoid degradation of fabric quality caused by warp str eaks. (1-13) Weft-feeding pump 2 9 is equipped with: pump casing 12 with water storage chamber 1 2 3; plunger 14; pressure cylinder 13 formed with water storage chamber; air spring device; with lock nut 17; joint 21 , Cam mechanism formed by cam 23 and cam lever 22. The conventional weft feeding pump 11 in Figs. 10 and 11 is provided with: a pump casing 12 having a water storage chamber 123; a plunger 14; the water storage chamber forming a pressure cylinder 13; a spring plate 15; a spring cap A cam mechanism formed by a cover 16; a locking nut 17; a joint 21; a cam 23 and a cam lever 22. The air spring device of the weft insertion pump 29 is composed of a pressure cylinder 30 and seal rings 33 and 34. The spring plate 15 constituting the weft-feeding pump 11 can be transferred to the piston 32 constituting the weft-feeding pump 29. In addition, the pump casing 12, plunger 14, and water storage chamber constituting the conventional weft feeding pump 11 are formed into a pressure cylinder 13, a lock nut 17 and a cam mechanism, which can still be used as components of the weft feeding pump 29. That is, the conventional spiral spring type weft feeding pump 11 is a spring cap -18-554101 V. Description of the invention (17) 16 is changed to a pressure cylinder 3 0, and a seal ring 3 3, 3 4 is added. With a few changes and additions of parts, it can be transformed into the weft casting pump 29 of the present invention. (1-4) Although the change in the water injection pressure obtained by the water injection device of this embodiment is shown in Fig. 3, the pressure gradient of the time change during the water injection stroke can be expressed by the following formula (6) Means. dP / dt = (dP / ds) (ds / dt) · · · (6) The pressure gradient d P / dt of the conventional water spray device using coil spring 18 is when there is no disturbance on the right 'It shows no more linear changes. In addition, when the pressure gradient dP / dt of this embodiment using the air spring device is dP / ds when considering the curve obtained by differentiating the equation (5) by the shift amount s, what is the design of the compression chamber 35? , Can also achieve a change from a straight line to leave. As a result, in the air spring pump, by changing the air pressure or the volume of the air chamber, the non-linear characteristics of the air spring can be used to change the spring force or the gradient of the spring force, thereby corresponding to various weaving conditions (for example, weaving Width, weft type, weaving machine speed, etc.), and water jet pressure can be achieved in a wide range of conditions. (1-15) The curves Pbl, Pb2, Pb3, Pb4, Pb5 in the graph in Figure 4 are the parameters of the weight of the air enclosed in the compression chamber 35, which represents the length in the axial direction of the compression chamber 35. 1B and 2B), and the load of the piston 32 (that is, the thrust of the plunger 14) at that time. The air weights on the curves Pbl, Pb2, Pb 3, Pb 4, and Pb 5 decrease in this order. That is, the initial air-sealing pressure in the compression chamber 35 (the quasi-initial pressure P i set by the pressure regulating valve-19-554101 V. Invention Description (18) 38) is based on the curves Pb 1, Pb2, Pb3, The order of Pb4 and Pb5 becomes lower. When the weight of the air enclosed in the compression chamber 35 is below a certain level (the example shown in the figure is the curve Pb4), take the axial length 压缩 of the compression chamber 35 as the short one, and select the action range of the piston 3 2, that is, the plunger 1 When the operating range of 4 (the example shown in the figure is h 1), the thrust of the plunger 14 and the gradient of the change of the plunger 14 will increase. Conversely, taking the length in the axial direction 压缩 of the compression chamber 35 as the elder and selecting the action range of the plunger 14 (the example shown in the figure is h2), the thrust of the plunger 14 and the gradient of the change to the plunger 14 will become smaller. If the weight of the air enclosed in the compression chamber 35 is increased, the thrust level of the plunger 14 will increase as a whole. When the weight of the air enclosed in the compression chamber 35 is increased, the gradient of the change in the thrust of the plunger 14 becomes larger. This is based on the action range h2 shown in the figure, for example, comparing the slopes of the curves Pbl, Pb2, Pb3, Pb4, and Pb5. The selection of the magnitude or thrust gradient of the plunger 14 can be selected based on the non-linear characteristics of the air spring of the air spring device. That is, the water spraying device of this embodiment using the air spring device can achieve a wide range of water jetting pressures in accordance with various weaving conditions (for example, weaving width, weft type, weaving machine speed, etc.). (1 to 6) The conventional water spray device using a coil spring 18 is shown in Fig. 12 and the water spray pressure can be changed by the load of the coil spring 18. To adjust the screw-in position of the spring cap 16 of the pump casing 12, it is necessary to adjust the initial compression amount. Adjust the weft insertion condition here, for example -20- 554101 V. Description of the invention (19) To observe using a stroboscope, it is necessary to repeatedly adjust the screw-in position of the spring cap 16 according to its observation status Homework. The adjustment of the screw-in position of the spring cap 16 must be a troublesome operation to accept the strong spring load of the coil spring 18. In the water injection device of this embodiment, when the water injection pressure is to be changed, the pressure adjustment valve 38 is operated to adjust the quasi-initial pressure P i in the compression chamber 35, and this pressure adjustment operation is easy. (1-7) The non-return valve 3 9 has the function of blocking the communication between the pressure regulating valve 38 and the compression chamber 35 when compressing the air in the compression chamber 35, and limiting the minimum pressure of the compression chamber 35 (also That is, the function of the quasi-initial pressure P i) set by the pressure regulating valve 38 and the function of supplementing the amount of leaked air when the air leaks from the compression chamber 35. It is assumed that the sealing function according to the sealing rings 3 3, 3 4 is complete. When there is no air leakage from the compression chamber 35, unless the pressure regulating valve 3 8 is operated, the air in and out of the check valve 39 during non-loom operation is checked. The valve 39 is only used as a stop valve. If there is no air leakage from the compression chamber 35, the pressure in the compression chamber 35 can be increased even by the operation of the pressure regulating valve 38, and cannot be reduced by the action of the check valve 39. The throttle path 40 is to actively leak the air in the compression chamber 35 to the pressure regulating valve 38 side. A configuration in which a throttle passage 40 is installed in parallel with the check valve 39 is that if the sealing mechanism of the seal rings 3 3 and 34 can fully function, the compression chamber 35 can be decompressed. This decompression structure can be set in the near initial stage of the compression chamber 35 -21-554101 V. Description of the invention (20) Pressure Pi. The air pressure source 36, the pressure regulating valve 38, the check valve 39, and the throttle passage 40 are quasi-initial pressure setting devices used for the initial pressure set by the fluid spring device. The air in the compression chamber 35 is compressed from the state of the quasi-initial pressure P i set by the quasi-initial pressure setting device. The pressure in the compression chamber 35 during the water injection process will become higher than the quasi-initial pressure P i. Since the stroke of the plunger 14 is constant for each weft insertion, the pressure when the air in the compression chamber 35 is compressed to the maximum is always kept constant. Therefore, the water jet is started under the pressure Pm when the air in the compression chamber 35 is compressed to the maximum. The water injection pressure at the initial stage of water injection always meets the pressure Pm which is higher than the quasi-initial pressure P i set by the pressure regulating valve 38. The water injection pressure during the water injection process will be lower than the pressure Pm and higher than P i Range. Therefore, it is possible to indirectly control the pressure at the beginning of water spraying, which is an important factor in terms of toft, and it is possible to adjust the water spraying pressure with high accuracy. (1-8) The principle is similar to that of a water-jet weft-jet weaving loom, which responds to the weft-throwing condition of the weft yarn by applying feedback control to the air-pressure for weft-injection weaving. . This kind of automation is to adjust the work of liberating the operator from the pressure of trouble, which can greatly improve the efficiency of the operation. This is a method of weaving air-injection weft looms. The original method is to directly adjust the injection pressure of air for weft-injection using a pressure adjustment valve. This is because it is easier to electrically control the pressure adjustment valve. Even in this embodiment, the pressure control valve 38 is also electrically controlled, and feedback control can be applied in response to the weft insertion condition. -22- 554101 V. Description of the Invention (21) Second Embodiment The following describes the embodiments of FIGS. 6 and 7. Regarding the same constituent parts of the first embodiment, the same reference numerals are used and detailed descriptions thereof are omitted. As shown in FIG. 6, a rubber diaphragm (diaphragm) 4 3 is attached to the air spring adjusting seat 4 2. Displacement transmitting bodies 45 and 46 are fixed to the diaphragm 4 3 and the cam lever 2 2. The displacement transmitting bodies 45 and 46 are in contact with each other, and the pressure in the pressure chamber 4 3 1 in the diaphragm 4 3 is transmitted to the plunger 14 through the displacement transmitting bodies 45 and 46, the cam lever 22 and the joint 21. The weft feeding pump 4 7 in the second embodiment removes the pressure cylinder 30 and the piston 32 constituting the weft feeding pump 29 in the first embodiment. The pressure chamber 4 3 1 in the diaphragm 4 3 is connected to an air pressure source 36 through an air pipe 37. On the air pipe 37, a pressure regulating valve 38 and an electromagnetic on-off valve 4 4 are installed. A pressure gauge 41 is connected to the air line 37 between the pressure regulating valve 38 and the electromagnetic on-off valve 44. The diaphragm 4 3 series will be a pressure chamber forming case constituting the air spring device. The electromagnetic on-off valve 4 4 is a short period immediately before the start of water injection (the period shown by T in FIG. 13), and is turned on by excitation. The initial pressure P k set by the pressure regulating valve 38 is supplied to Pressure chamber 4 3 1 in diaphragm 4 3. The electromagnetic on-off valve 4 4 is a supply switching device that switches the pressure air set by the pressure regulating valve 38 of the pressure setting device into a state where it can be supplied to the fluid spring device and is switched to a state where it cannot be supplied. The electromagnetic opening / closing valves 4 and 4 belonging to the switching device are in a state where they can be supplied from the excitation before the water injection stroke and after the water suction stroke. -23- 554101 V. Description of the Invention (22) The second embodiment has the following effects. (2-1) The water injection pressure at the initial stage of water injection always conforms to the initial pressure P k set by the pressure regulating valve 38, and the water injection pressure during the water injection process will be in a range below the initial pressure p k. Therefore, it is possible to directly control the initial pressure at the beginning of water jetting, which is an important factor for weft insertion. Water jet pressure can be adjusted with very good accuracy. Press, the air pressure source 36 of the fluid pressure source, the pressure regulating valve 38 and the electromagnetic on-off valve 4 4 with the pressure relief function are the initial stages of the initial pressure of the fluid spring device that sets the start of each water injection. Pressure setting device. (2-2) Since the seal rings 33 and 34 of the first embodiment are not needed, the durability of the cast weaving chestnut 47 is significantly improved compared with the cast weaving chestnut 29 of the first embodiment. (2-3) The curves Pci, Pc2, Pc3, and Pc4 in the graph in Figure 7 are in a state where the load on the plunger 14 is zero (that is, the cam follower 2 2 1 is on the cam surface The state of the maximum diameter position Ma of 2 3 1) The air pressure enclosed in the diaphragm 4 3 is used as a parameter to indicate the length L of the diaphragm 43 (illustrated in Fig. 6), and the load of the piston 32 at that time (that is, the plunger) 14 thrust). The air pressure levels on the curves P c 1, P c 2, P c 3, and P c 4 decrease in this order. That is, the initial air-sealing pressure (the initial pressure Pk set by the pressure regulating valve 38) at the diaphragm 43 is lowered in the order of the curves Pel, Pc2, Pc3, and Pc4. When the air pressure enclosed in the diaphragm 4 3 is constant (the example shown in the figure is -24-554101 V. Description of the invention (23) curve Pc3), take the short diaphragm 43 length L and select the action range of the plunger 14 (The example in the figure is h 3), not only the thrust of the plunger 14 becomes larger, but also the gradient of its change becomes smaller. Conversely, when the length L of the long diaphragm 4 3 is selected and the operating range of the plunger 14 is selected (h4 in the figure example), not only the thrust of the plunger 14 is reduced, but also the slope of the change is increased. When the initial pressure P k supplied to the pressure chamber 4 3 1 inside the diaphragm 43 is increased, the thrust level of the plunger 14 is increased as a whole. When the initial pressure P k supplied to the diaphragm 43 is increased, the gradient of the change in the thrust of the plunger 14 becomes larger. This is, for example, the action range h 4 shown in the figure, and the gradients of the curves Pci, Pc2, Pc3, and Pc4 can be compared clearly. The choice of the magnitude or thrust gradient of the plunger 14 is made possible by the non-linear characteristics of the air spring provided to the pressure chamber 4 3 1 in the diaphragm 4 3 constituting the air spring device. In other words, even in the water jetting device of the second embodiment, it is possible to realize a water jetting pressure that can be used in a wide range of conditions for various weaving conditions. (2-4) The period of time T before the start of water injection is the period before the water injection stroke and after the water suction stroke. During this period, when the volume in the pressure chamber 4 3 1 is the smallest, the air pressure in the pressure chamber 4 3 1 when the volume in the pressure chamber 4 3 1 is the smallest is reset to the initial pressure P k every time the weft is inserted. Therefore, the air pressure in the pressure chamber 431 is reset to the period before the water injection stroke and after the water suction stroke is correctly reset to the period of the initial pressure P k at the beginning of the water injection. -25- 554101 V. Description of the invention (24) C 2-5) The same effect as the item (χ _ 8) of the embodiment] _ can be obtained. (Third Embodiment) The embodiments shown in Figs. 6 and 7 will be described below. Regarding the same constituent parts of the first embodiment, the same reference numerals are used and detailed descriptions thereof are omitted. A nut-type position adjusting body 4 8 is screwed on the plunger 14. At the position adjustment unit 48, the piston 32 is relatively rotatably supported. The axial movement of the piston 32 of the position adjustment body 48 is prevented by a pair of snap rings 49'50. The position adjusting body 48 is fixed to the plunger 14 by screwing on the bolt of the locking nut 51 of the plunger 14. In the graph in Figure 4, if you want to change the operating range of the plunger 14 from h 2 to h 1, the screw position of the position adjustment body 4 8 is shown near the side of the connector 2 as shown by the chain line. can. With this change in screw position, the seal ring 3 4 will be closer to the seal ring 3 3. As a result, the length Η of the compression chamber 35 when the piston 32 is located at the double-acting end position becomes shorter than the solid line position in FIG. 8. The water jet pressure and its gradient (corresponding to the spring constant) are optimally suited to the above-mentioned weaving conditions. In the conventional water spray device, if the weaving conditions are changed, the weaving conditions can be adapted to the changed weaving conditions, and a coil spring must be selected. However, coil springs also have manufacturing constraints. Naturally, there are constraints on the length and spring constant. It is often difficult to choose the best coil spring system. In addition, in order to cope with various weaving conditions, various types of coil springs must be prepared. -26- V. Description of the Invention (25) It is uneconomical in terms of cost and management. In the water jetting device of the third embodiment, the water jetting pressure is changed as in the first embodiment. When the gradient of the water jetting pressure is to be changed, the screwing position of the position adjusting body 4 8 for the plunger 1 4 may be changed. . Changing the screwing position of the position adjusting body 48 can be easily performed by reducing the pressure in the compression chamber 35 to atmospheric pressure. Fourth Embodiment The fourth embodiment of Fig. 9 is described below. Regarding the same constituent parts of the second embodiment, the same reference numerals are used and detailed descriptions thereof are omitted. A female spiral body 5 2 is fixed to the diaphragm 4 3, and a male spiral body 5 3 is screwed to the female spiral body 5 2. The male spiral body 5 3 is fixed to the female spiral body 5 2 by screwing on the locking nut 54 of the male spiral body 5 3. The male spiral body 5 3 is a displacement transmitting body 46 which abuts on the cam lever 22 side. In the graph of Fig. 7, when the operating range of the plunger 1 4 is changed from h 4 to h 3, as shown in the female spiral body 5 2 as a chain line, if it can be close to the air spring adjusting seat 4 2, as long as the female spiral body 5 is changed, The male screw body 5 3 can be screwed on. With this change in screwing position, the length L of the diaphragm 4 3 when the plunger 14 is in the double-acting end position will become shorter than that in the solid line position in FIG. 9. In the water ejection device of the fourth embodiment, when the gradient of the water injection pressure is to be changed, the screwing position of the male spiral body 5 2 and the male spiral body 53 may be changed. The screwing position of the male spiral body 53 can be easily changed by reducing the pressure of the diaphragm 43 to the atmospheric pressure. -27- V. Description of the invention (26) According to the invention, the following embodiments can be adopted. For example, (1) the initial pressure setting device formed by the pressure regulating valve 38 and the electromagnetic on-off valve 44 of the second embodiment is used in the first embodiment. (2) In the first and fourth embodiments, a coil spring is housed in the pressure chamber 4 3 1, and the thrust of the plunger 14 is shared by the air spring and the coil spring. (3) In the second embodiment and the fourth embodiment, a coil spring is housed in the pressure chamber 4 3 1, and the thrust of the generated plunger 14 is shared by the air spring and the coil spring. In items (2) and (3), although the suppression effect of the shock shock is slightly reduced, the original pressure of the air pressure source 36 has the benefit of reducing the pressure. (4) Instead of the electromagnetic on-off valve 44, use a mechanical on-off valve that opens and closes synchronously with the loom's rotation, and (5) a compressible gaseous fluid other than air, such as using inert gas (nitrogen, carbon dioxide, etc.) The pressure of the spring acts as a fluid spring device. Brief description of the drawings. Figure 1A is an overall view of a water jet and other devices immediately before the end of the water suction stroke of the first embodiment, and Figure 1B is a side sectional view of the thrown chestnut immediately before the end of the water suction stroke. . Fig. 2A is an overall view of the water jetting device immediately before the end of the water jetting stroke, and Fig. 2B is a side sectional view of the weft feeding pump immediately before the end of the water jetting stroke. -28- 554101 V. Description of the invention (27) Figure 3 is a graph showing the relationship between the volume of the compression chamber and the pressure in the compression chamber. Fig. 4 is a graph showing the relationship between the length of the compression chamber in the axial direction and the thrust of the plunger of the valve by taking the weight of the air enclosed in the compression chamber as a parameter. 5A, 5C, and 5E are graphs showing measurement results of changes in water injection pressure of a water injection device using a conventional coil spring, FIG. 5B, FIG. 5D, and FIG. 5 Figure F is a graph showing the measurement results of changes in the water jet pressure of the water jet device using the coil spring. Fig. 6 is an overall view showing a water spraying device according to a second embodiment. Fig. 7 is a graph showing the relationship between the length of the diaphragm and the thrust force of the plunger of the valve. Fig. 8 is a side sectional view showing a weft feeding pump according to a third embodiment. Fig. 9 is a side sectional view of a main part of a water spraying device according to a fourth embodiment. Fig. 10 is a general view of a conventional water spraying device. Fig. 11 is a side sectional view of the weft feeding pump 11; Fig. 12 is a graph showing the relationship between the length of the coil spring and the spring load. Fig. 13 is a graph showing the relationship between the rotation angle of the loom and the cam lift amount. Brief explanation of symbols: 11, 29, 47 ... Weft-feeding pump-29- 554101 V. Description of the invention (28) 12 ... Pump casing 13 ... Water storage chamber forms pressure cylinder 14 ... Plunger 15 ... Spring plate 16 ... Spring nut 18 ... Coil springs 17, 31, 54, 283 ... Locking nuts 19, 20, 39 ... Check valve 21 ... Joint 22 ... Cam lever 23 ... Cam 24 ... Suction tube 25 ... Float 26 ... Discharge tube 27 ... Weft insertion nozzle 28 ... stop 30 ... cylinder 32 ... piston 33,34 ... seal ring 35 ... compression chamber 36 ... air pressure source 37 ... air line 38 ... pressure regulating valve -30-554101 Description of the invention (29) 40 ... throttle path 41 ... manometer 42 ... air spring adjusting seat 43 ... diaphragm 4 4 ... electromagnetic on-off valve 45,46 ... shift transmission body 48 ... position adjustment bodies 49, 50 ... Buckles 52, 281 ... Female spiral body 53, 282 ... Male spiral body 121 ... Suction port 122 ... Discharge port 123 ... Water storage chamber 151 ... Seat 221 ... Cam follower 222 ... Support shaft 23 1 ... Cam surface Q1 ~ Q4 ... Loom Swing angle -31-