507033 五、發明説明（1 ) 之領域 本發明是關於一種可進行壓力流體之流量調節的節流閥 。本發明係適於一種有關投緯裝置，將開閉閥介於投緯用 噴嘴或投緯路徑上配置之輔助噴嘴爲止之流體通路上之間 ’由切換該開閉閥之開閉進行對該投緯用噴嘴或者輔助噴 嘴之壓縮空氣的供給或停止供給，依該開閉閥的開狀態之 該投緯用噴嘴或輔助噴嘴的壓縮空氣噴射作用，在緯紗作 投緯的噴氣織機，採用上述節流閥。 兔前之技術說明 例如，在噴氣織機中如第1圖所示，從壓縮機等壓力源 1之壓縮空氣’經由配置在第一管路3中的減壓閥2調整 爲設定壓力之後，導入壓縮空氣供給槽4，儲存在此壓縮 空氣供給槽4。在此，壓力源1、減壓閥2、第一管路3及 壓縮空氣供給槽4總稱爲壓縮空氣源。壓縮空氣從壓縮空 氣供給槽4經由第二管路5，由節流閥6調節流量後，藉 由電磁開閉閥7形成適當地供給到投緯用噴嘴8。 緯紗由壓縮空氣，從投緯用噴嘴8噴射於經紗開口內。 此時，爲了使緯紗之前端到達織端爲止之時間成爲一定， 必須對應於緯紗種類或各種運轉狀況，使自投緯用噴嘴8 所噴射之壓縮空氣流量需要經由電磁開閉閥7適當地作言周 節。 於是，日本特開平4-214442號公告所揭示之投緯裝置 中，提案有如次之節流閥裝置。亦即，於此習知裝置，如 第2圖所示，由壓縮空氣源經管路10所導之壓縮空氣，507033 V. Field of invention description (1) The present invention relates to a throttle valve capable of regulating the flow rate of a pressure fluid. The present invention is suitable for a weft insertion device, in which an opening / closing valve is interposed between a nozzle for a weft insertion or an auxiliary nozzle disposed on a weft insertion path, and the weft insertion is performed by switching the opening and closing of the opening and closing valve. The supply or stop of the compressed air of the nozzle or the auxiliary nozzle depends on the compressed air ejection action of the weft-injection nozzle or the auxiliary nozzle in the open state of the on-off valve. The air-jet loom used as the weft injecting weft adopts the aforementioned throttle valve. For example, in the air-jet loom, as shown in FIG. 1, compressed air from a pressure source 1 such as a compressor is adjusted to a set pressure through a pressure reducing valve 2 arranged in a first line 3 and then introduced. The compressed air supply tank 4 is stored in the compressed air supply tank 4. Here, the pressure source 1, the pressure reducing valve 2, the first line 3, and the compressed air supply tank 4 are collectively referred to as a compressed air source. The compressed air is supplied from the compressed air supply tank 4 through the second pipe 5 and adjusted by the throttle valve 6, and is then appropriately supplied to the weft insertion nozzle 8 through the electromagnetic on-off valve 7. The weft yarn is sprayed into the warp yarn opening from the nozzle 8 for weft insertion by compressed air. At this time, in order to make the time from the front end of the weft yarn to the weaving end constant, the flow rate of the compressed air sprayed from the weft-feeding nozzle 8 needs to be appropriately described according to the type of weft yarn or various operating conditions. Week Festival. Therefore, among the weft insertion devices disclosed in Japanese Unexamined Patent Application Publication No. 4-214442, a proposal is as follows as a throttle device. That is, in this conventional device, as shown in FIG. 2, the compressed air guided by the compressed air source through the pipe 10,
507033 五、發明説明(2 ) 從閥孔13進入管路11中，從此處通過閥孔14後，藉由 管路1 2送到噴嘴。 閥體15配設爲與閥孔13面對，閥16配設爲與閥孔14 面對。閥體15爲具有傾斜之切斷面17之圓柱狀。在管路 1 〇內以軸心爲中心來轉動調節，在與閥孔1 3面對的閥體 1 5之側面，調節該閥孔1 3之開度。並依此開度調節，予 以調節壓縮空氣之流量。此時，閥體1 5之轉動角度與流 路之有效剖面積間的關係，成爲如第3A圖之曲線。對應 於此，閥體1 5之轉動角度與投緯用噴嘴8之入口部壓力 的關係，成爲如第3B圖之曲線。又，閥孔14由電磁線圈 1 8作動的閥1 6作適當地開閉。 然而，在此習知技術中，以閥體15部分的閉塞閥孔13 之際，對壓縮空氣之流動成爲堤壩之部分，在其前後急遽 地變化流路剖面積。因此，堤壩產生之壓損變大，其結果 ，有在噴嘴8之入口萍難獲得充分高度的靜壓之問題點。 又，由於縮流之關係，產生比依實際的堤壩更大的閉塞狀 態，亦有壓縮空氣之流量調節精度降下之問題點。再者， 流體通路之屈曲大，亦使上述問題點更加顯著者。 發明之扼要說明 本發明係著眼於如上述習知技術所存在之問題點實施者 。因而，本發明之主要目的在於提供一種節流閥，不僅其 壓力損失少、流量調節容易，而且精度高。 又另外之目的在提供一種具備如此之節流閥，在噴氣織 機中的投緯裝置。 -4- 507033 五、發明説明（3 ) 爲了達成上述目的，依有關本發明之主要局面，節流閥 ，其特徵爲具有，與流體通路垂直相交所穿設之閥孔，及 ***該閥孔以軸心爲中心而可轉動調節之閥體，在對應該 閥體之該流體通路之開口部的位置外周面，形成有深度沿 著外周方向連續地變化之凹刻部。 依本發明，因在節流部分之流路剖面積之變化平穩，故 壓力損失少、並不易引起縮流，而且流路剖面積之變化對 閥體之轉動角度爲具有直線性之故，變成容易進行流量調 節。 該凹刻部之深度，愈朝向外周方向漸漸變深之後，形成 漸漸地淺爲理想。在節流部分之流路剖面積之變化，變成 更爲圓滑，壓力損失變少。 又，該凹刻部，對該閥體之軸心成偏心之軸心爲中心所 形成之部份圓錐的組合構成爲較佳。並依如此的構成，該 閥體之凹刻部以車床之簡單的機械加工，就能容易地形成。 再者，使該閥體爲圓柱狀，此圓柱狀之該閥體的外周面 形成有該凹刻部，對應於該閥體之旋轉的該凹刻部之軌跡 ，與該流體通路形成交叉爲理想。隨著圓柱狀之閥體的旋 轉之通過剖面積變化，可使其更爲平穩。 再者，又配設具備以電氣的旋轉驅動之輸出軸的致動器 ，將該閥體安裝在該致動器之該輸出軸時，亦可作轉動調 節。並由此，使該閥體之轉動調節變成可自動化。 又，該閥孔之中心軸，係配置在對該流體通路之中心軸 成偏心的位置爲理想。依如此的構成，即使節流流量爲 507033 五、發明説明（4 ) 最大狀態時，亦可經常確保於某大小之流路。 依有關本發明之另一局面，於噴氣織機中的投緯裝置， 其特徵爲具有如上述的節流閥，同時該流體通路，爲連結 於噴氣織機經壓力調整的壓縮空氣源，及噴射該壓縮空氣 之噴嘴的流體通路者。 依本發明，如上所述之節流閥的作用，可在噴氣織機來 享受。亦即，在噴氣織機中因應於所使用緯紗之種類或投 緯之狀態，變成可作細緻的壓力調整，故可提高投緯功能 ，同時亦可聯繫於壓縮空氣消費量之減低。 又，依本發明之再另一局面，該噴嘴爲用以投緯緯紗之 投緯用噴嘴，又於該噴氣織機的投緯裝置，再以連結該壓 縮空氣源與該投緯用噴嘴而配設在該流體通路上的開閉閥 ，並由該開閉閥之切換開閉進行對該投緯用噴嘴之該壓縮 空氣的供給及停止供給，在該開閉閥之開狀態中，由該投 緯用噴嘴之壓縮空氣噴射作用，具有投緯該緯紗的開閉閥 ，在每一個投緯循環中，對應於該開閉閥之開閉時序，用 來控制該節流閥之節流狀態。 在噴氣織機中，投緯用噴嘴之噴射壓力下降特性會對緯 紗之投緯狀態給予影響。關閉控制對投緯用噴嘴之壓縮空 氣的供給及停止的開閉閥時，在投緯用噴嘴之噴射壓力急 遽地降下。因此，由紗種類使緯紗振動而容易產生顫抖或 鬆弛。緯紗產生顫抖或鬆驰係帶來織布品質之降低。 投緯用噴嘴中爲了避免噴射壓力急遽地降下，在投緯用 噴嘴之噴射結束之際，對電磁開閉閥輸出脈衝列之驅動信 -6- 507033 五、發明説明（5 ) 號，使電磁開閉閥以小刻度地開閉，有使投緯用噴嘴之噴 射結束之時的噴射壓力慢慢地降下的方法。 可是，欲使電磁開閉閥以小刻度地開閉時，必須使用可 高速動作的電磁開閉閥。使用這種電磁開閉閥時，其壽命 比先前所使用之標準應的答性能之電磁開閉閥大幅度地縮 短。 本發明不必使用可非常地高速動作之電磁開閉閥，可改 良在投緯用噴嘴之噴射壓力特性。投緯用噴嘴之噴射壓力 特性可與開閉閥另外之節流閥選擇節流狀態來調整。因而 ，不需要用以獲得所希望噴射壓力特性之極高速動作之開 閉閥。 又，具有控制裝置爲理想，其可在每一個投緯循環中對 應於該開閉閥之開閉時序以控制該節流閥之節流狀態爲理 想。可更簡單地進行調整節流閥之節流狀態。 再者，該節流閥配設在該開閉閥之上游側較佳。開閉閥 之上游側，爲了避免在使開閉閥下游之殘壓狀態之長期化 上，作爲節流閥之配置地點合適。 再者，又可使該投緯用噴嘴，至少作爲投緯用主噴嘴或 者投緯用輔助噴嘴之一側。 圖式之簡單說明 第1圖是顯示噴氣織機中的壓縮空氣之送給路徑說明圖 第2圖是顯示習知裝置的節流閥裝置之說明圖； 第3 A圖是顯示習知裝置中閥體之角度與流路有效剖面 507033 五、發明説明（6 ) 積之關係曲線圖，第3B圖是顯示閥體之角度與壓力效率 之關係曲線圖； 第4圖是本發明第1實施形態中其節流閥之局部剖面正 面圖（在節流狀態）； 第5圖是節流閥之局部剖面正面圖（在放開狀態）； 第6圖是節流閥之局部剖面平面圖（在放開狀態）； 第7圖是節流閥之局部剖面平面圖（在局部放開狀態）； 第8圖是節流閥之局部剖面平面圖（在節流狀態）； 第9A圖是顯示閥體之角度與流路有效剖面積之關係曲 線圖，第9B圖是顯示閥體之角度與壓力效率之關係曲線 圖；507033 V. Description of the invention (2) Enter valve 11 from valve hole 13 and pass through valve hole 14 from here, and then send it to nozzle through pipe 12. The valve body 15 is arranged to face the valve hole 13, and the valve 16 is arranged to face the valve hole 14. The valve body 15 has a cylindrical shape having an inclined cut surface 17. Rotate and adjust the center of the shaft in the pipeline 10, and adjust the opening of the valve hole 13 on the side of the valve body 15 facing the valve hole 13. And adjust according to the opening degree to adjust the flow of compressed air. At this time, the relationship between the rotation angle of the valve body 15 and the effective sectional area of the flow path becomes a curve as shown in Fig. 3A. Corresponding to this, the relationship between the rotation angle of the valve body 15 and the pressure at the inlet portion of the weft insertion nozzle 8 becomes a curve as shown in Fig. 3B. The valve hole 14 is appropriately opened and closed by a valve 16 operated by a solenoid 18. However, in this conventional technique, when the valve hole 13 of the valve body 15 is closed, the flow of compressed air becomes a part of the dam, and the cross-sectional area of the flow path is rapidly changed before and after. Therefore, the pressure loss caused by the dam becomes large. As a result, there is a problem that it is difficult to obtain a sufficiently high static pressure at the inlet of the nozzle 8. In addition, due to the shrinkage relationship, a closed state larger than the actual dam is generated, and there is a problem that the accuracy of the flow rate adjustment of the compressed air is reduced. Furthermore, the large buckling of the fluid path also makes the above problems more significant. Brief Description of the Invention The present invention is directed to the practitioners who have problems with the conventional techniques as described above. Therefore, the main object of the present invention is to provide a throttle valve which has not only small pressure loss, easy flow rate adjustment, but also high accuracy. Yet another object is to provide a weft insertion device having such a throttle valve in an air-jet loom. -4- 507033 V. Description of the invention (3) In order to achieve the above-mentioned object, according to the main aspect of the present invention, a throttle valve is characterized by having a valve hole passing through the fluid channel perpendicularly intersecting with the valve hole, and inserting the valve hole The valve body which can be adjusted around the axis is rotatably formed on the outer peripheral surface of the valve body at a position corresponding to the opening portion of the fluid passage, and a recessed portion is formed whose depth continuously changes along the outer peripheral direction. According to the present invention, since the change in the cross-sectional area of the flow path in the throttle section is stable, the pressure loss is small, and it is not easy to cause shrinkage, and the change in the cross-sectional area of the flow path is linear to the valve body's rotation angle. Easy to adjust flow. It is preferable that the depth of the notched portion gradually becomes deeper toward the outer peripheral direction, and then gradually becomes shallower. The change in the cross-sectional area of the flow path in the throttle section becomes smoother and the pressure loss becomes smaller. In addition, it is preferable that the concave and engraved portion is a combination of a partial cone formed by the axis center of the valve body being eccentric. With such a configuration, the concave portion of the valve body can be easily formed by simple machining of a lathe. Furthermore, the valve body is made into a cylindrical shape. The concave shape of the valve body is formed on the outer peripheral surface of the cylindrical shape. The trajectory of the concave shape corresponding to the rotation of the valve body forms an intersection with the fluid path. ideal. The cross-sectional area of the cylindrical valve body can be changed to make it more stable. Furthermore, an actuator equipped with an output shaft driven by electrical rotation is provided. When the valve body is mounted on the output shaft of the actuator, it can also be adjusted for rotation. Therefore, the rotation adjustment of the valve body can be automated. The center axis of the valve hole is preferably arranged at a position eccentric to the center axis of the fluid passage. According to such a structure, even when the throttle flow is 507033 5. When the maximum state of the invention (4), it can always ensure the flow path of a certain size. According to another aspect of the present invention, the weft insertion device in the air-jet loom is characterized by having a throttle valve as described above, and the fluid passage is a pressure-adjusted compressed air source connected to the air-jet loom, and jets the The fluid path of the compressed air nozzle. According to the present invention, the function of the throttle valve as described above can be enjoyed in the air-jet loom. That is, in the air-jet loom, due to the type of weft yarn used or the state of weft insertion, it becomes possible to make detailed pressure adjustments, so the weft insertion function can be improved, and it can also be related to the reduction of compressed air consumption. Furthermore, according to still another aspect of the present invention, the nozzle is a weft-feeding nozzle for weft-feeding weft yarns, and is connected to the weft-feeding device of the air-jet loom, and is connected with the compressed air source and the weft-feeding nozzle. An on-off valve provided in the fluid path is used to switch the opening and closing of the on-off valve to supply and stop the compressed air to the weft insertion nozzle. In the open state of the on-off valve, the weft insertion nozzle is The compressed air ejection function has an opening and closing valve for weft insertion of the weft yarn, and in each weft insertion cycle, corresponding to the opening and closing sequence of the opening and closing valve, is used to control the throttle state of the throttle valve. In the air-jet loom, the drop pressure characteristics of the weft insertion nozzle affect the weft insertion state of the weft yarn. When the on-off valve that controls the supply and stop of compressed air to the weft-feeding nozzle is closed, the injection pressure at the weft-feeding nozzle is sharply reduced. Therefore, the weft yarn is vibrated depending on the type of yarn, and it is easy to cause trembling or slackening. The weaving yarns tremble or slacken, which reduces the quality of the fabric. In order to prevent the injection pressure from dropping sharply in the weft-feeding nozzle, when the spraying of the weft-feeding nozzle is finished, a drive letter is output to the electromagnetic on-off valve in a pulse train-6- 507033 V. Inventive note (5) for electromagnetic opening and closing The valve is opened and closed on a small scale, and there is a method of gradually lowering the injection pressure at the end of the injection of the weft-feeding nozzle. However, in order to open and close the electromagnetic on-off valve on a small scale, it is necessary to use an electromagnetic on-off valve capable of high-speed operation. When using this type of electromagnetic on-off valve, the life span of the electromagnetic on-off valve with a standard response performance that was previously used is greatly shortened. In the present invention, it is not necessary to use an electromagnetic on-off valve that can operate at a very high speed, and the injection pressure characteristics of the nozzle for weft insertion can be improved. The injection pressure characteristics of the weft insertion nozzle can be adjusted by selecting the throttle state with another throttle valve of the on-off valve. Therefore, there is no need for an on-off valve for extremely high-speed operation to obtain a desired injection pressure characteristic. It is also desirable to have a control device that can control the throttle state of the throttle valve in accordance with the opening and closing sequence of the on-off valve in each weft insertion cycle. It is easier to adjust the throttle state of the throttle valve. Furthermore, it is preferable that the throttle valve is arranged on the upstream side of the on-off valve. On the upstream side of the on-off valve, in order to avoid prolonging the residual pressure state downstream of the on-off valve, it is suitable as a place for setting the throttle valve. Furthermore, the nozzle for weft insertion can be used as at least one of the main nozzle for weft insertion or the auxiliary nozzle for weft insertion. Brief description of the drawing. Fig. 1 is an explanatory diagram showing a feed path of compressed air in an air jet loom. Fig. 2 is an explanatory diagram showing a throttle device of a conventional device. Fig. 3 A is a valve showing a conventional device. The angle of the body and the effective section of the flow path 507033 5. The description of the relationship between the product of the invention (6), Figure 3B is a graph showing the relationship between the angle of the valve body and the pressure efficiency; Figure 4 is the first embodiment of the present invention Partial sectional front view of the throttle valve (in the throttled state); Figure 5 is a partial sectional front view of the throttle valve (in the released state); Figure 6 is a partial sectional plan view of the throttle valve (in the released state) State); Figure 7 is a partial sectional plan view of the throttle valve (in a partially released state); Figure 8 is a partial sectional plan view of the throttle valve (in a throttled state); Figure 9A is a diagram showing the angle and Relation curve diagram of effective cross-sectional area of the flow path. Figure 9B is a graph showing the relationship between the angle of the valve body and the pressure efficiency;
第1 0 A圖是顯示第2實施形態，壓縮空氣之供給路徑槪 要圖，第10B圖是第10A圖中A-A線之剖面圖，第10C 圖是顯示閥開度最大狀態之剖面圖； · 第1 1.A圖是用以說明噴射壓力特性之曲線圖，第1 1 B 圖是顯示閥開度爲零之狀態的剖面圖，第Π C圖是顯示閥 開度最大狀態之剖面圖，第Π D圖是說明習知之噴射壓力 特性之曲線圖； 第1 2 A圖是顯示第3實施形態，壓縮空氣之供給路徑之 槪要圖，第12B圖是第12A圖中B-B線之剖面圖； 第1 3 A圖是顯示閥開度最大狀態之剖面圖，第1 3B及 1 3C圖是顯示閥開度最小狀態之剖面圖，第1 3D圖是說明 噴射壓力特性之曲線圖； 第1 4圖是另外說明噴射壓力特性之曲線圖； 507033 五、發明説明（7 ) 第1 5圖是另外說明噴射壓力特性之曲線圖； 第1 6圖是另外說明噴射壓力特性之曲線圖； 第1 7圖是顯示第4實施形態，壓縮空氣之供給路徑之 槪要圖。 曼明較佳實施形態之詳細說明 下面將本發明之較佳實施形態參照圖面說明之。首先， 雖然第1圖是參照作爲習知技術之說明，但欲將本發明採 用在噴氣織機之際，該基本構成係一樣。因而，僅與本發 明相關之節流閥使用新符號（60, 80, 90, 1 00)，其他仍維持 相同符號。 第1實施形熊 根據第4〜8圖詳細說明本發明之節流閥60。本體61上 穿設有連通於第二管路5之流體通路62，同時穿設有與流 體通路62成垂直相交方向之閥孔63。然後，流體通路62 與閥孔63在互相連通狀態。閥孔63中有圓柱狀之閥體64 以其軸心爲中心形成可轉動調節地嵌插著。尙，閥孔6 3 的中心軸係配設在對流體通路6 2之中心軸成偏心的位置 。並由此’由節流閥60使流體通路62之流路剖面積爲最 小時，亦有某一定量之壓縮空氣經常流動著。然而，依_ 體64之直徑及偏心量，使流路剖面積爲零，亦即可使節 流閥6 0全閉。詳細在後面敘述。 自閥體64之本體61的突出部之一端，裝設用來轉動調 節閥體64之把手65。另一方面，自閥體64之本體61之 突出部另一端，裝設有防止脫落用之圓形扣件66。閥體 507033 五、發明説明（8 ) 64之兩端部附近刻設有〇-環溝67。0-環溝67內嵌入有 用以保持氣密性之〇 -環6 8。 在閥體64軸方向之大致中央附近，其外周面刻設有深 度在外周方向連續的變化之凹刻部69。此凹刻部69，例 如可利用車床，使閥體64夾住在偏心位置上旋轉，以車 刀的車削可簡單地獲得。此時，單純地以上下之部分圓錐 70a，70b之組合，形成凹刻部69。因而，凹刻部69之其 深度在圓周方向連續的變化（連續的增大，接著連續的減 少）。亦即，其流路剖面積連續的變化。尙，凹刻部是由 組合互成逆向的部分圓錐構成，其結果使凹刻部之流路剖 面呈現爲三角形者，但是並不限定於該形狀。因而，使凹 刻部之流路剖面，例如可變形爲半圓形或四角形等種種之 形狀。 接著，說明本實施形態之作用。送給投緯用噴嘴8的壓 縮空氣之流量調節（進一步爲投緯用噴嘴8之入口部的壓 力調節），是作業者藉由把手65轉動閥體64來進行。亦 即，由於閥體64的旋轉，由凹刻部69的流體通路62之 流路有效剖面積予適當地調節。 如第6圖（及第5圖）所示，閥體64之中心線S(形成凹 刻部69之部分圓錐70a，70b的軸心與閥體64之軸心的連 線）在與流體通路62之軸心垂直相交之位置時，由凹刻部 69的流路寬度Gi變成最大。亦即，流路剖面積變成最大 。（如第6圖所示）從其位置使閥體64左旋轉90°時，成爲如 第7圖所示狀態。此時依凹刻部69之流路寬度成爲G2。 -10- 507033 五、發明説明（9 ) 其後更使閥體64轉動至第8圖所示位置。則在此位置， 以部分7 1變成可密封之狀態，依凹刻部69的流路寬度 G3成爲最小。亦即，流路剖面積變成最小。因流路剖面積 在此最大與最小之間平穩連續的變化（參照第9 A圖），故 所求的投緯用噴嘴8的入口部的壓力，亦獲得第9B圖所 示關係，控制容易而成爲高精度者。 閥體64之轉動調節，係由作業者藉由把手65以手動進 行，但代替此把手，可將步進馬達、伺服馬達、電磁線圈 等之致動器連結於閥體，則可成爲自動調節。從而，可使 進行此壓縮空氣之流量控制的系統全體的自動控制化變成 可能。對於此待後述之。 節流閥60係例示配置在噴氣織機的壓縮空氣源與投緯 用噴嘴（投緯用主噴嘴）8連結之流體通路。然而，亦可在 噴氣織機之折曲寬度方向（亦即沿著緯紗之投緯路徑）配置 之多數個輔助噴嘴，與連接壓縮空氣源流體通路配設節流 閥。 簠2實施形熊 其次，本發明具體化的第2實施形態相關之節流閥80 根據第1 0及Π圖說明之。不厭其重複之煩簡單地說明構 成時，第1 0 A圖所示之參照符號8是投緯用主噴嘴，緯紗 Y由投緯用主噴嘴8之噴射向經紗開口內射出而投緯。參 照符號4爲壓縮空氣供給槽。壓縮空氣供給槽4之壓力， 依減壓閥2來調整壓力。壓縮空氣供給槽4，藉由供給管 85連接於電磁開閉閥7。 -11- 507033 五、發明説明（10 ) 在供給管85之中途，有閥孔91對供給管85內之壓縮 空氣用之流體通路1 4 1形成垂直相交。閥孔9 1以可旋轉 地安裝著閥體87。亦即，閥體87係其旋轉中心軸線161 對流體通路1 4 1成垂直相交地配設著。閥體87係固定於 步進馬達88之輸出軸171。步進馬達88旋轉驅動閥體87 。步進馬達88接受控制裝置89之控制。控制裝置89，根 據檢測織機之旋轉角度之旋轉編碼器’90獲得之織機旋轉 角度檢測資訊，用來控制步進馬達8 8之旋轉驅動。做爲 控制手段之控制裝置89在每一個投緯循環，對應於電磁 開閉閥7之開閉時序以控制步進馬達88之作動。 如第10B圖所示，閥體87之周面上形成有凹刻部162 以如延伸於周方向。如第1 0A圖所示，凹刻部1 62是由組 合互成逆向之一對圓錐面E 1，E2所形成。凹刻部1 62之 其深度是成爲隨著向周方向漸漸地變深之後，再漸漸地變 淺的形狀。對應於閥體87之旋轉的凹刻部1 62之軌跡， 是與流體通路141交叉。閥體87在第10A及10B圖之旋 轉位置時，閥孔91中流體之通過剖面積成爲零。因而， 壓縮空氣供給槽4之壓縮空氣係不能供給於電磁開閉閥7 側。閥體87在第1 0C圖之旋轉位置時，閥孔9 1中流體之 通過剖面積成爲最大。因而，壓縮空氣供給槽4之壓縮空 氣，對電磁開閉閥7可供給最大量。 由具有以上說明的閥孔9 1及凹刻部1 62之閥體87形成 節流閥80。 第Π A圖之曲線Μ顯示對於每一個投緯循環時之電磁 -12- 507033 五、發明説明（11 ) 開閉閥7之激磁信號，曲線C1是顯示每一個投緯循環與 閥體87有關之閥開度，亦即顯示閥孔9 1中之通過剖面積 。閥體87有關之閥開度在第10B圖及第11B圖之全閉狀 態爲閥開度零，第1 0C圖及第1 1 C圖之全開狀態爲最大閥 開度H〇。曲線F1爲以曲線C1所表示之閥開度狀態，亦 即顯示在節流狀態及賦予激磁信號Μ時之每一個投緯循 環之投緯用主噴嘴8之噴射壓波形。第1 1 D圖之曲線F〇 ’係表示未有由步進馬達88及閥體87所成節流閥時激磁 電磁開閉閥7時之噴射壓力波形。各曲線之橫軸0顯示織 機旋轉角度。 控制裝置89用來控制步進馬達88之作動，其閥體87 係依第10B圖及第10C圖、第11B圖及第11C圖之順序 改變其旋轉位置。第1 0B圖及第1 0C圖所示之節流狀態， 對應於一個投緯循環，第：ΠΒ圖及第1 1C圖所示之節流狀 態，則對應於下一個投緯循環。 第2實施形態可獲得以下效果。 (2-1)曲線F〇所示之投緯用主噴嘴8中之先前的噴射壓 力，在投緯用主噴嘴8具有噴射壓力之降下變成急遽之特 性。於本實施形態以曲線F1所顯示投緯用主噴嘴8之噴 射壓力，具有抑制在投緯用主噴嘴8的噴射壓力急遽條下 之特性。投緯用主噴嘴8抑制噴射壓力的急遽降下予以抑 制緯紗Y之振動來防止產生顫抖或緯紗鬆弛。 如此在投緯用主噴嘴8中噴射壓力特性之改良，可由與 電磁開閉閥7對應於另外之節流閥80之電磁開閉閥7的 -13- 507033 五、發明説明（12 ) 開閉時序，而選擇節流狀態來調整。因而，就不要爲了獲 得所要之噴射壓力特性之電磁開閉閥7的高速動作，不須 要採用能作非常高速動作之電磁開閉閥，即可改良在投緯 用主噴嘴8中之噴射壓力特性。 (2-2)即使在電磁開閉閥7從開狀態移行至閉狀態之後， 從電磁開閉閥7在下游側的流體通路係於殘壓狀態。此殘 壓狀態爲長時，投緯用主噴嘴8中的噴射壓力之降下時間 變成過於長，因而引起緯紗之鬆弛而產生投緯不良，在弱 紗之投緯時容易產生斷線。將節流閥80配置在電磁開閉 閥7之下游側時，由閥體87之節流作用，使電磁開閉閥7 下游側之流體通路之殘壓狀態拉長，因而容易產生上述之 缺失。將節流閥80配置在電磁開閉閥7上游側之構成， 避免在電磁開閉閥7之下游側的殘壓狀態之長期化上有利 〇 (2-3)控制裝置89控制步進馬達88之作動，係以閥體 87依第10B圖、第10C圖、第11B圖及第11C圖所示旋 轉位置之順序移行。閥體87有關之閥開度，即閥孔91中 流體之通過剖面積，在考量凹刻部1 62之形狀後，自決定 閥體87之旋轉位置可分度。在閥孔9 1帶來所要通過剖面 積的閥體87之旋轉位置，係由指定步進馬達88之旋轉位 置來簡單地獲得。 (2-4)由做爲電動致動器之步進馬達88驅動的閥體87之 高速旋轉、迅速的旋轉增速及迅速之旋轉減速容易。依閥 體87的閥孔91之通過剖面積在每一個投緯循環時變化之 -14- 507033 五、發明説明（13 ) 構成，是以每一個投緯循環時之節流程度及包括節流時序 的節流狀態，配合短時間之投緯時序來設定下最適當。 (2-5)凹刻部162係成爲其深度愈向圓周方向時，漸漸地 變深之後，形成漸漸地變淺的形狀。具有這種形狀之溝 162的閥體87，隨著閥體87之旋轉的通過剖面積之變化 使其連續的變平穩，因而噴射壓力特性的控制精度變高。 (2-6)供給管85內之流體通路141及凹刻部162構成直 線的路徑。如此直線的形狀之流體通路在減低壓損方面有 效。 第3實施形態 其次，說明第1 2圖及第1 3圖之第3實施形態相關之節 流閥90。與第2實施形態相同構成部附與相同符號。 與第1實施形態同樣地，如第12B圖所示的第3實施形 態的節流閥90閥孔92的中心軸線2 1 1，係位於從流體通 路141之中心軸線離開的位置。如第13A，13B及13C圖 所示，收容在閥孔92之閥體93之周面，凹刻部221以延 伸周方向地形成。如第1 2B圖所示，凹刻部22 1是由組合 互成逆向之一對圓錐面E3，E4形成。凹刻部22 1係其深 度隨著向周方向漸漸地變深之後，形成漸漸地變淺的形狀 。對應於閥體93之旋轉的凹刻部22 1之軌跡，係與流體 通路141交叉。閥體93在第12A及12B圖之旋轉位置時 ，在閥孔92附近的流體之通過剖面積成爲最大。閥體93 在第13B及13C圖之旋轉位置時，於閥孔92附近的流體 之通過剖面積變成最小。 -15- 507033 五、發明説明（14 ) 第13D圖之曲線C2，顯示有關閥體93之閥開度，亦即 顯示閥孔92附近之通過剖面積。閥體93有關之閥開度， 在第12A，12B圖及第13A圖中使節流程度爲最大閥開度 H1，在第13B及l3C圖使節流程度爲最小閥開度H2。曲 線F2爲表示給予激磁信號Μ及曲線C2表示之閥開度狀 態時之投緯用主噴嘴8之噴射壓力波形。控制裝置89，係 閥體9依第13Α、13Β、13C圖之順序進行變化旋轉位置 ，用來控制步進馬達88之作動。第13Α，13Β，13C圖所顯 示節流狀態，係對應於一個投緯循環。 於第3實施形態之節流閥90，亦可獲得與第2實施形態 中（2-1)〜(2-6)項同樣的效果。 本發明中，亦均可實現第14圖之曲線F3所顯示之噴射 壓力特性、第15圖之曲線F41，F42所顯示之噴射壓力特 性，第1 6圖之曲線F5所顯示之噴射壓力特性。從第1 4 圖中亦可了解，與第2實施形態時同樣地，表示可抑制噴 射壓力急遽的降下。第15圖之例子顯示有投緯之緯紗’ 從織布被切斷分離之際所產生之切斷衝擊，由曲線F42所 顯示之噴射壓力予以緩和。第1 6圖之例子顯示有弱紗之 投緯中可抑制噴射壓力之急遽的上升，用於防止斷線。 第1 4圖及第1 6圖之情況，使用第3實施形態相關之節 流閥90，可帶來閥開度曲線C3，C5。第15圖之情況’使 用第2實施形態相關之節流閥80，可帶來閥開度曲線C4 1， C42。 第4實施形1 >16- 507033 五、發明説明（15 ) 其次，說明第1 7圖之第4實施形態相關之節流閥1 〇〇。 與第2實施形態相同之構成部附與相同符號。 在角狀之供給管94內之流體通路23 1的直角部，配置 有閥體95。由步進馬達88所驅動之閥體95形成有傾斜面 241。傾斜面241在第17圖之實線位置與虛線位置之間轉 動，依閥體95之節流量由閥體95之旋轉位置來調整。 尙，本發明中亦可有如以下之實施形態。例如，閥體87, 93, 95可以用伺服馬達驅動。又，閥體87, 93, 95僅切換 爲2個位置配置時，可以使用旋轉線圈驅動閥體87, 93， 95。再者，作爲節流閥亦可以使用常開形之電磁開閉閥。 尙，亦可在開閉閥之下游配置節流閥。 又，上述之實施形態中，雖然節流閥是以適用於噴氣織 機之例說明，但是本發明並不限定於此，只要流量控制之 對象爲壓力流體就可適用。例如，一般空氣輸送或汽車用 燃料噴射裝置等等均可適用。 符號之說明 Y 1 2 3 4 5 6 7 緯紗 壓力源 減壓閥 第一管路 壓縮空氣供給槽 第二管路 節流閥 電磁開閉閥 -17- 507033 五、發明説明（16 ) 8 投緯用噴嘴 10,1 1,12 管路 13?14,63?91?92 閥孔 15,64,87,93,95 閥體 16 閥 17 切斷面 18 電磁線圈 60,80,90，100 節流閥 61 本體 62，141，231 流體通路 - 65 把手 66 圓形扣件 67,68 〇-環溝 69,162,221 凹刻部 70a，70b 部分圓錐 71 部分 85,94 供給管 88 步進馬達 89 控制裝置 161 旋轉中心軸線 171 輸出軸 21 1 中心軸線 241 傾斜面 -18-Fig. 10A is a schematic diagram showing a compressed air supply path in the second embodiment. Fig. 10B is a cross-sectional view taken along the line AA in Fig. 10A, and Fig. 10C is a cross-sectional view illustrating the maximum valve opening state; Fig. 11.A is a graph for explaining the injection pressure characteristic, Fig. 1 1 B is a sectional view showing a state where the valve opening degree is zero, and Fig. Π C is a sectional view showing a maximum state of the valve opening degree. Fig. ΠD is a graph illustrating the conventional injection pressure characteristics. Fig. 12A is a schematic diagram showing a compressed air supply path in the third embodiment. Fig. 12B is a cross-sectional view taken along the line BB in Fig. 12A. ; Figure 1 A is a sectional view showing the maximum state of the valve opening, Figures 1 3B and 1 3C are sectional views showing the minimum state of the valve opening, and Figure 1 3D is a graph illustrating the injection pressure characteristics; Figure 4 is a graph illustrating the injection pressure characteristics separately; 507033 V. Description of the invention (7) Figure 15 is a graph illustrating the injection pressure characteristics separately; Figure 16 is a graph illustrating the injection pressure characteristics separately; Fig. 7 shows the fourth embodiment of the compressed air supply path. Fig. Detailed description of the preferred embodiment of Manmin The preferred embodiment of the present invention will be described below with reference to the drawings. First, although FIG. 1 is a description of a conventional technique, the basic configuration is the same when the present invention is applied to an air-jet loom. Therefore, only the throttle valve related to the present invention uses the new symbol (60, 80, 90, 100), and the other symbols remain the same. First Embodiment The shape of the throttle valve 60 according to the present invention will be described in detail with reference to Figs. 4 to 8. The main body 61 is provided with a fluid passage 62 communicating with the second pipeline 5, and at the same time, a valve hole 63 is formed through the fluid passage 62 in a direction perpendicular to the fluid passage 62. Then, the fluid passage 62 and the valve hole 63 are in communication with each other. A cylindrical valve body 64 is formed in the valve hole 63 so as to be rotatable and adjustably inserted around the shaft center. Alas, the central axis of the valve hole 6 3 is arranged at a position eccentric to the central axis of the fluid passage 62. Therefore, the throttle valve 60 minimizes the cross-sectional area of the flow path of the fluid passage 62, and a certain amount of compressed air is constantly flowing. However, depending on the diameter and eccentricity of the body 64, the cross-sectional area of the flow path is zero, which can also make the throttle 60 fully closed. The details will be described later. A handle 65 for adjusting the valve body 64 is provided from one end of the protruding portion of the body 61 of the valve body 64. On the other hand, from the other end of the protruding portion of the main body 61 of the valve body 64, a round fastener 66 for preventing falling off is mounted. Valve body 507033 V. Description of the invention (8) Near the two ends of the 64 are engraved with 0-ring grooves 67. The 0-ring grooves 67 are embedded with 0-rings 6 to maintain air tightness. Near the center of the valve body 64 in the axial direction, the outer peripheral surface is engraved with a notched portion 69 having a depth that continuously changes in the outer peripheral direction. This notch 69 can be obtained by turning the valve body 64 at an eccentric position with a lathe, for example, by turning with a turning tool. At this time, the combination of the upper and lower partial cones 70a, 70b is simply formed to form the concave engraved portion 69. Therefore, the depth of the recessed portion 69 changes continuously in the circumferential direction (continuously increasing, and then continuously decreasing). That is, the cross-sectional area of the flow path continuously changes. Alas, the recessed engraved portion is composed of a combination of partial cones that are mutually opposite. As a result, the cross section of the flow path of the recessed engraved portion is triangular, but it is not limited to this shape. Therefore, the cross section of the flow path of the recessed portion can be deformed into various shapes such as a semicircular shape or a quadrangular shape. Next, the effect of this embodiment will be described. The adjustment of the flow rate of the compressed air fed to the weft insertion nozzle 8 (further the pressure adjustment at the inlet of the weft insertion nozzle 8) is performed by the operator turning the valve body 64 with the handle 65. That is, due to the rotation of the valve body 64, the effective cross-sectional area of the flow path of the fluid passage 62 of the recessed portion 69 is appropriately adjusted. As shown in FIG. 6 (and FIG. 5), the center line S of the valve body 64 (the connection between the axis of the partial cones 70 a and 70 b forming the concave portion 69 and the axis of the valve body 64) is in fluid passage When the axis of 62 intersects perpendicularly, the flow path width Gi of the notch 69 becomes maximum. That is, the cross-sectional area of the flow path becomes maximum. (As shown in Fig. 6) When the valve body 64 is rotated 90 ° to the left from its position, the state shown in Fig. 7 is obtained. At this time, the width of the flow path according to the notched portion 69 becomes G2. -10- 507033 V. Description of the invention (9) Thereafter, the valve body 64 is further rotated to the position shown in FIG. 8. At this position, the portion 71 becomes a sealable state, and the flow path width G3 of the recessed portion 69 becomes the smallest. That is, the cross-sectional area of the flow path is minimized. Because the cross-sectional area of the flow path changes smoothly and continuously between this maximum and minimum (refer to Figure 9A), the pressure at the inlet of the nozzle 8 for weft insertion is also obtained as shown in Figure 9B, which is easy to control Become a high-precision person. The rotation adjustment of the valve body 64 is manually performed by the operator through the handle 65, but instead of this handle, actuators such as stepper motors, servo motors, and electromagnetic coils can be connected to the valve body, which can be automatically adjusted. . This makes it possible to automatically control the entire system for controlling the flow rate of the compressed air. This will be described later. The throttle valve 60 is an example of a fluid passage connected to a compressed air source disposed on the air-jet loom and a nozzle for weft insertion (main nozzle for weft insertion) 8. However, it is also possible to arrange a plurality of auxiliary nozzles in the bending width direction of the air-jet loom (that is, along the weft insertion path), and a throttle valve is connected to the fluid path connecting the compressed air source.簠 2 Implementation Shape Next, the throttle valve 80 related to the second embodiment of the present invention will be described with reference to Figs. 10 and Π. When the structure is simply explained, the reference symbol 8 shown in FIG. 10A is the main nozzle for weft insertion, and the weft Y is ejected into the opening of the warp by the injection of the main nozzle 8 for weft insertion, and weft insertion is performed. Reference numeral 4 is a compressed air supply tank. The pressure of the compressed air supply tank 4 is adjusted by the pressure reducing valve 2. The compressed air supply tank 4 is connected to an electromagnetic on-off valve 7 via a supply pipe 85. -11- 507033 V. Description of the invention (10) In the middle of the supply pipe 85, there are valve holes 91 that intersect the fluid passages 1 4 1 for compressed air in the supply pipe 85 vertically. The valve body 91 is rotatably mounted with a valve body 87. That is, the valve body 87 is arranged so that its rotation center axis 161 intersects the fluid passages 1 4 1 perpendicularly. The valve body 87 is fixed to the output shaft 171 of the stepping motor 88. The stepping motor 88 rotationally drives the valve body 87. The stepping motor 88 is controlled by the control device 89. The control device 89 is used to control the rotation driving of the stepping motor 88 according to the rotation angle detection information of the loom obtained by the rotary encoder '90 which detects the rotation angle of the loom. The control device 89 as a control means controls the operation of the stepping motor 88 in accordance with the opening and closing timing of the electromagnetic on-off valve 7 in each weft insertion cycle. As shown in FIG. 10B, a concave portion 162 is formed on the peripheral surface of the valve body 87 so as to extend in the circumferential direction. As shown in Fig. 10A, the recessed engraved portion 162 is formed by combining a pair of conical surfaces E1, E2 in opposite directions. The depth of the notched portion 162 is a shape that gradually becomes shallower as it gradually becomes deeper in the circumferential direction. The trajectory of the concave portion 162 corresponding to the rotation of the valve body 87 intersects the fluid passage 141. When the valve body 87 is in the rotation position in Figs. 10A and 10B, the flow cross-sectional area of the fluid in the valve hole 91 becomes zero. Therefore, the compressed air of the compressed air supply tank 4 cannot be supplied to the electromagnetic on-off valve 7 side. When the valve body 87 is in the rotation position in Fig. 10C, the cross-sectional area of the fluid passing through the valve hole 91 is maximized. Therefore, the compressed air in the compressed air supply tank 4 can supply a maximum amount to the electromagnetic on-off valve 7. The throttle valve 80 is formed by the valve body 87 having the valve hole 91 and the recessed portion 162 described above. The curve M in Fig. ΠA shows the electromagnetic signals for each weft insertion cycle. -12-507033 V. Explanation of the invention (11) The excitation signal of the opening and closing valve 7, the curve C1 shows that each weft insertion cycle is related to the valve body 87. The valve opening degree, that is, the passage cross-sectional area in the valve hole 91 is displayed. The valve opening degree of the valve body 87 in the fully closed state of FIGS. 10B and 11B is the valve opening degree of zero, and the fully opened state of FIGS. 10C and 11C is the maximum valve opening degree H0. The curve F1 is the valve opening state indicated by the curve C1, that is, the injection pressure waveform of the main nozzle 8 for weft insertion in each of the weft insertion cycles when the throttle state and the excitation signal M is given is displayed. The curve F0 'in FIG. 1D shows the injection pressure waveform when the solenoid valve 7 is excited without the throttle valve formed by the stepping motor 88 and the valve body 87. The horizontal axis 0 of each curve shows the loom rotation angle. The control device 89 is used to control the operation of the stepping motor 88, and its valve body 87 changes its rotation position in the order of FIG. 10B and FIG. 10C, FIG. 11B and FIG. 11C. The throttling states shown in Figs. 10B and 10C correspond to one weft insertion cycle, and the throttling states shown in Figs. ΠB and 11C correspond to the next weft insertion cycle. According to the second embodiment, the following effects can be obtained. (2-1) The previous ejection pressure in the weft-feeding main nozzle 8 shown by the curve F0 has the characteristic that the ejection pressure of the weft-feeding main nozzle 8 decreases sharply. The injection pressure of the main nozzle 8 for weft insertion shown by the curve F1 in this embodiment has a characteristic of suppressing the pressure of the main nozzle 8 for weft insertion to be sharp. The main nozzle 8 for weft insertion suppresses a sharp drop in the injection pressure and suppresses the vibration of the weft yarn Y to prevent chattering or weft slack. In this way, the improvement of the injection pressure characteristic in the main nozzle 8 for weft insertion can be performed by the -13- 507033 of the electromagnetic on-off valve 7 corresponding to the electromagnetic on-off valve 7 and the other throttle valve 80. 5. Description of the invention (12) Opening and closing sequence, and Select the throttle state to adjust. Therefore, it is not necessary to improve the high-speed operation of the electromagnetic on-off valve 7 in order to obtain the desired injection pressure characteristics, and it is not necessary to use an electromagnetic on-off valve capable of very high-speed operation, so that the injection pressure characteristics in the main nozzle 8 for weft insertion can be improved. (2-2) Even after the electromagnetic on-off valve 7 moves from the open state to the closed state, the fluid passage on the downstream side from the electromagnetic on-off valve 7 is in a residual pressure state. When this residual pressure state is long, the drop time of the ejection pressure in the main nozzle 8 for weft insertion becomes too long, which causes the weft yarn to slacken, causing weft insertion failure, and thread breakage easily occurs when the weak yarn is inserted. When the throttle valve 80 is arranged on the downstream side of the electromagnetic on-off valve 7, the residual pressure state of the fluid path on the downstream side of the electromagnetic on-off valve 7 is prolonged by the throttling action of the valve body 87, so that the above-mentioned defects are liable to occur. The configuration in which the throttle valve 80 is arranged on the upstream side of the electromagnetic on-off valve 7 is advantageous in avoiding the prolongation of the residual pressure state downstream of the electromagnetic on-off valve 7. (2-3) The control device 89 controls the operation of the stepping motor 88 The valve body 87 moves in the order of rotation positions shown in FIG. 10B, FIG. 10C, FIG. 11B, and FIG. 11C. The valve opening related to the valve body 87, that is, the cross-sectional area of the fluid passing through the valve hole 91, is determined by considering the shape of the recessed portion 162, and the rotation position of the valve body 87 can be indexed. The rotation position of the valve body 87 to be passed through the valve hole 91 is obtained simply by specifying the rotation position of the stepping motor 88. (2-4) The valve body 87 driven by the stepping motor 88 as an electric actuator is capable of high-speed rotation, rapid rotation increase, and rapid rotation deceleration. -14- 507033 which changes according to the cross-sectional area of the valve hole 91 of the valve body 87 at each weft insertion cycle V. Description of the invention (13) The structure is based on the degree of throttling and throttling during each weft insertion cycle The timing of the throttling state is best set in conjunction with the short-time weft input timing. (2-5) The recessed portion 162 is formed into a shape that gradually becomes shallower as the depth gradually becomes deeper in the circumferential direction. The valve body 87 having the groove 162 having such a shape changes continuously as the passage area of the valve body 87 passes through to make it continuously stable, so that the control accuracy of the injection pressure characteristic becomes high. (2-6) The fluid path 141 and the recessed portion 162 in the supply pipe 85 constitute a straight path. Such straight-line fluid passages are effective in reducing low pressure loss. Third Embodiment Next, a throttle valve 90 according to the third embodiment shown in Figs. 12 and 13 will be described. The same components as those in the second embodiment are assigned the same reference numerals. Similarly to the first embodiment, the center axis 2 1 1 of the valve hole 92 of the throttle valve 90 of the third embodiment shown in Fig. 12B is located away from the center axis of the fluid passage 141. As shown in Figs. 13A, 13B, and 13C, the recessed portion 221 is formed in the circumferential direction of the peripheral surface of the valve body 93 housed in the valve hole 92. As shown in Fig. 12B, the notch 221 is formed by combining a pair of conical surfaces E3 and E4 in opposite directions. The recessed portion 22 1 has a shape that gradually becomes shallower as the depth gradually becomes deeper in the circumferential direction. The trajectory of the concave portion 22 1 corresponding to the rotation of the valve body 93 crosses the fluid passage 141. When the valve body 93 is in the rotation position in FIGS. 12A and 12B, the cross-sectional area of the fluid passing through the valve hole 92 becomes the largest. When the valve body 93 is in the rotation position in FIGS. 13B and 13C, the cross-sectional area of the fluid passing near the valve hole 92 becomes the smallest. -15- 507033 V. Explanation of the invention (14) Curve C2 in FIG. 13D shows the valve opening of the valve body 93, that is, the passage cross-sectional area near the valve hole 92. For the valve opening degree of the valve body 93, the throttle degree is set to the maximum valve opening degree H1 in FIGS. 12A, 12B and 13A, and the throttle degree is set to the minimum valve opening degree H2 in FIGS. 13B and 13C. A curve F2 is a waveform of the injection pressure of the main nozzle 8 for weft insertion when the excitation signal M and the valve opening state shown by the curve C2 are given. The control device 89 is used to change the rotation position of the valve body 9 in the order of Figs. 13A, 13B and 13C, and is used to control the operation of the stepping motor 88. The throttling states shown in Figures 13A, 13B, and 13C correspond to a weft insertion cycle. In the throttle valve 90 of the third embodiment, the same effects as those of the items (2-1) to (2-6) in the second embodiment can be obtained. In the present invention, the injection pressure characteristics shown by the curve F3 in FIG. 14, the injection pressure characteristics shown by the curves F41 and F42 in FIG. 15, and the injection pressure characteristics shown by the curve F5 in FIG. 16 can also be realized. As can be understood from FIG. 14, similarly to the case of the second embodiment, it is shown that a sharp drop in the injection pressure can be suppressed. The example in Fig. 15 shows that the cutting impact generated when the weft insertion weft 'is cut and separated from the woven fabric is relieved by the injection pressure shown by curve F42. The example in Fig. 16 shows that weft insertion can be suppressed during the weft insertion with a weak yarn to prevent a sudden increase in the jetting pressure to prevent thread breakage. In the case of FIGS. 14 and 16, the use of the throttle valve 90 according to the third embodiment can bring the valve opening curves C3 and C5. In the case of Fig. 15 ', the use of the throttle valve 80 according to the second embodiment can bring the valve opening degree curves C4 1, C42. Fourth Embodiment 1 > 16-507033 5. Explanation of the Invention (15) Next, a throttle valve 100 according to the fourth embodiment shown in Fig. 17 will be described. The same components as those in the second embodiment are assigned the same reference numerals. A valve body 95 is disposed at a right angle portion of the fluid passage 231 in the angular supply pipe 94. The valve body 95 driven by the stepping motor 88 is formed with an inclined surface 241. The inclined surface 241 rotates between the position of the solid line and the position of the broken line in FIG. 17, and is adjusted by the rotation position of the valve body 95 according to the throttle of the valve body 95. Alas, the present invention may also have the following embodiments. For example, the valve bodies 87, 93, 95 can be driven by a servo motor. When the valve bodies 87, 93, and 95 are switched to a two-position arrangement, the valve bodies 87, 93, and 95 can be driven by a rotary coil. Furthermore, a normally-open electromagnetic on-off valve can also be used as the throttle valve. Alas, a throttle valve can also be placed downstream of the on-off valve. In the above-mentioned embodiment, the throttle valve is described as an example applicable to an air-jet loom, but the present invention is not limited to this, and may be applied as long as the object of flow control is a pressure fluid. For example, general air transportation or fuel injection devices for automobiles are applicable. Explanation of symbols Y 1 2 3 4 5 6 7 Weft pressure source pressure reducing valve First line compressed air supply tank Second line throttle valve electromagnetic on-off valve -17-507033 V. Description of the invention (16) 8 For weft insertion Nozzle 10,1 1,12 Line 13? 14,63? 91? 92 Valve hole 15,64,87,93,95 Valve body 16 Valve 17 Cut-off surface 18 Solenoid coil 60,80,90,100 Throttle valve 61 Body 62, 141, 231 Fluid passage-65 Handle 66 Round fastener 67, 68 〇-ring groove 69, 162, 221 Recessed part 70a, 70b Partial cone 71 Part 85, 94 Supply tube 88 Stepper motor 89 Control device 161 Rotation center Axis 171 Output shaft 21 1 Central axis 241 Inclined surface -18-