JP4629401B2 - Spool rotation prevention structure of spool valve - Google Patents

Description

本発明は、スプールの移動により複数の流路間を切換えるスプール弁型の電磁切換弁やパイロット切換弁等のスプールの回転を防止するスプール弁のスプール回転防止構造に関する。   The present invention relates to a spool rotation prevention structure for a spool valve that prevents rotation of a spool such as a spool valve type electromagnetic switching valve or a pilot switching valve that switches between a plurality of flow paths by movement of the spool.

この種のスプール弁のスプール回転防止構造は、本体の嵌合穴にスプールを軸方向へ摺動自在に挿入し、本体の両側には通電により発生する電磁力でスプールを移動する電磁石を備えると共に、スプールの両側にはスプールを中立位置に保持するばねを備え、電磁石の通電・非通電によりスプールを電磁力とばね力との対向作用で軸方向に移動して複数の流路間を切換える。そして、スプールの一端部に軸に平行な面取り部を設け、本体には嵌合穴に同心の開口穴を形成し、開口穴とスプールの面取り部との間には蒲鉾形の回転止め部材を配置し、回転止め部材は、外径を開口穴の内径よりやや小さくすると共に底辺部を開口穴からスプールの面取部までの寸法よりやや小さくし、本体に打ち込んだスプリングピンに微小回転可能に係止している。このため、複数の流路間を流入・流出する流体の流体力によってスプールを回転させようとするが、スプールの面取り部が回転止め部材の底辺部に接触し、回転止め部材の外径が開口穴の内径に当接し、スプールの回転を防止している。なお、スプールを中立位置に保持するばねの一方は、回転止め部材と干渉しないよう他方のばねより小径のものを用いている。
特開平８−２１９３００号公報（２−３頁、図１−３） This type of spool valve anti-rotation structure for a spool valve includes an electromagnet for inserting a spool into a fitting hole of the main body so as to be slidable in the axial direction and moving the spool by electromagnetic force generated by energization on both sides of the main body. A spring for holding the spool in a neutral position is provided on both sides of the spool, and the spool is moved in the axial direction by the opposing action of the electromagnetic force and the spring force by the electromagnet energization / non-energization to switch between the plurality of flow paths. Then, a chamfered part parallel to the shaft is provided at one end of the spool, a concentric opening hole is formed in the main body, and a hook-shaped anti-rotation member is provided between the opening hole and the chamfered part of the spool. The anti-rotation member is arranged so that the outer diameter is slightly smaller than the inner diameter of the opening hole and the base is slightly smaller than the dimension from the opening hole to the chamfered portion of the spool, so that the spring pin driven into the body can be rotated slightly. Locked. For this reason, the spool is rotated by the fluid force of the fluid flowing in and out of the plurality of flow paths, but the chamfered portion of the spool contacts the bottom of the rotation stop member, and the outer diameter of the rotation stop member is opened. It contacts the inner diameter of the hole to prevent the spool from rotating. One of the springs that hold the spool in the neutral position has a smaller diameter than the other spring so as not to interfere with the rotation stop member.
JP-A-8-219300 (page 2-3, FIG. 1-3)

ところが、かかる従来のスプール弁のスプール回転防止構造では、スプールの回転を防止するために、スプールに面取り部を形成すると共に、本体に回転止め部材を微小回転可能に係止するため、スプールと本体との両方にスプールの回転を防止する構成を施さなければならず、構成が複雑になる問題があった。   However, in the conventional spool rotation prevention structure of the spool valve, in order to prevent the rotation of the spool, a chamfered portion is formed in the spool, and the rotation stopper member is locked to the main body so as to be able to rotate slightly. Both have to be provided with a configuration for preventing the rotation of the spool, resulting in a complicated configuration.

本発明の課題は、スプールに回転を防止する構成を格別に施すことなくスプールの回転を防止し、構成を簡素化し得るスプール弁のスプール回転防止構造を提供することにある。   An object of the present invention is to provide a spool rotation prevention structure for a spool valve that can prevent the rotation of the spool without simplifying the structure for preventing the rotation of the spool and can simplify the structure.

かかる課題を達成すべく、本発明は課題を解決するため次の手段をとった。即ち、
本体に軸方向へ嵌合穴を穿設すると共に、流体を流入する供給流路と流体を流入出する負荷流路と流体を流出する排出流路とを軸方向へ間隙を有して嵌合穴内周面に開口して設け、嵌合穴には前記複数の流路間を切換連通するスプールを軸方向へ摺動自在に挿入し、供給流路が開口する箇所の嵌合穴内周面とスプール外周面との間に環状隙間を形成し、供給流路には環状隙間に流入する流体の流量を環状隙間の周方向の一方向と他方向とに対向して略同等に調整する流量調整部材を設け、前記スプールを中立位置に保持するばねを前記スプールの両側に備え、前記供給流路が開口する個所の前記嵌合穴内径を前記スプールの外径より大きく設け、前記供給流路を前記嵌合穴の中心より径方向外側に偏移して前記嵌合穴に接線方向で接続し、前記流量調整部材は流体が流通する絞り穴を貫通形成し、前記供給流路から前記絞り穴を通過して前記環状隙間に流入する流体と前記供給流路から前記絞り穴を通過せずに前記環状隙間に流入する流体とに分配し、この分配した流体を前記環状隙間の周方向の一方向と他方向とに対向して流量を略同等に調整することを特徴とするスプール弁のスプール回転防止構造がそれである。 In order to achieve this problem, the present invention has taken the following measures to solve the problem. That is,
A fitting hole is drilled in the body in the axial direction, and a supply flow path for flowing in fluid, a load flow path for flowing in and out fluid, and a discharge flow path for flowing out fluid are fitted with a gap in the axial direction. An opening is provided on the inner peripheral surface of the hole, and a spool for switching communication between the plurality of flow paths is inserted into the fitting hole so as to be slidable in the axial direction. An annular clearance is formed between the outer circumferential surface of the spool, and the flow rate adjustment that adjusts the flow rate of the fluid flowing into the annular clearance in the supply flow path in a substantially equal manner opposite to the circumferential direction in the circumferential direction of the annular clearance. Members are provided , springs for holding the spool in a neutral position are provided on both sides of the spool, the fitting hole inner diameter where the supply channel opens is larger than the outer diameter of the spool, and the supply channel is Shifted radially outward from the center of the fitting hole and connected to the fitting hole in a tangential direction, The flow rate adjusting member is formed by penetrating a throttle hole through which a fluid flows, and the fluid that passes through the throttle hole from the supply flow path and flows into the annular gap and the annular shape without passing through the throttle hole from the supply flow path. Spool rotation prevention of the spool valve, wherein the spool valve is distributed to the fluid flowing into the gap and the flow rate is adjusted to be substantially equal while facing the one direction and the other direction of the circumferential direction of the annular gap. That is the structure.

以上詳述したように、請求項１に記載の発明は、供給流路から環状隙間に流入する流体の流量が流量調整部材により周方向の一方向と他方向とに略同等に分配されて相対し、スプールを回転しようとする力が周方向で平衡して、スプールの回転を防止できる。そして、供給流路に流量調整部材を設けることでスプールの回転を防止しているため、スプールに回転を防止する構成を格別に施すことなくスプールの回転を防止でき、構成を簡素化することができる。 As described above in detail, according to the first aspect of the present invention, the flow rate of the fluid flowing into the annular gap from the supply flow path is substantially equally distributed between the circumferential direction in one direction and the other direction by the flow rate adjusting member. Then, the force to rotate the spool is balanced in the circumferential direction, and the rotation of the spool can be prevented. And since the rotation of the spool is prevented by providing the flow rate adjusting member in the supply flow path, the rotation of the spool can be prevented without specially providing the structure for preventing the rotation of the spool, and the configuration can be simplified. it can.

また、請求項１に記載の発明は、スプールに回転を防止する構成を格別に施すことなくできるため、スプールを中立位置に保持するばねは、スプールの両側に同一のものを備えることができ、スプールを中立位置に保持するばねの一方を、回転止め部材と干渉しないよう他方のばねより小径のものを用いなければならない従来のスプール回転防止構造に比し、必要とする部品の種類を削減することができる。 The invention described in Claim 1, since it without performing exceptionally configuration to prevent rotation in spool, a spring for holding the spool in the neutral position, it can be provided with identical on both sides of the spool Compared to the conventional spool rotation prevention structure, one of the springs that hold the spool in the neutral position must be smaller in diameter than the other spring so that it does not interfere with the anti-rotation member. can do.

また、請求項１に記載の発明は、供給流路が開口する個所の嵌合穴内径を前記スプールの外径より大きく設け、供給流路を嵌合穴の中心より径方向外側に偏移して嵌合穴に接線方向で接続しているため、供給流路の嵌合穴への開口面積を大きくすることができ、供給流路を大径にすることなく、供給流路から環状隙間に流入する流体の流量増加を図ることができる。 The invention according to claim 1, the fitting hole inner diameter of the point where supply passages are opened provided larger than the outer diameter of the spool, shift radially outward from the center of the fitting hole of the supply channel Since the connection hole is tangentially connected to the fitting hole, the opening area of the supply channel to the fitting hole can be increased, and the annular gap from the supply channel can be achieved without increasing the diameter of the supply channel. It is possible to increase the flow rate of the fluid flowing into the.

また、請求項１に記載の発明は、前記流量調整部材は流体が流通する絞り穴を貫通形成し、前記供給流路から前記絞り穴を通過して前記環状隙間に流入する流体と前記供給流路から前記絞り穴を通過せずに前記環状隙間に流入する流体とに分配し、この分配した流体を前記環状隙間の周方向の一方向と他方向とに対向して流量を略同等に調整しているため、この略同等に調整する流体の流量を絞り穴の大きさに応じて精度良く設定することができる。 The invention of claim 1, prior Symbol flow adjustment member is formed through a throttle hole through which fluid flows, the fluid flowing into the annular gap through the throttle hole from said supply passage supplies Distributing the fluid from the flow path to the fluid that flows into the annular gap without passing through the throttle hole, and the distributed fluid is opposed to the circumferential direction in one direction and the other direction so that the flow rate is substantially equal. Since the adjustment is performed, the flow rate of the fluid to be adjusted to be substantially the same can be accurately set according to the size of the throttle hole.

以下、スプール弁として電磁切換弁に本発明を実施した一実施形態を図面に基づき説明する。
図１及び図２において、１は略矩形状の本体で、両側面にソレノイド２，３を備えると共に、上面に端子箱４を備えている。５は本体１に軸方向へ貫通して穿設の嵌合穴で、本体１の両側面に開口し、両側面の開口はソレノイド２，３で閉塞している。嵌合穴５は軸方向の略中央部に拡径した第１拡径部５Ａを形成し、第１拡径部５Ａの軸方向両側に間隙を有して拡径した第２拡径部５Ｂと第３拡径部５Ｃとを形成し、さらに、第２拡径部５Ｂと第３拡径部５Ｃのそれぞれ軸方向外側に間隙を有して拡径した第４拡径部５Ｄと第５拡径部５Ｅとを形成している。本体１には流体を流入する供給流路Ｐと、流体を流入出する第１負荷流路Ａと第２負荷流路Ｂと、流体を流出する第１排出流路Ｔ１と第２排出流路Ｔ２とをそれぞれ嵌合穴５と略直交方向に本体１の下面から穿設している。供給流路Ｐは円筒形状の穴で、嵌合穴５の中心より径方向外側に偏移して嵌合穴５の第１拡径部５Ａに接線方向で接続し、嵌合穴５の第１拡径部５Ａ内周面へ先端部に加えて側面部を開口し、第１拡径部５Ａへの開口面積を大きくして流量増加を図っている。そして、供給流路Ｐは直径寸法を第１拡径部５Ａの軸方向における巾寸法より大きく設けている。また、第１負荷流路Ａは第２拡径部５Ｂ内周面に、第２負荷流路Ｂは第３拡径部５Ｃ内周面に、第１排出流路Ｔ１は第４拡径部５Ｄ内周面に、第２排出流路Ｔ２は第５拡径部５Ｅ内周面にそれぞれ開口している。 Hereinafter, an embodiment in which the present invention is applied to an electromagnetic switching valve as a spool valve will be described with reference to the drawings.
1 and 2, reference numeral 1 denotes a substantially rectangular main body having solenoids 2 and 3 on both side surfaces and a terminal box 4 on the upper surface. Reference numeral 5 denotes a fitting hole that penetrates the main body 1 in the axial direction and opens on both side surfaces of the main body 1, and the openings on both side surfaces are closed by solenoids 2 and 3. The fitting hole 5 forms a first enlarged diameter portion 5A having an enlarged diameter at a substantially central portion in the axial direction, and an enlarged second diameter portion 5B having a gap on both sides in the axial direction of the first enlarged diameter portion 5A. And the third enlarged diameter portion 5C, and the fourth enlarged diameter portion 5D and the fifth enlarged diameter portion 5D are expanded with a gap on the outer side in the axial direction of each of the second enlarged diameter portion 5B and the third enlarged diameter portion 5C. The enlarged diameter portion 5E is formed. The main body 1 has a supply channel P for flowing fluid, a first load channel A and a second load channel B for flowing fluid, and a first discharge channel T1 and second discharge channel for flowing fluid. T2 is drilled from the lower surface of the main body 1 in a direction substantially orthogonal to the fitting hole 5, respectively. The supply flow path P is a cylindrical hole, is shifted radially outward from the center of the fitting hole 5, is connected in a tangential direction to the first enlarged portion 5 </ b> A of the fitting hole 5, and In addition to the tip portion, the side surface portion is opened to the inner peripheral surface of the first enlarged diameter portion 5A, and the opening area to the first enlarged diameter portion 5A is increased to increase the flow rate. And the supply flow path P is provided with a diameter dimension larger than the width dimension in the axial direction of 5 A of 1st enlarged diameter parts. The first load flow path A is on the inner peripheral surface of the second enlarged diameter portion 5B, the second load flow path B is on the inner peripheral surface of the third enlarged diameter portion 5C, and the first discharge flow path T1 is the fourth enlarged diameter portion. On the 5D inner peripheral surface, the second discharge channel T2 opens to the inner peripheral surface of the fifth enlarged diameter portion 5E.

６は嵌合穴５に軸方向へ摺動自在に挿入したスプールで、軸方向へ間隙を有して第１ランド部６Ａと第２ランド部６Ｂとを備えると共に、第１ランド部６Ａと第２ランド部６Ｂとの間に位置する中央軸部６Ｃ及び第１ランド部６Ａの軸方向外側に位置する第１外側軸部６Ｄ及び第２ランド部６Ｂの軸方向外側に位置する第２外側軸部６Ｅを備えている。第１ランド部６Ａと第２ランド部６Ｂは、嵌合穴５に摺動する外径寸法に設けると共に、軸方向における巾寸法を嵌合穴５の第２拡径部５Ｂと第３拡径部５Ｃの巾寸法より小さく設けている。中央軸部６Ｃと第１外側軸部６Ｄと第２外側軸部６Ｅは、嵌合穴５より小径の外径寸法に設けている。７は環状隙間で、供給流路Ｐが開口する嵌合穴５の第１拡径部５Ａとスプール６の中央軸部６Ｃとの間に形成している。８は供給流路Ｐに設けた流量調整部材で、本体１の下面より供給流路Ｐの先端部に圧入して固定し、流体が流通する絞り穴９を軸方向に貫通形成し、絞り穴９の先端側を拡径した拡径部９Ａとしている。流量調整部材８は供給流路Ｐより環状隙間７に流入する流体の流量を環状隙間７の周方向の一方向と他方向とに略同等にするよう絞り穴９の開口面積と軸方向寸法を設定する。すなわち、供給流路Ｐを流れる流体の流量Ｑは流量調整部材８の絞り穴９を通過せずに供給流路Ｐの側面部から環状隙間７に流入して周方向の一方向に流れる流量Ｑ１と、絞り穴９を通過せずに供給流路Ｐの側面部から環状隙間７に流入して周方向の他方向に流れる流量Ｑ２と、絞り穴９を通過して供給流路Ｐの先端部から環状隙間７に流入して周方向の他方向に流れる流量Ｑ３とに分かれるので、Ｑ１＝Ｑ２＋Ｑ３でスプール６を回転しようとする力が周方向で平衡してスプール６の回転を防止する。よって、Ｑ１＝Ｑ２＋Ｑ３からＱ３＝Ｑ１−Ｑ２となるよう絞り穴９の開口面積と軸方向寸法を設定する。なお、絞り穴９の拡径部９Ａは、絞り穴９を通過した後の流体が第１拡径部５Ａへの供給流路Ｐの開口個所で絞られ流量Ｑ３の設定に狂いが生じることを確実に防止するよう絞り穴９後の開口面積を大きく設けるためのものである。 A spool 6 is slidably inserted in the fitting hole 5 in the axial direction and includes a first land portion 6A and a second land portion 6B with a gap in the axial direction, and the first land portion 6A and the first land portion 6A. A second outer shaft located on the outer side in the axial direction of the central shaft portion 6C located between the two land portions 6B, the first outer shaft portion 6D located on the outer side in the axial direction of the first land portion 6A, and the second land portion 6B. Part 6E is provided. The first land portion 6A and the second land portion 6B are provided in an outer diameter dimension that slides in the fitting hole 5, and the width dimension in the axial direction is set to the second enlarged diameter portion 5B and the third enlarged diameter diameter of the fitting hole 5. It is provided smaller than the width dimension of the part 5C. The central shaft portion 6 </ b> C, the first outer shaft portion 6 </ b> D, and the second outer shaft portion 6 </ b> E are provided with an outer diameter smaller than the fitting hole 5. An annular gap 7 is formed between the first diameter-enlarged portion 5A of the fitting hole 5 in which the supply flow path P opens and the central shaft portion 6C of the spool 6. Reference numeral 8 denotes a flow rate adjusting member provided in the supply flow path P. The flow adjustment member is press-fitted and fixed to the front end of the supply flow path P from the lower surface of the main body 1, and a throttle hole 9 through which fluid flows is formed in the axial direction. 9 is an enlarged diameter portion 9A having an enlarged diameter. The flow rate adjusting member 8 has the opening area and axial dimension of the throttle hole 9 so that the flow rate of the fluid flowing into the annular gap 7 from the supply flow path P is substantially equal in one direction in the circumferential direction of the annular gap 7 and the other direction. Set. That is, the flow rate Q1 of the fluid flowing through the supply flow path P flows into the annular gap 7 from the side surface portion of the supply flow path P without passing through the throttle hole 9 of the flow rate adjusting member 8 and flows in one circumferential direction. And a flow rate Q2 that flows into the annular gap 7 from the side surface portion of the supply flow path P without passing through the throttle hole 9 and flows in the other direction in the circumferential direction, and a front end portion of the supply flow path P through the throttle hole 9 Therefore, the force to rotate the spool 6 with Q1 = Q2 + Q3 is balanced in the circumferential direction to prevent the spool 6 from rotating. Therefore, the opening area and axial dimension of the aperture 9 are set so that Q1 = Q2 + Q3 to Q3 = Q1-Q2. Note that the enlarged diameter portion 9A of the throttle hole 9 causes the fluid after passing through the throttle hole 9 to be throttled at the opening portion of the supply flow path P to the first enlarged diameter portion 5A, resulting in an error in setting the flow rate Q3. This is to provide a large opening area after the throttle hole 9 so as to prevent it reliably.

１０、１１はスプール６を図１に示す中立位置に保持するばねで、スプール６を軸方向両端部から付勢するよう嵌合穴５の軸方向両端部に収装し、本体１両側面に固定したソレノイド２，３の固定鉄心２Ａ，３Ａとスプール６との間に挟持している。ソレノイド２，３は固定鉄心２Ａ，３Ａと対向して可動鉄心２Ｂ，３Ｂを軸方向へ移動自在に備え、端子箱４内部で図示しない外部電源と電気接続したコイル２Ｃ，３Ｃへの通電により生じる電磁力で可動鉄心２Ｂ，３Ｂを固定鉄心２Ａ，３Ａに向けて吸引して軸方向へ移動し、この可動鉄心２Ｂ，３Ｂの移動でロッド２Ｄ，３Ｄによりスプール６をばね１０，１１力に抗して軸方向へ摺動するよう押圧する。 Reference numerals 10 and 11 denote springs for holding the spool 6 in the neutral position shown in FIG. 1. The springs 6 and 11 are accommodated at both ends in the axial direction of the fitting hole 5 so as to urge the spool 6 from both ends in the axial direction. The fixed solenoid cores 2 </ b> A and 3 </ b> A of the fixed solenoids 2 and 3 are sandwiched between the spool 6. Solenoids 2 and 3 are provided with movable iron cores 2B and 3B that are movable in the axial direction so as to face fixed iron cores 2A and 3A, and are generated by energizing coils 2C and 3C that are electrically connected to an external power source (not shown) inside terminal box 4. The movable iron cores 2B and 3B are attracted toward the fixed iron cores 2A and 3A by the electromagnetic force and moved in the axial direction. The movement of the movable iron cores 2B and 3B causes the spool 6 to resist the force of the springs 10 and 11 by the rods 2D and 3D. Then, press to slide in the axial direction.

スプール６はソレノイド２，３の非通電による図１に示す中立位置と、ソレノイド２への通電で図１右方向への摺動による第１切換位置と、ソレノイド３への通電で図１左方向への摺動による第２切換位置との３位置に切換自在に設けている。そして、スプール６は中立位置で第１ランド部６Ａが第２拡径部５Ｂ内に位置すると共に、第２ランド部６Ｂが第３拡径部５Ｃ内に位置し、供給流路Ｐと第１負荷流路Ａと第２負荷流路Ｂと第１排出流路Ｔ１と第２排出流路Ｔ２との間を連通する。また、スプール６は第１切換位置で第１ランド部６Ａが第１拡径部５Ａと第２拡径部５Ｂとの間で嵌合穴５に接すると共に、第２ランド部６Ｂが第３拡径部５Ｃと第５拡径部５Ｅとの間で嵌合穴５に接し、第１負荷流路Ａを供給流路Ｐと遮断して第１排出流路Ｔ１に切換連通し、第２負荷流路Ｂを第２排出流路Ｔ２と遮断して供給流路Ｐに切換連通する。また、スプール６は第２切換位置で第１ランド部６Ａが第２拡径部５Ｂと第４拡径部５Ｄとの間で嵌合穴５に接すると共に、第２ランド部６Ｂが第１拡径部５Ａと第３拡径部５Ｃとの間で嵌合穴５に接し、第１負荷流路Ａを第１排出流路Ｔ１と遮断して供給流路Ｐに切換連通し、第２負荷流路Ｂを供給流路Ｐと遮断して第２排出流路Ｔ２に切換連通する。   The spool 6 is in the neutral position shown in FIG. 1 when the solenoids 2 and 3 are not energized, the first switching position when the solenoid 2 is energized and slid rightward in FIG. It is provided so as to be switchable to three positions with the second switching position by sliding to the right. The spool 6 is in a neutral position, the first land portion 6A is located in the second enlarged diameter portion 5B, the second land portion 6B is located in the third enlarged diameter portion 5C, and the supply flow path P and the first The load flow path A, the second load flow path B, the first discharge flow path T1, and the second discharge flow path T2 are communicated with each other. In the spool 6 at the first switching position, the first land portion 6A is in contact with the fitting hole 5 between the first enlarged diameter portion 5A and the second enlarged diameter portion 5B, and the second land portion 6B is in the third enlarged position. Between the diameter portion 5C and the fifth enlarged diameter portion 5E, the fitting hole 5 is contacted, the first load flow path A is cut off from the supply flow path P, and the first discharge flow path T1 is switched to communicate with the second load. The flow path B is cut off from the second discharge flow path T2 and switched to the supply flow path P. In the spool 6 at the second switching position, the first land portion 6A is in contact with the fitting hole 5 between the second enlarged diameter portion 5B and the fourth enlarged diameter portion 5D, and the second land portion 6B is in the first enlarged position. Between the diameter portion 5A and the third enlarged diameter portion 5C, the fitting hole 5 is contacted, the first load flow path A is cut off from the first discharge flow path T1, and the supply flow path P is switched to communicate with the second load. The flow path B is cut off from the supply flow path P and switched to the second discharge flow path T2.

次に、かかる構成の作動を説明する。
図１及び図２の状態で、供給流路Ｐを流体源に、第１負荷流路Ａと第２負荷流路Ｂを流体アクチュエータに、第１排出流路Ｔ１と第２排出流路Ｔ２を低圧側としてのタンクにそれぞれ接続する。
スプール６は、ソレノイド２，３へ非通電状態であるため、ばね１０，１１で中立位置に保持され、供給流路Ｐと第１負荷流路Ａと第２負荷流路Ｂと第１排出流路Ｔ１と第２排出流路Ｔ２との間を連通している。供給流路Ｐの流体は環状隙間７に流入して嵌合穴５内を流れて第１排出流路Ｔ１，第２排出流路Ｔ２よりタンクに流出する。 Next, the operation of this configuration will be described.
1 and 2, the supply flow path P is used as a fluid source, the first load flow path A and the second load flow path B are used as fluid actuators, and the first discharge flow path T1 and the second discharge flow path T2 are set. Connect each tank to the low pressure side.
Since the spool 6 is not energized to the solenoids 2 and 3, the spool 6 is held in a neutral position by the springs 10 and 11, and the supply flow path P, the first load flow path A, the second load flow path B, and the first discharge flow The path T1 communicates with the second discharge channel T2. The fluid in the supply flow path P flows into the annular gap 7, flows through the fitting hole 5, and flows out from the first discharge flow path T1 and the second discharge flow path T2 to the tank.

スプール６が中立位置に保持された状態で、一方のソレノイド２を通電すると、スプール６をばね１１力に抗して図１の右方向に軸方向摺動して第１切換位置に切換え、供給流路Ｐより環状隙間７に流入した流体は第３拡径部５Ｃ、第２負荷流路Ｂを流れて流体アクチュエータに流入すると共に、流体アクチュエータより第１負荷流路Ａに流出した流体は第２拡径部５Ｂより第４拡径部５Ｄ、第１排出流路Ｔ１を流れてタンクに流出する。そして、一方のソレノイド２を非通電にすると、スプール６はばね１１力により図１の中立位置に復帰する。 When one solenoid 2 is energized while the spool 6 is held in the neutral position, the spool 6 is axially slid in the right direction in FIG. 1 against the force of the spring 11 and switched to the first switching position. The fluid that has flowed into the annular gap 7 from the flow path P flows into the fluid actuator through the third enlarged diameter portion 5C and the second load flow path B, and the fluid that has flowed out of the fluid actuator into the first load flow path A 2 From the large diameter portion 5B, the fourth large diameter portion 5D flows through the first discharge channel T1 and flows out to the tank. When one solenoid 2 is deenergized, the spool 6 returns to the neutral position in FIG.

また、スプール６が中立位置に保持された状態で、他方のソレノイド３を通電すると、スプール６をばね１０力に抗して図１の左方向に軸方向摺動して第２切換位置に切換え、供給流路Ｐより環状隙間７に流入した流体は第２拡径部５Ｂ、第１負荷流路Ａを流れて流体アクチュエータに流入すると共に、流体アクチュエータより第２負荷流路Ｂに流出した流体は第３拡径部５Ｃより第５拡径部５Ｅ、第２排出流路Ｔ２を流れてタンクに流出する。そして、他方のソレノイド３を非通電にすると、スプール６はばね１０力により中立位置に復帰する。 When the other solenoid 3 is energized while the spool 6 is held at the neutral position, the spool 6 is axially slid leftward in FIG. 1 against the force of the spring 10 and switched to the second switching position. The fluid that has flowed into the annular gap 7 from the supply flow path P flows through the second enlarged diameter portion 5B and the first load flow path A to flow into the fluid actuator, and flows out from the fluid actuator to the second load flow path B. Flows from the third enlarged diameter portion 5C through the fifth enlarged diameter portion 5E and the second discharge flow path T2 to the tank. When the other solenoid 3 is deenergized, the spool 6 returns to the neutral position by the force of the spring 10.

かかる作動で、供給流路Ｐから環状隙間７に流入する流体は、流量調整部材８により、絞り穴９を通過せずに環状隙間７に流入して周方向の一方向に流れる流量Ｑ１と、絞り穴９を通過せずに環状隙間７に流入して周方向の他方向に流れる流量Ｑ２と、絞り穴９を通過して環状隙間７に流入して周方向の他方向に流れる流量Ｑ３とに分けられ、流量Ｑ１，Ｑ２，Ｑ３の関係を、Ｑ１＝Ｑ２＋Ｑ３からＱ３＝Ｑ１−Ｑ２となるよう設定しているため、流量が環状隙間７の周方向の一方向と他方向とに略同等に分配されて相対し、スプール６を回転しようとする力が周方向で平衡して、スプール６の回転を防止でき、特に、ソレノイド２，３の電磁力とこの電磁力により撓んで増加したばね１０，１１力とでスプール６を保持する第１切換位置や第２切換位置に比し、ソレノイド２，３の電磁力が作用せずにばね１０，１１の取付荷重でのみスプール６を保持している中立位置においても良好にスプール６の回転を防止できる。そして、供給流路Ｐに流量調整部材８を設けることでスプール６の回転を防止しているため、スプール６に回転を防止する構成を格別に施すことなくスプール６の回転を防止でき、構成を簡素化することができる。   With this operation, the fluid flowing into the annular gap 7 from the supply flow path P flows into the annular gap 7 without passing through the throttle hole 9 by the flow rate adjusting member 8 and flows in one direction in the circumferential direction, A flow rate Q2 that flows into the annular gap 7 without passing through the throttle hole 9 and flows in the other direction in the circumferential direction, and a flow rate Q3 that flows through the throttle hole 9 into the annular gap 7 and flows in the other direction in the circumferential direction Since the relationship between the flow rates Q1, Q2, and Q3 is set so that Q1 = Q2 + Q3 to Q3 = Q1-Q2, the flow rate is substantially equal in one direction in the circumferential direction of the annular gap 7 and in the other direction. And the force to rotate the spool 6 is balanced in the circumferential direction so that the spool 6 can be prevented from rotating. In particular, the electromagnetic force of the solenoids 2 and 3 and the spring increased by bending due to this electromagnetic force. The first switching position for holding the spool 6 with 10, 11 force, Compared to second switching position, it is also prevented satisfactorily rotation of the spool 6 at the neutral position where the electromagnetic force of the solenoid 2 is holding the spool 6 only in the mounting load of the spring 10, 11 does not act. And since the rotation of the spool 6 is prevented by providing the flow rate adjusting member 8 in the supply flow path P, the rotation of the spool 6 can be prevented without specially providing the structure for preventing the spool 6 from rotating. It can be simplified.

また、スプール６に回転を防止する構成を格別に施すことなくできるため、スプールを中立位置に保持するばねの一方を、回転止め部材と干渉しないよう他方のばねより小径のものを用いなければならない従来のスプール回転防止構造に比し、スプール６を中立位置に保持するばね１０，１１をスプール６の両側に同一のものを備えることができ、必要とする部品の種類を削減することができる。 In addition, since the spool 6 can be configured without any special configuration to prevent rotation, one of the springs that hold the spool in the neutral position must be smaller in diameter than the other spring so as not to interfere with the rotation stop member. Compared to a conventional spool rotation prevention structure, the same springs 10 and 11 for holding the spool 6 in the neutral position can be provided on both sides of the spool 6, and the number of necessary parts can be reduced.

また、供給流路Ｐが開口する嵌合穴５の第１拡径部５Ａ内径をスプール６の外径より大きく設け、供給流路Ｐを嵌合穴５の中心より径方向外側に偏移して嵌合穴５の第１拡径部５Ａに接線方向で接続しているため、供給流路Ｐを嵌合穴５の第１拡径部５Ａ内周面へ先端部に加えて側面部を開口できて供給流路Ｐの嵌合穴５への開口面積を大きくすることができ、供給流路Ｐを大径にすることなく供給流路Ｐから環状隙間７に流入する流体の流量増加を図ることができる。 Further, the inner diameter of the first enlarged diameter portion 5A of the fitting hole 5 in which the supply flow path P is opened is larger than the outer diameter of the spool 6, and the supply flow path P is shifted radially outward from the center of the fitting hole 5. Since the connection passage P is connected to the first enlarged portion 5A of the fitting hole 5 in the tangential direction, the side portion is added to the inner peripheral surface of the first enlarged portion 5A of the fitting hole 5 in addition to the tip portion. The opening area of the supply channel P to the fitting hole 5 can be increased, and the flow rate of the fluid flowing from the supply channel P into the annular gap 7 can be increased without increasing the diameter of the supply channel P. Can be planned.

また、流量調整部材８は流体が流通する絞り穴９を貫通形成し、供給流路Ｐから絞り穴９を通過して環状隙間７に流入する流体と供給流路Ｐから絞り穴９を通過せずに環状隙間７に流入する流体とに分配し、この分配した流体を環状隙間７の周方向の一方向と他方向とに対向して流量を略同等に調整する流体としているため、この略同等に調整する流体の流量を絞り穴９の開口面積、軸方向寸法の大きさに応じて精度良く設定することができる。 The flow rate adjusting member 8 penetrates the throttle hole 9 through which the fluid flows, and allows the fluid flowing from the supply channel P through the throttle hole 9 to flow into the annular gap 7 and the throttle channel 9 from the supply channel P. Without being distributed to the fluid that flows into the annular gap 7 and the distributed fluid is a fluid that adjusts the flow rate substantially the same in one circumferential direction and the other direction of the annular gap 7. The flow rate of the fluid to be adjusted equally can be accurately set according to the opening area of the throttle hole 9 and the size of the axial direction.

なお、一実施形態では、スプール弁としてソレノイド２，３によりスプール６を切換える電磁切換弁としたが、パイロット流体によりスプールを切換えるパイロット切換弁や機械操作でスプールを切換える機械操作式の切換弁でも良い。また、スプール６は中立位置と第１切換位置と第２切換位置との３位置に切換自在に設けたが、２位置や４位置に切換自在に設けたものでも良い。さらに、第１負荷流路Ａと第２負荷流路Ｂとの２個の負荷流路を設けると共に、第１排出流路Ｔ１と第２排出流路Ｔ２との２個の排出流路を設けたが、１個の負荷流路や１個の排出流路でも良いことは勿論である。 In one embodiment shaped state, but the electromagnetic switching valve for switching the spool 6 by the solenoid 2,3 as a spool valve, the switching valve of the machine operated for switching the spool in the pilot selector valve and machine operation to switch the spool by a pilot fluid But it ’s okay. Further, the spool 6 is provided so as to be switchable between three positions of the neutral position, the first switching position, and the second switching position, but may be provided so as to be switchable to two positions or four positions. Furthermore, two load channels, a first load channel A and a second load channel B, are provided, and two discharge channels, a first discharge channel T1 and a second discharge channel T2, are provided. However, it is needless to say that one load channel or one discharge channel may be used.

本発明の一実施形態を示した電磁切換弁の縦断面図である。It is a longitudinal cross-sectional view of the electromagnetic switching valve which showed one Embodiment of this invention. 図１の線Ｘ−Ｘに沿った拡大断面図である。It is an expanded sectional view along line XX of FIG.

１：本体
５：嵌合穴
６：スプール
７：環状隙間
８：流量調整部材
Ｐ：供給流路
Ａ：第１負荷流路（負荷流路）
Ｂ：第２負荷流路（負荷流路）
Ｔ１：第１排出流路（排出流路）
Ｔ２：第２排出流路（排出流路） 1: Body 5: Fitting hole 6: Spool 7: Annular gap
8: Flow rate adjusting member
P: Supply channel A: First load channel (load channel)
B: Second load channel (load channel)
T1: First discharge channel (discharge channel)
T2: Second discharge channel (discharge channel)

Claims (1)

本体に軸方向へ嵌合穴を穿設すると共に、流体を流入する供給流路と流体を流入出する負荷流路と流体を流出する排出流路とを軸方向へ間隙を有して嵌合穴内周面に開口して設け、嵌合穴には前記複数の流路間を切換連通するスプールを軸方向へ摺動自在に挿入し、供給流路が開口する箇所の嵌合穴内周面とスプール外周面との間に環状隙間を形成し、供給流路には環状隙間に流入する流体の流量を環状隙間の周方向の一方向と他方向とに対向して略同等に調整する流量調整部材を設け、前記スプールを中立位置に保持するばねを前記スプールの両側に備え、前記供給流路が開口する個所の前記嵌合穴内径を前記スプールの外径より大きく設け、前記供給流路を前記嵌合穴の中心より径方向外側に偏移して前記嵌合穴に接線方向で接続し、前記流量調整部材は流体が流通する絞り穴を貫通形成し、前記供給流路から前記絞り穴を通過して前記環状隙間に流入する流体と前記供給流路から前記絞り穴を通過せずに前記環状隙間に流入する流体とに分配し、この分配した流体を前記環状隙間の周方向の一方向と他方向とに対向して流量を略同等に調整することを特徴とするスプール弁のスプール回転防止構造。 A fitting hole is drilled in the body in the axial direction, and a supply flow path for flowing in fluid, a load flow path for flowing in and out fluid, and a discharge flow path for flowing out fluid are fitted with a gap in the axial direction. An opening is provided on the inner peripheral surface of the hole, and a spool for switching communication between the plurality of flow paths is inserted into the fitting hole so as to be slidable in the axial direction. An annular clearance is formed between the outer circumferential surface of the spool, and the flow rate adjustment that adjusts the flow rate of the fluid flowing into the annular clearance in the supply flow path in a substantially equal manner opposite to the circumferential direction in the circumferential direction of the annular clearance. Members are provided , springs for holding the spool in a neutral position are provided on both sides of the spool, the fitting hole inner diameter where the supply channel opens is larger than the outer diameter of the spool, and the supply channel is Shifted radially outward from the center of the fitting hole and connected to the fitting hole in a tangential direction, The flow rate adjusting member is formed by penetrating a throttle hole through which a fluid flows, and the fluid that passes through the throttle hole from the supply flow path and flows into the annular gap and the annular shape without passing through the throttle hole from the supply flow path. Spool rotation prevention of the spool valve, wherein the spool valve is distributed to the fluid flowing into the gap and the flow rate is adjusted to be substantially equal while facing the one direction and the other direction of the circumferential direction of the annular gap. Construction.

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