JPH02261911A - Fluid pressure driving continuous operating reciprocating actuator - Google Patents
Fluid pressure driving continuous operating reciprocating actuatorInfo
- Publication number
- JPH02261911A JPH02261911A JP1084329A JP8432989A JPH02261911A JP H02261911 A JPH02261911 A JP H02261911A JP 1084329 A JP1084329 A JP 1084329A JP 8432989 A JP8432989 A JP 8432989A JP H02261911 A JPH02261911 A JP H02261911A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- chamber
- fluid pressure
- valve
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 53
- 230000007246 mechanism Effects 0.000 claims abstract description 64
- 230000009471 action Effects 0.000 claims description 29
- 230000004048 modification Effects 0.000 description 8
- 238000012986 modification Methods 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000007789 sealing Methods 0.000 description 6
- 230000001105 regulatory effect Effects 0.000 description 5
- 238000005192 partition Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000004044 response Effects 0.000 description 2
- 230000004308 accommodation Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
Landscapes
- Reciprocating Pumps (AREA)
- Actuator (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、流体圧駆動連続作動型往復動アクチュエータ
に関し、特に加圧エアや油圧の供給を受けて出力ロッド
を連続的に往復駆動するアクチュエータに関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a fluid pressure-driven continuously operating reciprocating actuator, and particularly to an actuator that continuously reciprocates an output rod by receiving pressurized air or oil pressure. Regarding.
従来、この種の流体圧駆動連続作動型往復動アクチュエ
ータとしては、ハウジング内にバネ復帰型単動流体圧シ
リンダを組込み、シリンダの作動室に対して流体圧供給
口と排出口とを方向切換弁機構の切換作動により択一的
に連通可能にし、作動室と供給口が連通されると供給さ
れた流体圧く通常は圧縮空気）によりピストンと出力ロ
ッドが復帰バネに抗して進出駆動され、また作動室が排
出口に連通されるとピストンと出力ロッドが復帰バネに
より後退駆動され、且つピストンに連動連結された制御
弁機構により制御用流体圧流路が切換えられて方向切換
弁機構を切換作動させるように構成したものが知られて
いる。Conventionally, this type of fluid-pressure-driven continuous-acting reciprocating actuator incorporates a spring return type single-acting fluid pressure cylinder in the housing, and connects the fluid pressure supply port and discharge port to the working chamber of the cylinder using a directional control valve. Communication is selectively enabled by the switching operation of the mechanism, and when the working chamber and the supply port are communicated, the piston and output rod are driven forward against the return spring by the supplied fluid pressure (usually compressed air). Furthermore, when the working chamber is communicated with the discharge port, the piston and output rod are driven backward by the return spring, and the control fluid pressure flow path is switched by the control valve mechanism interlocked with the piston to switch the direction switching valve mechanism. There are known devices configured to do this.
本願出願人は、特公昭５５−４０７６１号公報に示すよ
うに、従来装置の諸欠点を解消して小型・軽量にして比
較的安価に製作でき且つ作動確実性と耐久性に優れたも
のを実用化した。As shown in Japanese Patent Publication No. 55-40761, the applicant has put into practical use a device that eliminates the various drawbacks of conventional devices, is small and lightweight, can be manufactured at a relatively low cost, and has excellent operational reliability and durability. It became.
上記往復動アクチュエータは、作動室に供給される流体
圧でピストンと出力ロットを進出駆動させ、また復帰バ
ネでピストンと出力ロッドを復帰作動させる構成となっ
ていたので、次のような諸欠点が残っている。The above-mentioned reciprocating actuator has a structure in which the piston and output rod are moved forward by the fluid pressure supplied to the working chamber, and the piston and output rod are moved back by the return spring, so it has the following drawbacks. Remaining.
上記往復動アクチュエータをプランジャ型油圧ポンプ駆
動用のアクチュエータに適用した場合を例にして説明す
ると、復帰バネを収容する為にピストンの往復動ストロ
ークと最大圧縮状態の復帰バネの長さの合計長さ以上の
バネ収容室を設けなければならないのでアクチュエータ
が大型化すること、出力アップつまり油圧ポンプの吐出
量増加の為にピストンの往復動サイクルを高速化すると
復帰バネが追従不能となり復帰バネが破損してしまうの
で高速化に限界があること、油圧ポンプの吐出量増加の
為にピストン及び出力ロッドのストロークを大きくする
と、復帰バネのバネ長が大きくなるので大型の復帰バネ
が必要となり全体として大型化してしまうこと、復帰バ
ネの追従性を高める為に復帰バネのバネ力を強くすると
１サイクル当りの出力が低下し油圧ポンプの吐出圧が低
下してしまうこと及び低圧の流体圧で駆動できなくなっ
て油圧ポンプの汎用性が低下すること、など種々の問題
がある。To explain the case where the above reciprocating actuator is applied to an actuator for driving a plunger type hydraulic pump as an example, in order to accommodate the return spring, the total length of the reciprocating stroke of the piston and the length of the return spring in the maximum compression state is required. The actuator becomes larger because it is necessary to provide more spring accommodation chambers, and if the reciprocating cycle of the piston is made faster to increase the output, that is, increase the discharge amount of the hydraulic pump, the return spring will not be able to follow the movement and the return spring will be damaged. If the stroke of the piston and output rod is increased to increase the discharge amount of the hydraulic pump, the spring length of the return spring will become larger, which will require a larger return spring and increase the overall size. If you increase the spring force of the return spring to improve its followability, the output per cycle will decrease and the discharge pressure of the hydraulic pump will decrease, and the hydraulic pump will not be able to drive with low fluid pressure. There are various problems such as a decrease in the versatility of the hydraulic pump.
本発明は、復帰バネに代えて流体圧によりピストンを復
帰駆動し得るような流体圧駆動連続作動型往復動アクチ
ュエータを提供することを目的とする。SUMMARY OF THE INVENTION An object of the present invention is to provide a fluid pressure-driven continuously operated reciprocating actuator that can return a piston using fluid pressure instead of a return spring.
本発明に係る流体圧駆動連続作動型往復動アクチュエー
タは、ハウジング内にピストンとこのピストンに固着さ
れた出力ロッドとを有する複動流体圧シリンダを設け、
この流体圧シリンダにピストンを流体圧で進出駆動する
往動作動室とピストンを流体圧で後退駆動する復動作動
室を設け、上記往動作動室を流体圧供給口に接続する供
給位置と排出口に接続する排出位置とに択一的に切換え
られる切換弁体と、この切換弁体を供給位置に付勢する
付勢手段と、その付勢力に抗して切換弁体を流体圧で排
出位置に切換える弁作動室とを備えた切換弁機構を設け
、上記ピストンから延び切換弁体に挿通された弁部材を
介して、ピストンが後退限位置にあるときは弁作動室を
排出口に接続し且つピストンが後退限位置と進出限位置
の間にあるときは弁作動室を封止し且つピストンが進出
限位置にあるときは弁作動室を流体圧供給口に接続する
制御弁機構を設け、上記ピストンの進出作動時、復動作
動室内の流体圧が第１設定圧より高いときに開弁して復
動作動室を排出口に接続するリリーフ弁機構を設け、上
記ピストンの後退作動時、復動作動室内の流体圧が第１
設定圧以下の第２設定圧未満のときに開弁して復動作動
室を流体圧供給口に接続する供給弁機構を設けたもので
ある。A fluid-pressure-driven continuously operating reciprocating actuator according to the present invention includes a double-acting fluid-pressure cylinder having a piston and an output rod fixed to the piston in a housing,
This fluid pressure cylinder is provided with a forward motion chamber that drives the piston forward using fluid pressure and a backward motion chamber that drives the piston backward using fluid pressure, and a supply position and an exhaust position that connect the forward motion chamber to the fluid pressure supply port. A switching valve body connected to an outlet and selectively switched to a discharge position, a biasing means for biasing the switching valve body to a supply position, and a fluid pressure to discharge the switching valve body against the biasing force. A switching valve mechanism is provided, which includes a valve operating chamber that is switched to a position, and the valve operating chamber is connected to the discharge port when the piston is at the retraction limit position via a valve member that extends from the piston and is inserted through the switching valve body. and a control valve mechanism is provided which seals the valve operating chamber when the piston is between the retraction limit position and the extension limit position and connects the valve operation chamber to the fluid pressure supply port when the piston is at the extension limit position. , a relief valve mechanism is provided which opens when the fluid pressure in the double action chamber is higher than the first set pressure when the piston moves forward to connect the double action chamber to the discharge port; , the fluid pressure in the double action chamber is the first
A supply valve mechanism is provided which opens the valve when the pressure is lower than the second set pressure and connects the double action chamber to the fluid pressure supply port.
本発明に係る流体圧駆動連続作動型往復動アクチュエー
タにおいては、流体圧供給口に圧力流体が供給されてい
る状態で、ピストンが後退限位置にあるときには制御弁
機構によって弁作動室が排出口に接続されているので、
切換弁体は付勢手段により供給位置に保持され、圧力流
体が流体圧供給口から往動作動室へ供給され、ピストン
は往動作動室内の流体圧によって復動作動室内の流体圧
に抗して進出駆動される。ピストンが後退限位置から進
出限位置に達するまでは制御弁機構によって弁作動室が
流体圧排出状態で封止されるので切換弁体は供給位置に
保持される。従って、上記のように往動作動室に圧力流
体が供給され、ピストンは進出駆動される。この間復動
作動室内の流体は加圧され、第１設定圧より高くなると
リリーフ弁機構によりリリーフされるので第１設定圧に
保持される。In the fluid pressure-driven continuously operating reciprocating actuator according to the present invention, when the piston is at the retraction limit position with pressure fluid being supplied to the fluid pressure supply port, the valve operating chamber is moved to the discharge port by the control valve mechanism. Since it is connected,
The switching valve body is held in the supply position by the biasing means, pressure fluid is supplied from the fluid pressure supply port to the forward movement chamber, and the piston resists the fluid pressure in the backward movement chamber by the fluid pressure in the forward movement chamber. is driven forward. Until the piston reaches the retraction limit position from the retraction limit position, the valve operating chamber is sealed in a fluid pressure discharged state by the control valve mechanism, so that the switching valve body is held in the supply position. Therefore, as described above, pressure fluid is supplied to the forward movement chamber, and the piston is driven to move forward. During this time, the fluid in the reciprocating movement chamber is pressurized, and when it becomes higher than the first set pressure, it is relieved by the relief valve mechanism, so that the fluid is maintained at the first set pressure.
その後、ピストンが進出限位置に達すると、制御弁機構
により弁作動室が流体圧供給口に接続され、切換弁体は
弁作動室内の流体圧により付勢手段の付勢力に抗して排
出位置に切換えられるので、往動作動室は排出口に接続
され、復動作動室内の第１設定圧の圧力流体によりピス
トンは後退駆動を開始する。ピストンが進出限位置から
後退限位置に達するまでは弁作動室が流体圧充填状態で
封止されるので切換弁体は排出位置に保持される。After that, when the piston reaches the extension limit position, the valve operating chamber is connected to the fluid pressure supply port by the control valve mechanism, and the switching valve body is moved to the discharge position by the fluid pressure in the valve operating chamber against the urging force of the urging means. Therefore, the forward motion chamber is connected to the discharge port, and the piston starts to be driven backward by the pressure fluid at the first set pressure in the backward motion chamber. Since the valve operating chamber is filled with fluid pressure and sealed until the piston reaches the backward limit position from the forward limit position, the switching valve body is held in the discharge position.
上記ピストンの後退に応して復動作動室内の流体圧が第
１設定圧以下の第２設定圧より低下したときには供給弁
機構が開いて復動作動室へ圧力流体が供給されるので第
２設定圧に保持され、ピストンは後退していく。こうし
て、ピストンが後退限位置に達すると、制御弁機構によ
り弁作動室が排出口に接続され、切換弁体が供給位置に
切換えられ、以下前記同様に繰返し、ピストンは往復駆
動されることになる。When the fluid pressure in the double action chamber falls below the second set pressure which is lower than the first set pressure in response to the retraction of the piston, the supply valve mechanism opens and pressurized fluid is supplied to the double action chamber. The set pressure is maintained and the piston moves backward. In this way, when the piston reaches the retraction limit position, the valve operating chamber is connected to the discharge port by the control valve mechanism, the switching valve body is switched to the supply position, and the same as above is repeated, and the piston is driven back and forth. .
本発明の往復動アクチュエータにおいては、復動作動室
内に第１設定圧以下且つ第２設定圧以上の流体圧を保持
し、その流体圧でピストンを後退駆動するように構成し
たので、復帰バネを省略することが可能となり、往復動
サイクルを高速化して往復動アクチュエータの出力アッ
プを実現出来、ピストンの往復動のストロークを必要に
応して自由に大きく或いは小さく設計することが出来、
復動作動室はピストンの往復動ストロークに必要なだけ
の小型の作動室に形成できるため、往復動アクチュエー
タの小型化を図ることが出来る。しかも、第１設定圧及
び第２設定圧は必要に応して調節可能にも構成し得るの
で往復動アクチュエータの汎用性を向上させることも可
能である。In the reciprocating actuator of the present invention, a fluid pressure lower than the first set pressure and higher than the second set pressure is maintained in the double motion chamber, and the piston is driven backward by the fluid pressure. This makes it possible to speed up the reciprocating cycle and increase the output of the reciprocating actuator, and the reciprocating stroke of the piston can be freely designed to be larger or smaller as necessary.
Since the reciprocating movement chamber can be formed into a small-sized working chamber that is necessary for the reciprocating stroke of the piston, it is possible to downsize the reciprocating actuator. Moreover, since the first set pressure and the second set pressure can be configured to be adjustable as necessary, it is also possible to improve the versatility of the reciprocating actuator.
本発明に係る流体圧駆動連続作動型往復動アクチュエー
タによれば、上記〔作用〕の項で説明したように、リリ
ーフ弁機構と供給弁機構とによってピストンの位置に拘
らず復動作動室内の圧力流体を所定の範囲の圧力に保持
し、その圧力流体によりピストンを後退駆動するように
構成したことにより、復帰バネを省略できること、往復
動サイクルの高速化つまり出力アップを実現し得ること
、ピストンの往復動ストロークを必要に応して自由に大
きく或いは小さ（設計することが出来ること、復動作動
室を小型化して往復動アクチュエータを小型化し得るこ
と、往復動アクチュエータの汎用性を向上し得ること、
などの効果が得られる。According to the fluid pressure-driven continuously operating type reciprocating actuator according to the present invention, as explained in the [Function] section above, the relief valve mechanism and the supply valve mechanism reduce the pressure in the double action chamber regardless of the position of the piston. By maintaining the fluid at a predetermined pressure range and using the pressure fluid to drive the piston backward, the return spring can be omitted, the reciprocating cycle can be made faster, and the output can be increased. The reciprocating stroke can be freely designed to be larger or smaller as needed; the reciprocating actuator can be made smaller by making the reciprocating movement chamber smaller; and the versatility of the reciprocating actuator can be improved. ,
Effects such as this can be obtained.
以下、本発明の実施例について図面に基いて説明する。 Embodiments of the present invention will be described below with reference to the drawings.
本実施例は、圧縮空気（以下、加圧エアという）駆動連
続作動型往復動アクチュエータによりプランジャを駆動
するようにしたエア駆動式油圧ポンプに本発明を適用し
た場合の一例である。This embodiment is an example in which the present invention is applied to an air-driven hydraulic pump in which a plunger is driven by a continuously operating reciprocating actuator driven by compressed air (hereinafter referred to as pressurized air).
第１図に示すように、この油圧ポンプＨＰは往復動アク
チュエータＡＣとポンプ本体部ＰＣとを備え、往復動ア
クチュエータＡＣのハウジングｌＯは、上部ハウジング
１１と中間ハウジング１２と下部ハウジング１３とを複
数のコモンボルト１４で一体的に連結して構成されてい
る。As shown in FIG. 1, this hydraulic pump HP includes a reciprocating actuator AC and a pump main body PC, and the housing lO of the reciprocating actuator AC has an upper housing 11, an intermediate housing 12, a lower housing 13, and a plurality of They are integrally connected by a common bolt 14.
ハウジング１０内の下半部内には複動エアシリンダ２０
が設けられ、このエアシリンダ２０のシリンダ孔２１内
にはピストン２２が装着され、ピストン２２の下端から
延びる出力ロソド２３の下部にプランジャ２４が形成さ
れ、シリンダ孔２１のうちのピストン２２の上側には往
動作動室２５がまたピストン２２の下側には復動作動室
２６が夫々形成されている。Inside the lower half of the housing 10 is a double acting air cylinder 20.
A piston 22 is installed in the cylinder hole 21 of the air cylinder 20, and a plunger 24 is formed at the lower part of the output rod 23 extending from the lower end of the piston 22. A forward movement chamber 25 and a backward movement chamber 26 are formed below the piston 22, respectively.
下部ハウジング１３内にはプランジャ孔１５が設けられ
、プランジャ２４がプランジ中孔１５内に進退駆動され
゛、吸入口１６から吸入チエツク弁１７を介してプラン
ジャ孔１５に吸入された油はプランジャ２４により圧縮
され、吐出チエツク弁１８を介して吐出口１９へ吐出さ
れる。A plunger hole 15 is provided in the lower housing 13, and a plunger 24 is driven forward and backward into the plunger hole 15. It is compressed and discharged to the discharge port 19 via the discharge check valve 18.
−ト、記ハウジング１０の上部の側部には外部の加圧エ
ア供給源から加圧エア（例えば、５．０ｋｇ／ｃｄＧ）
が供給される加圧エア供給口３が設けられ、ハウジング
１０の上端部内には排気口としてのマフラ４を介して大
気中に連通ずる排気室５が形成されている。- Pressurized air (for example, 5.0 kg/cdG) is supplied to the upper side of the housing 10 from an external pressurized air supply source.
A pressurized air supply port 3 is provided to which air is supplied, and an exhaust chamber 5 is formed in the upper end of the housing 10 to communicate with the atmosphere via a muffler 4 serving as an exhaust port.
次に、切換弁機＃！３０について説明する。Next, the switching valve machine #! 30 will be explained.
中間ハウジング１２の仕切壁３１の上面には中間ハウジ
ング１２内に収容された環状部材３２が固着され、環状
部材３２の外周側には加圧エア供給口３に連なる加圧エ
ア供給路３３が形成され、仕切壁３１の凹部３４と環状
部材３２の内側には切換弁体３５が装着され、切換弁体
３５の下端部の下部ピストン部３６が凹部３４に気密摺
動自在に装着されるとともに、切換弁体３５の中段部に
は環状かつ鍔状の切換弁部３７が形成され、切換弁体３
５の上端部の上部ピストン部３８は環状部材３２のシリ
ンダ孔３９に気密摺動自在に内嵌され、切換弁部３７と
下部ピストン３６との間で切換弁体３５の外周部には排
気路４０により排気室５に連なる環状排気路４１が形成
され、切換弁部３７の外周側には通路４２ａにより往動
作動室２５に連なる環状通路４２が形成されている。環
状部材３２には切換弁部３７の上面の環状の第１弁面４
３が当接する第１弁座４４が形成され、仕切壁３１には
切換弁部３７の下面の環状の第２弁面４５が当接する第
２弁座４６が形成され、第１弁面４３と上部ピストン部
３８との間で切換弁体３５の外周側には通路４７により
加圧エア供給路３３に連なる環状の受圧室４８が形成さ
れ、切換弁体３５はスプリング４９で下方へ弾性付勢さ
れている。An annular member 32 housed in the intermediate housing 12 is fixed to the upper surface of the partition wall 31 of the intermediate housing 12, and a pressurized air supply path 33 connected to the pressurized air supply port 3 is formed on the outer peripheral side of the annular member 32. A switching valve body 35 is installed inside the recess 34 of the partition wall 31 and the annular member 32, and a lower piston portion 36 at the lower end of the switching valve body 35 is installed in the recess 34 in an airtight and slidable manner. An annular and brim-shaped switching valve portion 37 is formed in the middle part of the switching valve body 35.
The upper piston part 38 at the upper end of the switching valve body 35 is fitted into the cylinder hole 39 of the annular member 32 in an airtight and slidable manner. 40 forms an annular exhaust passage 41 which is connected to the exhaust chamber 5, and an annular passage 42 which is connected to the forward motion chamber 25 by a passage 42a is formed on the outer peripheral side of the switching valve portion 37. The annular member 32 has an annular first valve surface 4 on the upper surface of the switching valve section 37.
3 is in contact with the first valve seat 44, and the partition wall 31 is formed with a second valve seat 46 in which the annular second valve surface 45 on the lower surface of the switching valve part 37 is in contact. An annular pressure receiving chamber 48 connected to the pressurized air supply path 33 is formed by a passage 47 on the outer circumferential side of the switching valve body 35 between the upper piston portion 38 and the switching valve body 35 is elastically biased downward by a spring 49. has been done.
上記切換弁体３５の第２弁面４５が第２弁座４６に当接
したときには第１弁面４３と第１弁座４４間が開き、往
動作動室２５は通路４２ａ、環状通路４２、受圧室４８
、通路４７及び加圧エア供給路３３により加圧エア供給
口３に連通される。When the second valve surface 45 of the switching valve body 35 comes into contact with the second valve seat 46, the space between the first valve surface 43 and the first valve seat 44 opens, and the forward movement chamber 25 includes the passage 42a, the annular passage 42, Pressure receiving chamber 48
, a passage 47 and a pressurized air supply path 33 communicate with the pressurized air supply port 3 .
従って、このときの切換弁体３５の位置を供給位置とい
う。Therefore, the position of the switching valve body 35 at this time is called the supply position.
上記切換弁体３５の第１弁面４３が第１弁座４４に当接
したときには第２弁面４５と第２弁座４６間が開き、往
動作動室２５は通路４２ａ１環状通路４２、環状排気路
４１及び排気路４０により排気室５に連通される。従っ
て、このときの切換弁体３５の位置を排出位置という。When the first valve surface 43 of the switching valve body 35 comes into contact with the first valve seat 44, the space between the second valve surface 45 and the second valve seat 46 opens, and the forward movement chamber 25 is divided into the passage 42a1, the annular passage 42, the annular passage 42, and the annular passage 42a. It communicates with the exhaust chamber 5 through an exhaust path 41 and an exhaust path 40 . Therefore, the position of the switching valve body 35 at this time is called the discharge position.
上記切換弁体３５の下部ピストン３６と凹部３４とで弁
作動室５０が形成され、弁作動室５０に加圧エアが供給
されないときには、切換弁体３５は受圧室４８の加圧エ
アとスプリング４９とで供給位置に付勢され、弁作動室
５０に後述のように加圧エアが供給されたときには、切
換弁体３５は排出位置へ切換えられる。A valve operating chamber 50 is formed by the lower piston 36 and the recess 34 of the switching valve body 35, and when pressurized air is not supplied to the valve operating chamber 50, the switching valve body 35 uses the pressurized air in the pressure receiving chamber 48 and the spring 49. When pressurized air is supplied to the valve operating chamber 50 as described later, the switching valve body 35 is switched to the discharge position.
次に、制御弁機構６０について説明する。Next, the control valve mechanism 60 will be explained.
上記ピストン２２の中心部に固着されたロッド状の弁部
材６１は、仕切壁３１の摺動孔６２と切換弁体３５の挿
通孔６３とを挿通して上方へ延び、弁部材６１の途中部
には小径部６４が形成され、摺動孔６２の内周部には弁
部材６１の外周面に気密状に圧接される上下１対のＯリ
ング６５・６６が装着され、挿通孔６３の上端部の内周
部には弁部材６１の外周面に気密状に圧接される０リン
グ６７が装着され、仕切壁３１には加圧エア供給口３に
連なる加圧エア通路６８がＯリング６５・６６の外側ま
で形成されている。A rod-shaped valve member 61 fixed to the center of the piston 22 extends upward through a sliding hole 62 of the partition wall 31 and an insertion hole 63 of the switching valve body 35. A small-diameter portion 64 is formed in the sliding hole 62, and a pair of upper and lower O-rings 65 and 66 are attached to the inner circumferential portion of the sliding hole 62 and are pressed against the outer circumferential surface of the valve member 61 in an airtight manner. An O-ring 67 is attached to the inner periphery of the valve member 61, and the O-ring 67 is connected to the outer periphery of the valve member 61 in an airtight manner. It is formed to the outside of 66.
上記ピストン２２が第１図に図示の後退限位置にあると
きには、小径部６４によりＯリング６７の封止が解除さ
れ、弁作動室５０が挿通孔６３の弁部材６１の外側の環
状隙間６９により排気室５に連通され、またピストン２
２が第２図に図示の進出限位置にあるときにはＯリング
６７により環状隙間６９が封止されるとともに小径部６
４により０リング６５の封止が解除されて加圧エア通路
６８が弁作動室５０に連通され、またピストン２２が後
退限位置と進出服位置の間にあるときには両０リング６
５・６７により弁作動室５０は封止される。When the piston 22 is at the retraction limit position shown in FIG. It communicates with the exhaust chamber 5, and the piston 2
2 is at the advanced limit position shown in FIG.
4, the sealing of the O-ring 65 is released and the pressurized air passage 68 is communicated with the valve operating chamber 50, and when the piston 22 is between the retraction limit position and the advanced position, both O-rings 6
5.67 seals the valve operating chamber 50.
次に、リリーフ弁機構８０と供給弁機構８１について説
明する。Next, the relief valve mechanism 80 and the supply valve mechanism 81 will be explained.
この往復動アクチュエータＡＣは、往動作動室２５に供
給された加圧エアによりピストン２２と出力ロット２３
を進出駆動させ、また復動作動室２６内に常時収容され
ている第１設定圧（例えば、０．５ｋｇ／ｃｎｌＧ）以
下且つ第２設定圧（例えば、０゜４ ｋｇ ／ ａｌ
Ｇ ）以上の加圧エアによりピストン２２と出力ロット
２３を後退駆動させるように構成されている。その為、
ピストン２２の進出作動時復動作動室２６内の加圧エア
の圧力が第１設定圧より高いときにリリーフ作動するリ
リーフ弁機構８０と、ピストン２２の後退作動時復動作
動室２６内の加圧エアの圧力が第２設定圧未満のときに
加圧エアを供給する供給弁機構８１が次のように設けら
れている。This reciprocating actuator AC is moved between the piston 22 and the output rod 23 by pressurized air supplied to the reciprocating movement chamber 25.
The pressure is lower than the first set pressure (e.g., 0.5 kg/cnlG) and the second set pressure (e.g., 0°4 kg/al.
G) The piston 22 and the output rod 23 are configured to be driven backward by the above pressurized air. For that reason,
A relief valve mechanism 80 that performs relief operation when the pressure of pressurized air in the double action chamber 26 when the piston 22 moves forward is higher than the first set pressure, and a relief valve mechanism 80 that operates in relief when the pressure of the pressurized air in the double action chamber 26 when the piston 22 moves backward; A supply valve mechanism 81 that supplies pressurized air when the pressure of the pressurized air is less than the second set pressure is provided as follows.
中間ハウジング１２内において環状部材３２には環状の
供給弁体８３が気密摺動自在に外嵌され、この供給弁体
８３の上方において上部ハウジング１１には環状のリリ
ーフ弁体８４が気密摺動自在に内嵌され、リリーフ弁体
８４の下面には環状の第３弁面８５が形成され、供給弁
体８３の上端部には第３弁面８５が当接する第３弁座８
６が形成され、供給弁体８３の中段外周段部の上面には
環状の第４弁面８７が形成され、上部ハウジング１１の
鍔部８９の下面には第４弁面８７が当接する第４弁座８
８が形成され、鍔部８９の上面にはリリーフ弁体８４の
下限位置を規制する第１規制部９０が形成され、環状部
材３２の外周部には供給弁体８３の下限位置を規制する
第２規制部９１が形成されている。An annular supply valve body 83 is fitted onto the annular member 32 in the intermediate housing 12 so as to be slidable in an airtight manner, and an annular relief valve body 84 is slidably and airtightly fitted in the upper housing 11 above the supply valve body 83. An annular third valve surface 85 is formed on the lower surface of the relief valve body 84 , and a third valve seat 8 with which the third valve surface 85 abuts is formed on the upper end of the supply valve body 83 .
6 is formed, an annular fourth valve surface 87 is formed on the upper surface of the middle outer peripheral step of the supply valve body 83, and a fourth valve surface 87 abuts on the lower surface of the flange 89 of the upper housing 11. Valve seat 8
8 is formed, a first regulating part 90 for regulating the lower limit position of the relief valve element 84 is formed on the upper surface of the flange part 89, and a first regulating part 90 for regulating the lower limit position of the supply valve element 83 is formed on the outer periphery of the annular member 32. Two regulating portions 91 are formed.
上記上部ハウジング１１とリリーフ弁体８４と供給弁体
８３間には環状受圧室９２が形成され、供給弁体８３と
環状部材３２間には連通孔９３ａにより環状受圧室９２
に連通された環状の背圧室９３が形成され、環状受圧室
９２は通路９４、ボルト孔と共通の環状通路９５及び中
間ハウジング１２の下端の孔９６により復動作動室２６
に連通されている。An annular pressure receiving chamber 92 is formed between the upper housing 11, the relief valve body 84 and the supply valve body 83, and a communication hole 93a is formed between the supply valve body 83 and the annular member 32.
An annular back pressure chamber 93 is formed which communicates with the double action chamber 26 , and the annular pressure receiving chamber 92 is formed by a passage 94 , an annular passage 95 common to the bolt hole, and a hole 96 at the lower end of the intermediate housing 12 .
is communicated with.
更に、ＩＪ ＩＪ−フ弁体８４は第１設定圧を設定する
為の圧縮コイルスプリングからなる第１スプリング９７
で下方へ弾性付勢され、供給弁体８３は第１スプリング
９７と協働して第２設定圧を設定する為の圧縮コイルス
プリングからなる第２スプリング９８で上方へ弾性付勢
されている。Further, the IJ IJ-F valve body 84 has a first spring 97 made of a compression coil spring for setting the first set pressure.
The supply valve body 83 is elastically urged downward by a second spring 98, which is a compression coil spring that cooperates with the first spring 97 to set a second set pressure.
復動作動室２６内の加圧エアの圧力が第１設定圧以下且
つ第２設定圧以上のときにリリーフ弁体８４と供給弁体
８３は第１図に図示の状態を保持し、第３弁面８５と第
３弁座８６間及び第４弁面８７と第４弁座８８間が夫々
閉じられている。When the pressure of the pressurized air in the double action chamber 26 is lower than the first set pressure and higher than the second set pressure, the relief valve body 84 and the supply valve body 83 maintain the state shown in FIG. A space between the valve surface 85 and the third valve seat 86 and a space between the fourth valve surface 87 and the fourth valve seat 88 are respectively closed.
ピストン２２の進出作動時、復動作動室２６内の加圧エ
アの圧力が第１設定圧より高くなると、環状受圧室９２
の加圧エアによりリリーフ弁体８４が上方へ移動し、第
３弁面８５が第３弁座８．６から離れて加圧エアがリリ
ーフされるので、復動作動室２６の圧力は第１設定圧に
維持される。ピストン２２の後退作動時、復動作動室２
６内の加圧エアの圧力が第２設定圧より低くなると、第
１スプリング９７のバネ力でリリーフ弁体８４が第２ス
プリング９８に抗して供給弁体８３を下方へ押動するの
で第４弁面８７が第４弁座８８から離れ、加圧エア供給
路３３から環状受圧室９２へ加圧エアが供給されるので
、復動作動室２６の圧力は第２設定圧に維持される。When the piston 22 moves forward and the pressure of the pressurized air in the double action chamber 26 becomes higher than the first set pressure, the annular pressure receiving chamber 92
Pressurized air moves the relief valve body 84 upward, and the third valve surface 85 separates from the third valve seat 8.6, releasing the pressurized air, so that the pressure in the double action chamber 26 is reduced to the first Maintained at set pressure. When the piston 22 moves backward, the double movement chamber 2
When the pressure of the pressurized air in 6 becomes lower than the second set pressure, the relief valve body 84 pushes the supply valve body 83 downward against the second spring 98 due to the spring force of the first spring 97. Since the fourth valve surface 87 is separated from the fourth valve seat 88 and pressurized air is supplied from the pressurized air supply path 33 to the annular pressure receiving chamber 92, the pressure in the double action chamber 26 is maintained at the second set pressure. .
尚、上記第１〜第４弁面４３・４５・８５・８７には耐
摩耗性に優れる合成樹脂部材が埋込まれている。In addition, a synthetic resin member having excellent wear resistance is embedded in the first to fourth valve surfaces 43, 45, 85, and 87.
次に、上記往復動アクチュエータＡＣの作動について説
明する。Next, the operation of the reciprocating actuator AC will be explained.
加圧エア供給口３に加圧エアが供給されている状態で、
ピストン２２が後退限位置にあるときには制御弁機構６
０によって弁作動室５０が排気室５に接続されているの
で、切換弁体３５は受圧室４８の加圧エアとスプリング
４９の付勢力により供給位置に保持され、加圧エアが加
圧エア供給口３から往動作動室２５へ供給され、ピスト
ン２２は往動作動室２５内の加圧エアによつて復動作動
室２６内の加圧エアに抗して進出駆動される。ピストン
２２が後退限位置から進出限位置に達するまでは制御弁
機構６０によって弁作動室５０がエア圧排出状態で封止
されるので切換弁体３５は供給位置に保持される。従っ
て、上記のように往動作動室２５に加圧エアの供給が継
続され、ピストン２２は進出駆動される。この間復動作
動室２６内功エアは加圧され、第１設定圧より高くなる
とリリーフ弁機構８０によりリリーフされるので第１設
定圧に保持される。With pressurized air being supplied to the pressurized air supply port 3,
When the piston 22 is at the retraction limit position, the control valve mechanism 6
0 connects the valve operating chamber 50 to the exhaust chamber 5, the switching valve body 35 is held at the supply position by the pressurized air in the pressure receiving chamber 48 and the biasing force of the spring 49, and the pressurized air is supplied to the exhaust chamber 5. The piston 22 is supplied from the port 3 to the forward motion chamber 25 , and the piston 22 is driven forward by the pressurized air in the forward motion chamber 25 against the pressurized air in the backward motion chamber 26 . Since the valve operating chamber 50 is sealed in an air pressure discharge state by the control valve mechanism 60 until the piston 22 reaches the advanced limit position from the backward limit position, the switching valve body 35 is held in the supply position. Therefore, as described above, pressurized air continues to be supplied to the forward motion chamber 25, and the piston 22 is driven to move forward. During this time, the air in the reciprocating motion chamber 26 is pressurized, and when the pressure becomes higher than the first set pressure, it is relieved by the relief valve mechanism 80, so that the pressure is maintained at the first set pressure.
その後、ピストン２２が進出限位置に達すると、制御弁
機構６０により弁作動室５０が加圧エア供給口３に接続
され、切換弁体３５は弁作動室５０内の加圧エアにより
受圧室４８の加圧エアとスプリング４９の付勢力に抗し
て排出位置に切換えられるので、往動作動室２５は排気
室５に接続され、復動作動室２６内の第１設定圧の加圧
エアによりピストン２２は後退駆動を開始する。ピスト
ン２２が進出限値１から後退限位置に達するまでは弁作
動室５０が加圧エア充填状態で封止されるので切換弁体
３５は排出位置に保持される。上記ピストン２２の後退
に応して復動作動室２６内のエア圧が第１設定圧以下の
第２設定圧より低下したときには供給弁機構８１が開い
て復動作動室２６へ加圧エアが供給されるので第２設定
圧に保持され、ピストン２２の後退が′ｍ続される。こ
うして、ピストン２２が後退限位置に達すると、制御弁
機構６０により弁作動室５０が排気室５に接続され、切
換弁体３５が供給位置に切換えられ、以下前記同様に繰
返し、ピストン２２は往復駆動されることになる。Thereafter, when the piston 22 reaches the extension limit position, the valve operating chamber 50 is connected to the pressurized air supply port 3 by the control valve mechanism 60, and the switching valve body 35 is connected to the pressure receiving chamber 48 by the pressurized air in the valve operating chamber 50. The forward motion chamber 25 is connected to the exhaust chamber 5, and the forward motion chamber 25 is connected to the exhaust chamber 5, and the pressurized air at the first set pressure in the backward motion chamber 26 Piston 22 begins to drive backward. Since the valve operating chamber 50 is filled with pressurized air and sealed until the piston 22 reaches the backward limit position from the advance limit value 1, the switching valve body 35 is held at the discharge position. When the air pressure in the double action chamber 26 drops below the second set pressure which is lower than the first set pressure in response to the retraction of the piston 22, the supply valve mechanism 81 opens and pressurized air is supplied to the double action chamber 26. Since the pressure is supplied, the second set pressure is maintained, and the retraction of the piston 22 continues. In this way, when the piston 22 reaches the retraction limit position, the valve operating chamber 50 is connected to the exhaust chamber 5 by the control valve mechanism 60, and the switching valve body 35 is switched to the supply position. It will be driven.
以上の説明から明らかなように、往復動アクチュエータ
ＡＣにおいて、ピストン２２の往復作動に同期して切換
弁機構３０と制御弁機構６０によって、往動作動室２５
へ加圧エアが供給・排出され、またリリーフ弁機構８０
と供給弁機構８１によって復動作動室２６内には常時第
工設定圧以下且つ第２設定圧以上の加圧エアが保持され
るので、ピストン２２は往復動を連続的に繰返し、出力
ロット２３の先端のプランジャ２４はプランジャ孔１５
内で往復動を連続的に繰返すことになる。従って、油圧
ポンプ本体部ＰＣにおいては、油の吸入と圧縮・吐出と
を連続的に繰返すことになる。As is clear from the above description, in the reciprocating actuator AC, the switching valve mechanism 30 and the control valve mechanism 60 operate the reciprocating motion chamber 25 in synchronization with the reciprocating motion of the piston 22.
Pressurized air is supplied to and discharged from the relief valve mechanism 80.
Since pressurized air below the first set pressure and above the second set pressure is always maintained in the double action movement chamber 26 by the supply valve mechanism 81, the piston 22 continuously repeats reciprocating motion, and the output lot 23 The plunger 24 at the tip of the plunger hole 15
This means that the reciprocating motion will be repeated continuously. Therefore, in the hydraulic pump main body PC, suction, compression, and discharge of oil are continuously repeated.
このように、本実施例の油圧ポンプＨＰにおいては、加
圧エアによりピストン２２を後退駆動するように構成さ
れているので、ピストン２２を後退駆動させるための復
帰バネを省略することが可能となり、往復動サイクルを
高速化して往復動アクチュエータＡＣの出力アップを図
ることが出来、ピストン２２の往復動のストロークを必
要に応して自由に大きく或いは小さく設計することが出
来、復動作動室２６はピストン２２の往復動ストローク
に必要なだけの小型に形成できるため、油圧ポンプＨＰ
自体の小型化を図ることが出来る。In this way, the hydraulic pump HP of this embodiment is configured to drive the piston 22 backward by pressurized air, so it is possible to omit the return spring for driving the piston 22 backward. It is possible to increase the output of the reciprocating actuator AC by speeding up the reciprocating motion cycle, and the reciprocating stroke of the piston 22 can be freely designed to be large or small as required, and the reciprocating motion chamber 26 is The hydraulic pump HP can be made small enough to accommodate the reciprocating stroke of the piston 22.
The device itself can be made smaller.
次に、前記実施例の変形例について、第３図〜第６図に
基いて説明する。尚、前記実施例と同一の機構には同一
符号を付してその説明を省略する。Next, modifications of the above embodiment will be explained based on FIGS. 3 to 6. Incidentally, mechanisms that are the same as those in the previous embodiment are given the same reference numerals and their explanations will be omitted.
く変形例１〉
前記実施例の制御弁機構６０の０リング６７に代えて、
第３図に図示のような制御弁機構６０Ａを用いる。Modification Example 1> In place of the O-ring 67 of the control valve mechanism 60 of the above embodiment,
A control valve mechanism 60A as shown in FIG. 3 is used.
切換弁体３５Ａには筒部工００が設けられ、筒部１００
には弁孔ｌＯ１を開閉する第２弁部材１０２が装着され
、マフラ４には圧縮コイルバネからなる閉弁バネ１０３
が取付けられ、第２弁部材１０２は閉弁バネ１０３によ
り下方に弾性付勢され、第２弁部材１０２の下方にあっ
て、ピストン２２の中心部に固着されたロッド状の弁部
材６１Ａは、前記実施例の弁部材６１の小径部６４の下
端よりも上方の部分を取り除いたものである。The switching valve body 35A is provided with a cylindrical part 00, and a cylindrical part 100.
A second valve member 102 for opening and closing the valve hole lO1 is attached to the muffler 4, and a valve closing spring 103 made of a compression coil spring is attached to the muffler 4.
is attached, the second valve member 102 is elastically biased downward by the valve closing spring 103, and the rod-shaped valve member 61A, which is located below the second valve member 102 and is fixed to the center of the piston 22, The valve member 61 of the previous embodiment has a portion above the lower end of the small diameter portion 64 removed.
尚、制御弁機構６０Ａのその他の部分は前記実施例と同
様なので説明を省略する。Note that the other parts of the control valve mechanism 60A are the same as those in the previous embodiment, so a description thereof will be omitted.
上記制御弁機構６０Ａにおいて、ピストン２２が図示の
ように後退限位置にあるときは、弁部材６１Ａが閉弁バ
ネ１０３のバネ力に抗して第２弁部材１０２を突上げ弁
孔１０１を開孔するので、弁作動室５０は環状隙間６９
と弁孔１０１と筒部１００の通路を介して排気室５に接
続されるので、切換弁体３５Ａは供給位置に保持され、
またピストン２２が進出限位置にあるときには、第２弁
部材１０２は閉弁バネ１０３により下降して弁孔工ＯＸ
を閉じるとともに弁部材６１Ａの上端部がＯリング６６
の下方まで下降するので、加圧エア通路６８が弁作動室
５０に連通され、弁作動室５０に加圧エアが充填されて
、切換弁体３５Ａは排出位置に切換えられる。その他の
作動は前記実施例と同様なので説明を省略する。In the control valve mechanism 60A, when the piston 22 is at the retraction limit position as shown, the valve member 61A pushes up the second valve member 102 against the spring force of the valve closing spring 103 to open the valve hole 101. Since the hole is formed, the valve operating chamber 50 has an annular gap 69.
Since the switching valve body 35A is connected to the exhaust chamber 5 through the valve hole 101 and the passage of the cylindrical portion 100, the switching valve body 35A is held at the supply position.
Further, when the piston 22 is at the advanced limit position, the second valve member 102 is lowered by the valve closing spring 103 to open the valve hole OX.
When the upper end of the valve member 61A is closed, the O-ring 66
, the pressurized air passage 68 is communicated with the valve operating chamber 50, the valve operating chamber 50 is filled with pressurized air, and the switching valve body 35A is switched to the discharge position. Other operations are the same as those in the previous embodiment, so explanations will be omitted.
く変形例２〉
前記実施例の切換弁体３５の切換弁部３７に代えて、第
４図に図示のように切換弁機構３０Ａにおいて環状のシ
ール部材１１０を有する切換弁部３７Ｂを切換弁体３５
Ｂに設ける。第４図に図示のように切換弁体３５Ｂが供
給位置にあるときは、シール部材１１０が第２弁座４６
Ｂの内周面に当接し、往動作動室２５は通路４２ａ、環
状通路４２、環状隙間１１１、受圧室４８、通路４７及
び加圧エア供給路３３により加圧エア供給口３に連通さ
れる。Modification 2〉 Instead of the switching valve part 37 of the switching valve body 35 of the above embodiment, a switching valve part 37B having an annular sealing member 110 is used as the switching valve body in the switching valve mechanism 30A as shown in FIG. 35
Provided at B. When the switching valve body 35B is in the supply position as shown in FIG.
The forward motion chamber 25 is in communication with the pressurized air supply port 3 through the passage 42a, the annular passage 42, the annular gap 111, the pressure receiving chamber 48, the passage 47, and the pressurized air supply path 33. .
一方、切換弁体３５Ｂが排出位置に切換えられると、シ
ール部材１１０が第１弁座４４Ｂの内周面に当接すると
ともに、環状隙間１１１は環状排気路４１に連通した状
態になり、往動作動室２５は通路４２ａ１環状通路４２
、環状隙間１１１、環状排気路４１及び排気路４０によ
り排気室５に連通される。その他の作動は前記実施例と
同様なのでその説明を省略する。On the other hand, when the switching valve body 35B is switched to the discharge position, the sealing member 110 comes into contact with the inner peripheral surface of the first valve seat 44B, and the annular gap 111 becomes in communication with the annular exhaust passage 41, and the forward movement The chamber 25 has a passage 42a1 and an annular passage 42.
, an annular gap 111, an annular exhaust path 41, and an exhaust path 40 communicate with the exhaust chamber 5. The other operations are the same as those in the previous embodiment, so the explanation thereof will be omitted.
く変形例３〉
前記実施例のＩＪ ＩＪ−フ弁機横８０と供給弁機構８
１を省略し、それらに代えてリリーフ弁機構８００と供
給弁機構８１０を下部ハウジング１３のコーナ部１３ａ
・１３ｂに設ける。Modification Example 3> IJ IJ-F valve machine side 80 and supply valve mechanism 8 of the above embodiment
1 is omitted, and the relief valve mechanism 800 and the supply valve mechanism 810 are installed in the corner portion 13a of the lower housing 13 instead.
- Provided in 13b.
リリーフ弁機構８００について説明すると、第５図に図
示のようにコーナ部１３ａの下端面からリリーフ弁室１
２１が凹設され、復動作動室２６の底部からはリリーフ
弁室１２１に連通ずる排気孔１２２が形成され、コーナ
部１３ａの上部にはボルト孔と共通の環状通路９５をリ
リーフ弁室１２１に連通ずる排気通路１２３が形成され
、上部ハウジング１１には環状通路９５と排気室５とを
連通ずる排気通路１２４が形成されている。To explain the relief valve mechanism 800, as shown in FIG. 5, the relief valve chamber 1 is
21 is recessed, an exhaust hole 122 communicating with the relief valve chamber 121 is formed from the bottom of the double action chamber 26, and an annular passage 95 common to the bolt hole is formed in the upper part of the corner portion 13a to the relief valve chamber 121. An exhaust passage 123 is formed in communication with the exhaust passage 123 , and an exhaust passage 124 is formed in the upper housing 11 so as to communicate the annular passage 95 with the exhaust chamber 5 .
リリーフ弁室１２１の下部にはネジ部材１２５が下部ハ
ウジング１３に螺着して設けられ、ネジ部材１２５には
アジャスト・スクリュ１２６が螺合され、アジャスト・
スクリュ１２６のリリーフ弁室１２１内に位置する上部
には凹部１２７が形成され、アジャスト・スクリュ１２
６の下端部には溝１２８が形成されている。上記凹部１
２７には、第１設定圧を設定する為の圧縮コイルバネか
らなる第１スプリング１２９が設けられ、第１スプリン
グ１２９の上部には排気孔１２２を内方より開閉する弁
子１３０が設けられ、弁子１３０は第１スプリング１２
９により上方に弾性付勢されている。A screw member 125 is provided in the lower part of the relief valve chamber 121 by being screwed onto the lower housing 13, and an adjustment screw 126 is screwed into the screw member 125 to adjust the adjustment screw.
A recess 127 is formed in the upper part of the screw 126 located inside the relief valve chamber 121, and the adjustment screw 12
A groove 128 is formed in the lower end portion of 6. Said recess 1
27 is provided with a first spring 129 made of a compression coil spring for setting a first set pressure, and a valve element 130 that opens and closes the exhaust hole 122 from the inside is provided on the upper part of the first spring 129. The child 130 is the first spring 12
9 is elastically biased upward.
次に、供給弁機構８１Ｃについて説明すると、第６図に
図示のように下部ハウジング１３のコーナ部１３ａと相
隔った別のコーナ部１３ｂには、その下端面から供給弁
室１４１が凹設され、復動作動室２６の底部からは供給
弁室１４１に連通ずる供給孔１４２が形成され、コーナ
部１３ｂの上部には環状通路９５を供給弁室１４１に連
通ずる供給通路１４３が形成され、中間ハウジング１２
の上部には環状通路９５を加圧エア供給路３３に連通ず
る供給通路１４４が形成されている。Next, to explain the supply valve mechanism 81C, as shown in FIG. 6, a supply valve chamber 141 is recessed from the lower end surface of another corner part 13b of the lower housing 13, which is spaced apart from the corner part 13a. A supply hole 142 that communicates with the supply valve chamber 141 is formed from the bottom of the double action chamber 26, a supply passage 143 that communicates the annular passage 95 with the supply valve chamber 141 is formed in the upper part of the corner portion 13b, and the middle Housing 12
A supply passage 144 that communicates the annular passage 95 with the pressurized air supply passage 33 is formed in the upper part of the air supply passage 144 .
供給弁室１４１の下部にはネジ部材１４５が下部ハウジ
ング１３に螺着して設けられ、ネジ部材１４５にはアジ
ャスト・スクリュ１４６が螺合し、アジャスト・スクリ
ュ１４６の供給弁室１４１内に位置する上部には凹部１
４７が形成され、アジャスト・スクリュ１４６の下端部
には溝１４８が形成されている。上記凹部１４７には第
２設定圧を設定する為の圧縮コイルバネからなる第２ス
プリング１４９が設けられ、第２スプリング１４９の上
部には供給通路１４３を開閉する弁子１５０が設けられ
、弁子１５０は第２スプリング１４９により上方に弾性
付勢されている。A screw member 145 is provided in the lower part of the supply valve chamber 141 by being screwed into the lower housing 13, and an adjustment screw 146 is screwed into the screw member 145, and the adjustment screw 146 is located in the supply valve chamber 141. Concave part 1 at the top
47 is formed, and a groove 148 is formed at the lower end of the adjustment screw 146. A second spring 149 made of a compression coil spring for setting a second set pressure is provided in the recess 147, and a valve 150 for opening and closing the supply passage 143 is provided above the second spring 149. is elastically biased upward by a second spring 149.
このように構成されたリリーフ弁機構８００・供給弁機
構８１Ｃにおいて、復動作動室２６内の加圧エアの圧力
が第１設定圧以下且つ第２設定圧以上のときには、弁子
１３０・１５０は第５図・第６図に図示の状態を保持し
、弁子１３０は排気孔１２２を封止し弁子１５０は供給
通路１４３を封止している。In the relief valve mechanism 800 and supply valve mechanism 81C configured in this way, when the pressure of the pressurized air in the double action chamber 26 is lower than the first set pressure and higher than the second set pressure, the valves 130 and 150 are The state shown in FIGS. 5 and 6 is maintained, with the valve 130 sealing the exhaust hole 122 and the valve 150 sealing the supply passage 143.
ピストン２２の進出作動時、復動作動室２６内の加圧エ
アの圧力が第１設定圧より高くなると、そのエア圧によ
り弁子１３０が下方に移動し、弁子１３０による排気孔
１２２の封止が解除されて加圧エアが排気孔１２２、排
気通路１２３、環状通路９５及び排気通路１２４により
排気室５にすリーフされるので復動作動室２６は第１設
定圧に維持される。ピストン２２の後退作動時、復動作
動室２６内の加圧エアの圧力が第２設定圧より低くなる
と、加圧エア供給路３３からのエア圧により弁子１５０
が下方に移動し、弁子１５０による供給通路１４３の封
止が解除され、復動作動室２６に加圧エアが供給される
ので、復動作動室２６の圧力は第２設定圧に維持される
。When the piston 22 moves forward, when the pressure of the pressurized air in the double action chamber 26 becomes higher than the first set pressure, the air pressure moves the valve element 130 downward, causing the valve element 130 to seal the exhaust hole 122. Since the stop is released and pressurized air is released into the exhaust chamber 5 through the exhaust hole 122, the exhaust passage 123, the annular passage 95, and the exhaust passage 124, the double action chamber 26 is maintained at the first set pressure. When the piston 22 moves backward, when the pressure of the pressurized air in the double action chamber 26 becomes lower than the second set pressure, the valve 150 is moved by the air pressure from the pressurized air supply path 33.
moves downward, the sealing of the supply passage 143 by the valve 150 is released, and pressurized air is supplied to the double action chamber 26, so the pressure in the double action chamber 26 is maintained at the second set pressure. Ru.
また、アジャスト・スクリュ１２６・１４６の夫々の溝
１２８・１４８をスクリュドライバなどの工具で操作す
ることにより第１スプリング１２９、第２スプリング１
４９のバネ力を調節することが出来、第１設定圧と第２
設定圧の設定を変えることが出来る。更に、前記実施例
のリリーフ弁機構８０・供給弁機構８１を構成する比較
的大型な部材である供給弁体８３、リリーフ弁体８４、
第１スプリング９７及び第２スプリング９８にかえて、
下部ハウジング１３を有効利用してリリーフ弁機構８０
Ｃ・供給弁機構８ＩＣをコンパクトに構成出来るので、
往復動アクチュエータＡＣ自体を小型・軽量にすること
が出来る。In addition, by operating the respective grooves 128 and 148 of the adjustment screws 126 and 146 with a tool such as a screwdriver, the first spring 129 and the second spring 1 can be adjusted.
49 spring force can be adjusted, and the first setting pressure and the second setting pressure can be adjusted.
You can change the set pressure setting. Furthermore, a supply valve body 83, a relief valve body 84, which are relatively large members constituting the relief valve mechanism 80 and supply valve mechanism 81 of the embodiment,
Instead of the first spring 97 and the second spring 98,
Relief valve mechanism 80 by effectively utilizing lower housing 13
C. Since the supply valve mechanism 8IC can be configured compactly,
The reciprocating actuator AC itself can be made smaller and lighter.
尚、本実施例において加圧エアに代えて油圧を用いても
よく、また本発明は油圧ポンプの他に、油圧増圧ポンプ
、ガス増圧ポンプなど往復駆動を利用する各種装置に適
用することが出来る。In this embodiment, hydraulic pressure may be used instead of pressurized air, and the present invention can be applied to various devices that use reciprocating drive, such as hydraulic pressure booster pumps and gas pressure booster pumps, in addition to hydraulic pumps. I can do it.
第１図〜第６図は本発明の実施例を示すもので、第１図
はピストンが後退限位置にあるときの油圧ポンプの縦断
面図、第２図はピストンが進出限位置にあるときの油圧
ポンプの縦断面図、第３図〜第６図は本実施例の変形例
を示すもので、第３図は制御弁機構の変形例を示す油圧
ポンプの部分縦断面図、第４図は切換弁部の変形例を示
す油圧ポンプの部分縦断面図、第５図はリリーフ弁機構
の変形例を示す油圧ポンプの縦断面図、第６図は供給弁
機構の変形例を示す油圧ポンプの縦断面図である。
ＡＣ・・往復動アクチュエータ、 ３・・加圧エア供給
口、 ５・・排気室、 １０・・ハウジング、 ２０・
・複動エアシリンダ、
・・ピストン、 ２３・・出力ロッド、・・往動作動
室、 ２６・・復動作動室、切換弁機構、 ３５・３５
Ｂ・・切換弁９・・スプリング、 ５０・・弁作動室、
ＯＡ・・制御弁機構、 ６１・・弁部材、ＯＣ・・リリ
ーフ弁機構、
ＩＣ・・供給弁機構。
特 許 出 願 人 相生精機株式会社第
図
８０Ｃ：リリーフ弁機構
↑
第
図
／Figures 1 to 6 show embodiments of the present invention, with Figure 1 being a longitudinal cross-sectional view of the hydraulic pump when the piston is at its retraction limit position, and Figure 2 being a longitudinal cross-sectional view of the hydraulic pump when the piston is at its extension limit position. FIGS. 3 to 6 are longitudinal cross-sectional views of the hydraulic pump, and FIGS. 3 to 6 show modifications of the present embodiment. FIG. 5 is a partial longitudinal sectional view of a hydraulic pump showing a modification of the switching valve section, FIG. 5 is a longitudinal sectional view of a hydraulic pump showing a modification of the relief valve mechanism, and FIG. 6 is a hydraulic pump showing a modification of the supply valve mechanism. FIG. AC: reciprocating actuator, 3: pressurized air supply port, 5: exhaust chamber, 10: housing, 20:
・Double acting air cylinder, ・・Piston, 23・・Output rod, ・・Forward motion chamber, 26・・Backward motion chamber, switching valve mechanism, 35・35
B...Switching valve 9...Spring, 50...Valve operating chamber,
OA...control valve mechanism, 61...valve member, OC...relief valve mechanism, IC...supply valve mechanism. Patent applicant: Aioi Seiki Co., Ltd. Figure 80C: Relief valve mechanism ↑ Figure /
Claims (1)
れた出力ロッドとを有する複動流体圧シリンダを設け、
この流体圧シリンダにピストンを流体圧で進出駆動する
往動作動室とピストンを流体圧で後退駆動する復動作動
室を設け、 上記往動作動室を流体圧供給口に接続する供給位置と排
出口に接続する排出位置とに択一的に切換えられる切換
弁体と、この切換弁体を供給位置に付勢する付勢手段と
、その付勢力に抗して切換弁体を流体圧で排出位置に切
換える弁作動室とを備えた切換弁機構を設け、 上記ピストンから延び切換弁体に挿通された弁部材を介
して、ピストンが後退限位置にあるときは弁作動室を排
出口に接続し且つピストンが後退限位置と進出限位置の
間にあるときは弁作動室を封止し且つピストンが進出限
位置にあるときは弁作動室を流体圧供給口に接続する制
御弁機構を設け、 上記ピストンの進出作動時、復動作動室内の流体圧が第
１設定圧より高いときに開弁して復動作動室を排出口に
接続するリリーフ弁機構を設け、上記ピストンの後退作
動時、復動作動室内の流体圧が第１設定圧以下の第２設
定圧未満のときに開弁して復動作動室を流体圧供給口に
接続する供給弁機構を設けたことを特徴とする流体圧駆
動連続作動型往復動アクチュエータ。(1) providing a double-acting hydraulic cylinder having a piston and an output rod fixed to the piston in a housing;
This fluid pressure cylinder is provided with a forward motion chamber that drives the piston forward using fluid pressure and a backward motion chamber that drives the piston backward using fluid pressure, and a supply position and an exhaust position that connect the forward motion chamber to the fluid pressure supply port. A switching valve body connected to an outlet and selectively switched to a discharge position, a biasing means for biasing the switching valve body to a supply position, and a fluid pressure to discharge the switching valve body against the biasing force. A switching valve mechanism is provided, which includes a valve operating chamber that is switched to the reverse position, and the valve operating chamber is connected to the discharge port when the piston is at the retraction limit position via a valve member that extends from the piston and is inserted through the switching valve body. and a control valve mechanism is provided which seals the valve operating chamber when the piston is between the retraction limit position and the extension limit position and connects the valve operation chamber to the fluid pressure supply port when the piston is at the extension limit position. , a relief valve mechanism is provided that opens when the fluid pressure in the double action chamber is higher than the first set pressure when the piston advances, and connects the double action chamber to the discharge port, and when the piston moves backward; , characterized in that a supply valve mechanism is provided that opens when the fluid pressure in the double action chamber is lower than the first set pressure and lower than the second set pressure to connect the double action chamber to the fluid pressure supply port. Fluid pressure driven continuous reciprocating actuator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1084329A JP2676110B2 (en) | 1989-04-03 | 1989-04-03 | Fluid pressure continuously operated reciprocating actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1084329A JP2676110B2 (en) | 1989-04-03 | 1989-04-03 | Fluid pressure continuously operated reciprocating actuator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02261911A true JPH02261911A (en) | 1990-10-24 |
| JP2676110B2 JP2676110B2 (en) | 1997-11-12 |
Family
ID=13827477
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1084329A Expired - Fee Related JP2676110B2 (en) | 1989-04-03 | 1989-04-03 | Fluid pressure continuously operated reciprocating actuator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2676110B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7147442B2 (en) * | 2003-05-22 | 2006-12-12 | Kuo-Chung Yeh | Automatic oil pump, with a valved pumping piston and a valved driving piston unit |
-
1989
- 1989-04-03 JP JP1084329A patent/JP2676110B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7147442B2 (en) * | 2003-05-22 | 2006-12-12 | Kuo-Chung Yeh | Automatic oil pump, with a valved pumping piston and a valved driving piston unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2676110B2 (en) | 1997-11-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| LAPS | Cancellation because of no payment of annual fees |