JPS61155678A - Fluid pumping device - Google Patents
Fluid pumping deviceInfo
- Publication number
- JPS61155678A JPS61155678A JP27582984A JP27582984A JPS61155678A JP S61155678 A JPS61155678 A JP S61155678A JP 27582984 A JP27582984 A JP 27582984A JP 27582984 A JP27582984 A JP 27582984A JP S61155678 A JPS61155678 A JP S61155678A
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- passage
- pressure
- spiral groove
- shaft member
- 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.)
- Pending
Links
Landscapes
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、作動油等の流体を圧送する装置に関する。[Detailed description of the invention] Industrial applications The present invention relates to a device for pumping fluid such as hydraulic oil.
従来の技術及び発明が解決しようとする問題点流体の圧
送装置において、流体の圧送流量を精密に制御するには
、流体を連続圧送する方式とするのが望ましく、従来、
この種の圧送装置としては、一対の駆動歯車と従動歯車
を噛み合わせてケーシング内に収納し、両歯車の回転に
より流体を夫々の歯車の外周を回って吐出するようにし
た歯車ポンプが良く知られているが、この歯車ポンプは
歯車とケーシングの間のシールが難しく、洩れが生じや
すくて流体を高圧圧送できない欠点があり、また、歯車
ポンプとは別に、雄ねじ軸に雌ねじ軸を噛み合わせてケ
ーシング内に収納し１両ねじ軸の回転により雌ねじ軸の
ねじ溝内の流体を雄ねじ軸のねじ出で押し出すようにし
たねじポンプも知られているが、一般には、同じように
ねじ軸とケーシングの間のシールが難しくて流体を高圧
圧送できない欠点があった。なお、一部に高圧圧送可能
なものもあるが、洩れを押さえるのに高精度の加工及び
組付が要求されるので高価であり、洩れを上回る高速度
、高出力で高圧力を得ようとするために、いきおいポン
プ効率が低下する欠点がある。一方、流体を高圧圧送す
るには、プランジャポンプ、ダンヤフラムポンプ等が適
するが、これらは連続圧送ではなくて断続圧送であるか
ら。Problems to be Solved by the Prior Art and the Invention In a fluid pumping device, in order to precisely control the pumping flow rate of the fluid, it is desirable to adopt a system in which the fluid is pumped continuously.
A well-known example of this type of pumping device is a gear pump, in which a pair of drive gears and a driven gear are meshed together and housed in a casing, and the rotation of both gears causes fluid to be discharged around the outer periphery of each gear. However, this gear pump has the drawback that it is difficult to seal between the gear and the casing, leaks easily occur, and the fluid cannot be pumped under high pressure. There are also known screw pumps that are housed in a casing and are configured to push out the fluid in the thread groove of the female threaded shaft by the rotation of one double threaded shaft, but in general, the threaded shaft and casing are The problem was that it was difficult to seal between the two, making it impossible to pump fluid under high pressure. There are some products that can be pumped under high pressure, but they are expensive because they require high-precision machining and assembly to prevent leakage. Therefore, there is a drawback that the pump efficiency decreases. On the other hand, plunger pumps, dungeon pumps, etc. are suitable for high-pressure pumping of fluid, but these pumps do not perform continuous pumping but intermittent pumping.
脈動が大きく圧送流量の精密な制御ができなかった。The pulsation was large and the pumping flow rate could not be precisely controlled.
本発明は、叙上の点に鑑み完成されたものであって、圧
送流量の精密な制御ができるように連続圧送方式を採り
、しかも、高圧圧送を可能とした流体圧送装置を提供す
ることを目的とする。The present invention has been completed in view of the above points, and an object of the present invention is to provide a fluid pumping device that adopts a continuous pumping method so that the pumping flow rate can be precisely controlled, and that also enables high-pressure pumping. purpose.
実施例
以下１本発明の一実施例を第１図及び第２図にに基づい
て説明する。Embodiment One embodiment of the present invention will be described below with reference to FIGS. 1 and 2.
図において、ギャードモータを内蔵したボックス１の下
面には、中心孔３を有するシリンダ２が固定され、その
下端の取付孔４に流体の吸入口６を形成したキャップ５
が螺着されているとともに。In the figure, a cylinder 2 having a center hole 3 is fixed to the lower surface of a box 1 containing a guarded motor, and a cap 5 having a fluid inlet 6 formed in a mounting hole 4 at the lower end thereof is fixed.
is screwed on.
シリンダ２の上方部分の周壁に流体の吐出ロアが透設さ
れてこの吐出ロアにニップル８が螺着されており、この
シリンダ２の中心孔３内には、上端をギャードモータの
出力軸１０に連結した回転軸１１が、緊密にかつベアリ
ング１２．１３を介して軸心周りの回転自由に支持され
ている。A fluid discharge lower is transparently provided in the circumferential wall of the upper part of the cylinder 2, and a nipple 8 is screwed to this discharge lower. A rotary shaft 11 is supported tightly and freely rotatably about its axis via bearings 12.13.
この回転軸１１の外周面には、前記の吐出ロアと対応す
る部分に円周溝１５が形成され、そこから下端にわたっ
て、断面形状が半円形を成す１条の螺旋溝１６が連成さ
れているとともに、この回転軸１１の螺旋溝１６を形成
した部分の中心には、螺旋溝１６と同一半径の断面円形
を成す球体の戻り通路１８が形成され、その上端部が斜
め上方に傾斜して螺旋溝１６の上端部から略半周分下が
った位置に開口し、下端部が斜め下方に傾斜して螺旋溝
１６の下端部から略−周分上がった位置に開口しており
、また、シリンダ２の内周面には、螺旋溝１６の上記の
戻り通路１８の上端部が開口する位置から回転軸１１の
下端よりも僅かに下方の位置まで、螺旋溝１６と同一半
径の半円形を成す１本の直線溝２０が軸方向に沿って形
成され、特にこの直線溝２０のうちの、螺旋溝１６の戻
り通路１８の下端部が開口する部分と整合する位置２１
ａから上端である螺旋溝１６の戻り通路１８の上端部が
開口する部分と整合する位置２１ｂまでの領域において
流体の圧送通路２１が構成されており、この圧送通路２
１と螺旋溝１６の交差点の空間に、圧送通路２１．螺旋
溝１６及び戻り通路１８と同一半径の球体２３が夫々緊
密に嵌合されているとともに、戻り通路１８内に同じ球
体２３が一連に連なって挿入されている。A circumferential groove 15 is formed on the outer circumferential surface of the rotating shaft 11 in a portion corresponding to the discharge lower, and a single spiral groove 16 having a semicircular cross section is connected from there to the lower end. At the same time, a spherical return passage 18 having a circular cross section and the same radius as the spiral groove 16 is formed at the center of the part of the rotating shaft 11 where the spiral groove 16 is formed, and the upper end thereof is inclined diagonally upward. The spiral groove 16 opens at a position approximately half a turn downward from the upper end thereof, and its lower end slopes diagonally downward to open at a position approximately half a turn upward from the lower end of the spiral groove 16. On the inner circumferential surface of the spiral groove 16, a semicircular groove 1 having the same radius as the spiral groove 16 is formed from the position where the upper end of the return passage 18 of the spiral groove 16 opens to a position slightly below the lower end of the rotating shaft 11. A straight groove 20 of the book is formed along the axial direction, and in particular, a position 21 of the straight groove 20 that aligns with the portion where the lower end of the return passage 18 of the spiral groove 16 opens.
A fluid pressure-feeding passage 21 is configured in a region from a to a position 21b that aligns with the upper end of the return passage 18 of the spiral groove 16, and this pressure-feeding passage 2
1 and the spiral groove 16, there is a pressure feeding passage 21. Spheres 23 having the same radius as the spiral groove 16 and the return passage 18 are tightly fitted, respectively, and the same spheres 23 are inserted into the return passage 18 in series.
前記したシリンダ２の下端に螺着したキャップ５には吸
入管２５の一端が接続され、その他端が逆止弁２６を介
して油圧モータ等のアクチュエータ２７の作動油排出口
に接続されているとともに。One end of a suction pipe 25 is connected to the cap 5 screwed onto the lower end of the cylinder 2, and the other end is connected to a hydraulic oil outlet of an actuator 27 such as a hydraulic motor through a check valve 26. .
ニップル８に一端を接続した吐出管２８の他端が。The other end of the discharge pipe 28 has one end connected to the nipple 8.
逆止弁２９を介して前記のアクチュエータ２７の作動油
供給口に接続されており、また、この吐出管２８の途中
には、吐出管２８内を圧送される流体の圧力を検知して
、圧力が一定値以上に上がると回転軸１１の駆動用のモ
ータを停止し、一定値以下に下がるとモータを起動させ
る圧力スイッチ３０が介設されている。It is connected to the hydraulic oil supply port of the actuator 27 through a check valve 29, and a section in the middle of the discharge pipe 28 detects the pressure of the fluid being pumped through the discharge pipe 28, and A pressure switch 30 is provided that stops the motor for driving the rotary shaft 11 when the pressure rises above a certain value, and starts the motor when the pressure falls below a certain value.
また１回転軸１１の前記円周溝１５の上方には。Further, above the circumferential groove 15 of the one-rotation shaft 11.
シリンダ２の内周面と回転軸１１の外周面の間から洩れ
た作動油を溜める溜溝３１が周設され、その溜まった作
動油を排出管３２から外部へ排出するようになっており
、また、シリンダ２の上端面に形成された拡径孔３３の
下端の内周面と回転軸１１の外周面の間には、作動油の
洩れ止め用のパツキン３４が、ねじ３５のねじ込みによ
り皿ばね３６を介して圧縮されて緊密に嵌着されている
。A reservoir groove 31 is provided around the circumference to collect hydraulic oil leaking from between the inner circumferential surface of the cylinder 2 and the outer circumferential surface of the rotating shaft 11, and the accumulated hydraulic oil is discharged to the outside from a discharge pipe 32. Further, between the inner circumferential surface of the lower end of the enlarged diameter hole 33 formed in the upper end surface of the cylinder 2 and the outer circumferential surface of the rotating shaft 11, a packing 34 for preventing leakage of hydraulic oil is fitted with a countersunk screw 35. It is compressed and tightly fitted via a spring 36.
次に、本実施例の作用について説明する。Next, the operation of this embodiment will be explained.
ギャードモータの駆動により回転軸１１が矢線Ａ方向に
回転すると、螺旋溝１６に嵌合した球体２３が圧送通路
２１に沿って上方に移動し、球体２３が圧送通路２１の
終端部２１ｂに達すると。When the rotating shaft 11 rotates in the direction of the arrow A due to the drive of the geared motor, the sphere 23 fitted in the spiral groove 16 moves upward along the pressure-feeding passage 21, and when the sphere 23 reaches the terminal end 21b of the pressure-feeding passage 21, .
それ以上の上方への移動が阻止されることから、その終
端部２１ｂに整合した戻り通路１８の入口である上端部
から一連の球体２３を押して戻り通路１８内に入り込み
、これによって、戻り通路１８内の一連の球体２３の最
下方の球体２３が、圧送通路２１の始端部２１ａに整合
した戻り通路１８の出口である下端部から押し出されて
螺旋溝１６に嵌合し、これを繰り返すことによって、球
体２３が圧送通路２１に沿って上方に移動し、戻り通路
１８に沿って下方に移動する循環走行が行なわれるので
あり、この球体２３の循環走行に伴い、圧送通路２１の
始端部２１ａで螺旋１６に嵌合した球体２３が上方に移
動することにより、圧送通路２１のその球体２３の下側
の部分が負圧となって、アクチュエータ２７の作動油が
、吸入管２５を通り吸入口６から直線溝２０の下端部及
び螺旋溝１６の下端部を通って、その球体２３の下側の
圧送通路２１内に導入され、その作動油が次に圧送通路
２１の始端部２１ａに嵌合した球体２３の間で挟まれて
圧送通路２１内を上方に移送され、先の球体２３が圧送
通路２１の終端部２１ｂに達して戻り通路１８内に入り
込むと、その球体２３の下側の圧送通路２１内の作動油
が、後の球体２３で押されて加圧されて螺旋溝１６の上
端部を通り円周溝１５を介して吐出ロアから吐出され、
吐出管２８を通ってアクチュエータ２７に供給され、こ
の繰り返しにより、作動油がアクチュエータ２７を通っ
てＷＩｇＡされるのである。Since further upward movement is prevented, the series of spheres 23 is pushed into the return passage 18 from its upper end, which is the entrance of the return passage 18 aligned with its terminal end 21b, thereby causing the return passage 18 The lowermost sphere 23 of the series of spheres 23 in the series is pushed out from the lower end, which is the outlet of the return passage 18 aligned with the starting end 21a of the pumping passage 21, and fitted into the spiral groove 16, and by repeating this process. , the sphere 23 moves upward along the pressure-feeding passage 21 and moves downward along the return passage 18, thereby performing a circular movement. As the sphere 23 fitted into the spiral 16 moves upward, the lower part of the sphere 23 in the pressure feeding passage 21 becomes negative pressure, and the hydraulic oil of the actuator 27 passes through the suction pipe 25 and enters the suction port 6. The hydraulic oil is introduced into the pressure passage 21 below the sphere 23 through the lower end of the straight groove 20 and the lower end of the spiral groove 16, and the hydraulic oil is then fitted into the starting end 21a of the pressure passage 21. When the sphere 23 is sandwiched between the spheres 23 and transferred upward in the pressure-feeding passage 21 and reaches the terminal end 21b of the pressure-feeding passage 21 and enters the return passage 18, the pressure-feeding passage below the sphere 23 The hydraulic oil in 21 is pushed and pressurized by the rear sphere 23, passes through the upper end of the spiral groove 16, and is discharged from the discharge lower via the circumferential groove 15.
The hydraulic fluid is supplied to the actuator 27 through the discharge pipe 28, and by repeating this process, the hydraulic fluid passes through the actuator 27 and is WIgA.
上記実施例において１球体２３を挟む上下の圧送通路２
１は螺旋溝１６を介して僅かに連通することになるが１
球体２３が圧送通路２１に接触する構造となっていて接
触部分の摩擦抵抗が小さく。In the above embodiment, the upper and lower pressure feeding passages 2 sandwiching one sphere 23
1 will communicate slightly through the spiral groove 16, but 1
The structure is such that the sphere 23 contacts the pressure feeding passage 21, and the frictional resistance at the contact portion is small.
回転軸１１を高速回転させて球体２３を高速度で移動さ
せることが可能であるため１作動油の逆流が最小限に抑
えられて、作動油を吐出ロアから連続的に吐出すること
ができる。Since the rotating shaft 11 can be rotated at high speed and the sphere 23 can be moved at high speed, backflow of the hydraulic oil can be minimized and the hydraulic oil can be continuously discharged from the discharge lower.
なお、上記実施例において、戻り通路１８の下端の螺旋
溝１６に開口する位置より下方の螺旋溝１６と直線溝２
０のいずれか一方を塞ぐと１回転軸１１を逆転しても球
体２３がその位置より下方へ移動するのが阻止され、圧
送通路２１及び戻り通路１８内を上記と逆方向へ循環走
行するのであって、この場合には回転軸１１の逆転によ
り、吐出ロアから作動油を吸い込み、吸入口６から吐出
することも可能な可逆ポンプとなる。In the above embodiment, the spiral groove 16 and the straight groove 2 below the position opening into the spiral groove 16 at the lower end of the return passage 18
If either one of 0 is blocked, the sphere 23 is prevented from moving downward from that position even if the rotation axis 11 is reversed, and the sphere 23 circulates in the pressure passage 21 and the return passage 18 in the opposite direction to the above. In this case, by reversing the rotating shaft 11, the pump becomes a reversible pump that can suck in hydraulic oil from the discharge lower and discharge it from the suction port 6.
発明の構成及び作用効果 上記実施例によって具体的に説明したように。Structure and effects of the invention As specifically explained by the above embodiments.
本発明の流体圧送装置は、外周面に断面形状が円の一部
を成す螺旋溝を形成した回転軸を、シリンダ内に緊密に
かつ軸心周りの回転自由に嵌装し。In the fluid pumping device of the present invention, a rotating shaft having a spiral groove whose cross section forms part of a circle formed on the outer circumferential surface is tightly fitted into a cylinder and freely rotatable about the axis.
該シリンダの内周面に断面形状が前記円の残部を成す圧
送通路を軸方向に形成して、該圧送通路と前記螺旋溝の
交差点に夫々球体を緊密に嵌合するとともに、前記回転
軸の内部に、前記球体が一列に連なって走行する球体の
戻り通路を前記圧送通路の始端と終端に連通ずるように
形成し、前記圧送通路の始端を前記シリンダの流体吸入
口に、終端を該シリンダの流体吐出口に夫々連通し、前
記回転軸の回転により前記螺旋溝に嵌合した前記球体を
前記圧送通路に沿って一方向に循環走行させることによ
って、前記流体吸入口から前記圧送通路の始端に導いた
流体を前記球体で押圧しつつ移送し、該圧送通路の終端
に到った流体を前記流体吐出口から吐出する構成とじた
ことをを棗旨とするものであって、回転軸の回転により
球体が圧送通路に沿って一方向に循環走行することによ
って。A pressure-feeding passage whose cross-sectional shape forms the remainder of the circle is formed in the axial direction on the inner circumferential surface of the cylinder, and spheres are tightly fitted into the intersections of the pressure-feeding passage and the spiral groove, respectively, and A return passage for the spheres, in which the spheres run in a row, is formed inside so as to communicate with the starting end and the terminal end of the pressure feeding passage, and the starting end of the pressure feeding passage is connected to the fluid suction port of the cylinder, and the terminal end thereof is connected to the cylinder. The spheres, which are connected to the fluid discharge ports of each of the fluid suction ports and are fitted into the spiral grooves by rotation of the rotating shaft, are circulated in one direction along the pressure feeding passage, thereby moving the starting end of the pressure feeding passage from the fluid suction port to the starting end of the pressure feeding passage. The purpose of this system is to transfer the fluid guided by the sphere while being pressed by the sphere, and discharge the fluid that has reached the end of the pressure passage from the fluid discharge port, and the rotating shaft is The rotation causes the sphere to circulate in one direction along the pumping path.
圧送通路内に導入された流体が球体で順次に押圧されて
連続的に圧送され、しかも、球体が圧送通路と螺旋溝の
交差点に緊密に嵌合しているから。This is because the fluid introduced into the pressure passage is sequentially pressed by the spheres and is continuously pumped, and moreover, the spheres fit tightly into the intersections of the pressure passage and the spiral groove.
球体を挟む前後の圧送通路は極く僅かしか連通せず、流
体の洩れが極力押えられて流体の高圧圧送が可能となり
、また、球体は圧送通路に沿って移動する際に転がって
移動することができるから、摩擦抵抗が小さく、運転音
を小さく抑えることができるとともに、接触部分の摩耗
が低減できて耐久性を向上させることができ、さらに１
４球体の戻り通路を回転軸の内部に形成したことによっ
て、装置を小嵩にまとめることができる効果を奏する。There is very little communication between the pressure passages before and after the sphere, which minimizes fluid leakage and enables high-pressure pumping of fluid.Also, the sphere does not roll when moving along the pressure passage. As a result, frictional resistance is low, operating noise can be kept low, and wear on the contact parts can be reduced, improving durability.
By forming the four-sphere return passage inside the rotating shaft, there is an effect that the device can be assembled into a small volume.
第１図は本発明装置の一実施例の断面図及びブロック図
、第２図は第１図のＸＸ線断面図である。
２ニジリンダ ６：吸入口 ７：吐出口 １１：回転軸
１６：螺旋溝 １８：戻り通路 ２１：圧送通路 ２
１ａ： （圧送通路２１の）始端部 ２１ｂ： （
圧送通路２１の）終端部 ２３：球体FIG. 1 is a sectional view and block diagram of an embodiment of the apparatus of the present invention, and FIG. 2 is a sectional view taken along the line XX of FIG. 1. 2 Niji cylinder 6: Suction port 7: Discharge port 11: Rotating shaft 16: Spiral groove 18: Return passage 21: Pressure feeding passage 2
1a: Starting end (of pressure feeding passage 21) 21b: (
23: Sphere
Claims (1)
転軸を、シリンダ内に緊密にかつ軸心周りの回転自由に
嵌装し、該シリンダの内周面に断面形状が前記円の残部
を成す圧送通路を軸方向に形成して、該圧送通路と前記
螺旋溝の交差点に夫々球体を緊密に嵌合するとともに、
前記回転軸の内部に、前記球体が一列に連なって走行す
る球体の戻り通路を前記圧送通路の始端と終端に連通す
るように形成し、前記圧送通路の始端を前記シリンダの
流体吸入口に、終端を該シリンダの流体吐出口に夫々連
通し、前記回転軸の回転により前記螺旋溝に嵌合した前
記球体を前記圧送通路に沿って一方向に循環走行させる
ことによって、前記流体吸入口から前記圧送通路の始端
に導いた流体を前記球体で押圧しつつ移送し、該圧送通
路の終端に到った流体を前記流体吐出口から吐出する構
成としたことを特徴とする流体圧送装置A rotating shaft having a spiral groove whose cross-sectional shape forms part of a circle on its outer circumferential surface is fitted tightly into a cylinder and freely rotates around the axis, and the inner circumferential surface of the cylinder has a spiral groove whose cross-sectional shape forms a part of a circle. forming a pressure passage forming the remainder in the axial direction, and tightly fitting spheres at the intersections of the pressure passage and the spiral groove, respectively;
A return passage for the spheres, in which the spheres run in a row, is formed inside the rotating shaft so as to communicate with the starting end and the terminal end of the pressure passage, and the starting end of the pressure passage is connected to the fluid suction port of the cylinder; The terminal ends of the cylinders are connected to the fluid discharge ports of the cylinders, and the spheres fitted in the spiral grooves are caused to circulate in one direction along the pressure feeding passage by rotation of the rotary shaft, thereby causing the fluid to flow from the fluid suction ports to the fluid suction ports. A fluid pumping device characterized in that the fluid guided to the starting end of the pumping passage is transferred while being pressed by the sphere, and the fluid that reaches the terminal end of the pumping passage is discharged from the fluid discharge port.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27582984A JPS61155678A (en) | 1984-12-27 | 1984-12-27 | Fluid pumping device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27582984A JPS61155678A (en) | 1984-12-27 | 1984-12-27 | Fluid pumping device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61155678A true JPS61155678A (en) | 1986-07-15 |
Family
ID=17561004
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27582984A Pending JPS61155678A (en) | 1984-12-27 | 1984-12-27 | Fluid pumping device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61155678A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63198489U (en) * | 1987-06-12 | 1988-12-21 | ||
| CN105065255A (en) * | 2015-09-11 | 2015-11-18 | 魏江坤 | Screw ball pump |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4939006B1 (en) * | 1971-04-24 | 1974-10-22 |
-
1984
- 1984-12-27 JP JP27582984A patent/JPS61155678A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4939006B1 (en) * | 1971-04-24 | 1974-10-22 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63198489U (en) * | 1987-06-12 | 1988-12-21 | ||
| CN105065255A (en) * | 2015-09-11 | 2015-11-18 | 魏江坤 | Screw ball pump |
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