JPH0320550Y2 - - Google Patents
Info
- Publication number
- JPH0320550Y2 JPH0320550Y2 JP1985009244U JP924485U JPH0320550Y2 JP H0320550 Y2 JPH0320550 Y2 JP H0320550Y2 JP 1985009244 U JP1985009244 U JP 1985009244U JP 924485 U JP924485 U JP 924485U JP H0320550 Y2 JPH0320550 Y2 JP H0320550Y2
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- large diameter
- small diameter
- cylinder
- small
- 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.)
- Expired
Links
- 238000012856 packing Methods 0.000 claims description 23
- 230000001105 regulatory effect Effects 0.000 claims description 15
- 238000005086 pumping Methods 0.000 claims description 2
- 239000012530 fluid Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Reciprocating Pumps (AREA)
Description
【考案の詳細な説明】
［産業上の利用分野］
この考案は往復ポンプに関し、ピストン手段を
大径部及び小径部の二段に構成し、それぞれポン
プ室の吐出側に設定圧調整可能な調圧弁を設ける
ことにより、高圧時小径部ピストンに摺接して高
圧ポンプ室と低圧ポンプ室とを画設するシールの
背圧を調整するとともに、低圧大吐出量及び高圧
小吐出量の二様の用途に利用することができると
ころの往復ポンプに関するものである。[Detailed description of the invention] [Industrial field of application] This invention relates to a reciprocating pump, and the piston means is configured in two stages, a large diameter part and a small diameter part, each having an adjustable set pressure on the discharge side of the pump chamber. By providing a pressure valve, the back pressure of the seal that slides against the small diameter piston at high pressure and separates the high pressure pump chamber and the low pressure pump chamber can be adjusted, and it can also be used for two types of low pressure large discharge volume and high pressure small discharge volume. This relates to a reciprocating pump that can be used for.
［従来の技術］
従来の往復ポンプは、例えば特願昭59−2453号
に係わる発明（第２図示）のように、クランクケ
ース１にクランク６を介して軸支される連接棒７
に一種類の吐出圧力及び吐出量を発生しうるピス
トン手段であるプランジヤ４がピン連結され、プ
ランジヤ４はクランクケース１に装着されるシリ
ンダ５内に水気密状態に往復動可能に摺設され
る。[Prior Art] A conventional reciprocating pump has a connecting rod 7 that is pivotally supported by a crank case 1 via a crank 6, as in the invention related to Japanese Patent Application No. 59-2453 (shown in the second figure).
A plunger 4, which is a piston means capable of generating one type of discharge pressure and discharge amount, is connected with a pin, and the plunger 4 is slidably reciprocated in a watertight state within a cylinder 5 attached to the crankcase 1. .
また、高圧室と低圧室とを画設するシール２は
高圧室側から低圧室側へ向つて圧力を受けるた
め、該シール支持端３により、シールを低圧側か
ら支持する必要が生じ、高、低圧力両者の差が大
となる程、シールの低圧側背面を十分に支持する
ことになり、そのためシール支持端とシールを摺
動するプランジヤとの間隙が小とならざるを得
ず、組立時の公差及び製造過程での精度を厳しく
管理せざるを得ないという不都合があつた。 Further, since the seal 2 that separates the high pressure chamber and the low pressure chamber receives pressure from the high pressure chamber side toward the low pressure chamber side, it is necessary to support the seal from the low pressure side using the seal support end 3. The larger the difference between the low and low pressures, the more sufficient support is required for the low pressure side back of the seal, which forces the gap between the seal support end and the plunger that slides on the seal to become smaller, making it difficult to assemble the seal. There was an inconvenience in that the tolerances and precision in the manufacturing process had to be strictly controlled.
また従来の往復ポンプでは、限定された仕様範
囲、例えば圧力の上限が決められていて、その範
囲内において、所要動力と流速限界の許容できる
範囲で吸水量を決定して使用している。したがつ
てこの範囲を大巾に越えるときは二台のポンプを
独立して使用するか、あるいはクラツチ等によつ
て並列に接続して使用しなければならなかつた。 Furthermore, in conventional reciprocating pumps, a limited specification range, for example, an upper limit of pressure, is determined, and within that range, the amount of water absorbed is determined and used within an allowable range of required power and flow rate limit. Therefore, when exceeding this range, two pumps had to be used independently or connected in parallel using a clutch or the like.
［考案が解決しようとする課題］
しかし前記従来の往復ポンプにおいては、ポン
プを二台必要とし、設置場所も大きくとる必要が
あると共に、配管も複雑となり、また経費もかか
る等の問題がある。[Problems to be Solved by the Invention] However, the conventional reciprocating pump requires two pumps, requires a large installation space, has complicated piping, and is expensive.
［課題を解決するための手段］
この考案は以上に述べた事情に鑑みなされたも
ので、シリンダ体内に往復摺動可能のピストン手
段を備えてなる往復ポンプであつて、前記シリン
ダ体に互いに連通可能のシリンダ大径部とシリン
ダ小径部とを備え、これらシリンダ大径部及びシ
リンダ小径部には、前記ピストン手段を構成する
ピストン大径部とピストン小径部とをそれぞれ大
径パツキング手段及び小径パツキング手段を介し
て水気密状態で摺設させ、前記シリンダ大径部に
前記大径パツキング手段によつて互いに分離され
る大径部室及び吸入口を備える吸入室を形成し、
これら大径室及び吸入室を吸入弁を介して互いに
連通させ、この大径部室を吐出弁及び設定圧調整
可能の調圧弁を介して余水口に連通させ、前記ピ
ストン小径部に前記小径パツキング手段を介して
前記大径部室と分離される小径部室を画設し、こ
の小径部室を吸入弁を介して前記大径部室に連通
させるとともに吐出弁を介して吐出口に連通さ
せ、かつ吐出弁及び設定圧調整可能の調圧弁を介
して余水口に連通させ、もつて前記両調圧弁に対
する適宜の圧力設定により、高圧時前記小径パツ
キング手段の保持を容易にするとともに、低圧大
吐出量から高圧小吐出量のポンプ作用を可能とし
てなる往復ポンプを提案するものである。[Means for Solving the Problems] This invention was devised in view of the above-mentioned circumstances, and is a reciprocating pump comprising a piston means capable of reciprocating sliding within a cylinder body, the piston means communicating with the cylinder body mutually. The cylinder large diameter part and the cylinder small diameter part are provided with a large diameter packing means and a small diameter packing means respectively. forming a suction chamber in the large-diameter portion of the cylinder, the suction chamber having a large-diameter chamber and a suction port separated from each other by the large-diameter packing means;
The large-diameter chamber and the suction chamber are communicated with each other via a suction valve, and the large-diameter chamber is communicated with a spillway via a discharge valve and a pressure regulating valve capable of adjusting the set pressure, and the small-diameter packing means is connected to the small-diameter portion of the piston. A small-diameter chamber is separated from the large-diameter chamber through a suction valve, and the small-diameter chamber is communicated with the large-diameter chamber via a suction valve and a discharge port via a discharge valve. It communicates with the spillway through a pressure regulating valve whose set pressure can be adjusted, and by setting appropriate pressures for both pressure regulating valves, it is possible to easily hold the small diameter packing means at high pressure, and to adjust the pressure from low pressure large discharge amount to high pressure small This paper proposes a reciprocating pump that is capable of pumping the discharge amount.
［作用］
上述の構成から考案の往復ポンプによれば、一
台の往復ポンプによつて低圧大容量から高圧小容
量まで巾広い使用態様をうることができるもので
ある。[Function] According to the reciprocating pump devised from the above-described structure, a single reciprocating pump can be used in a wide range of applications from low-pressure, large-capacity to high-pressure, small-capacity.
［実施例］
以下添付図面に基づいてこの考案の一実施例を
説明する。[Example] An example of this invention will be described below based on the accompanying drawings.
第１図はこの考案による往復ポンプを示す要部
断面図で、図面中１１は下方に脚体が備えられて
床等に設置可能なクランクケースで、クランクケ
ース１１にはクランクを介して連接棒１２に軸支
される。 Figure 1 is a cross-sectional view of the main parts of a reciprocating pump according to this invention. In the drawing, reference numeral 11 is a crankcase that is provided with legs at the bottom and can be installed on the floor. The crankcase 11 is connected to a connecting rod via the crank. 12.
前記クランクケース１１の先端部には、基端部
にシリンダ大径部１３及び先端部にシリンダ小径
部１４が一体的に形成されるシリンダ１５が固着
される。 A cylinder 15 is fixed to the distal end of the crankcase 11, and is integrally formed with a cylinder large diameter section 13 at the base end and a cylinder small diameter section 14 at the distal end.
前記連接棒１２の先端部には、シリンダ大径部
１６とその先端部に一体的に形成されるピストン
小径部１７とを備えてなるプランジヤ形のピスト
ン手段１８の基端部がピン１９によつてピン連結
される。ピストン手段１８のピストン大径部１６
はピストン小径部１７より外径が大とされ、かつ
ピストン大径部１６は前記シリンダ大径部１３内
に、また前記ピストン小径部１７は前記シリンダ
小径部１４内にそれぞれ大径及び小径パツキング
手段である大径及び小径パツキング２０及び２１
を介して水気密状態で往復動可能に摺設される。 At the distal end of the connecting rod 12, a pin 19 connects the proximal end of a plunger-shaped piston means 18 comprising a cylinder large diameter section 16 and a piston small diameter section 17 integrally formed at the distal end thereof. They are connected with pins. Piston large diameter portion 16 of piston means 18
has a larger outer diameter than the piston small diameter portion 17, and the piston large diameter portion 16 is provided within the cylinder large diameter portion 13, and the piston small diameter portion 17 is provided with large diameter and small diameter packing means within the cylinder small diameter portion 14, respectively. Large diameter and small diameter packing 20 and 21
It is slidably installed so that it can reciprocate in a water-tight manner.
前記シリンダ大径部１３の先端部には大径部室
２２が形成され、かつシリンダ大径部１３の基端
部には前記大径パツキング２０を介して大径部室
２２に隣接する吸入室２３が形成される。吸入室
２３は吸入弁２４を介して大径部室２２に連通さ
れ、吸入室２３には吸入口２５が形成される。ま
た大径部室２２は、シリンダ１５のほぼ中央側部
に形成されると共に互いに直列に配設される吐出
弁２６及び設定圧調整可能の調圧弁２７を介して
余水口２８に連通される。 A large-diameter chamber 22 is formed at the distal end of the cylinder large-diameter section 13, and a suction chamber 23 adjacent to the large-diameter chamber 22 is formed at the base end of the cylinder large-diameter section 13 via the large-diameter packing 20. It is formed. The suction chamber 23 is communicated with the large diameter chamber 22 via a suction valve 24, and a suction port 25 is formed in the suction chamber 23. The large-diameter chamber 22 also communicates with a spill port 28 via a discharge valve 26 and a pressure regulating valve 27 that can adjust the set pressure, which are formed approximately at the central side of the cylinder 15 and are arranged in series with each other.
またシリンダ１５とクランクケース１１との間
にはオイルシール２９が介在され、クランクケー
ス１１内のオイルがシリンダ１５内に侵入するの
を防止している。 Further, an oil seal 29 is interposed between the cylinder 15 and the crankcase 11 to prevent oil in the crankcase 11 from entering the cylinder 15.
前記シリンダ小径部１４の先端側には、前記小
径パツキング２１を介して前記大径部室２２に隣
接される小径部室３０が形成される。小径部室３
０はピストン小径部１７に穿設される水路３１及
び水路３１の先端部に形成される吸入弁３２をそ
れぞれ介して前記大径部室２２に連通される。ま
た小径部室３０はシリンダ小径部１４の先端部に
形成される吐出弁３３を介して吐出路３４に連通
され、吐出路３４の端部には吐出口３５が形成さ
れる。また余水口３７は吐出路３４より分岐され
て配設される調圧弁３６を介して開口される。 A small-diameter chamber 30 is formed on the distal end side of the cylinder small-diameter section 14 and is adjacent to the large-diameter chamber 22 via the small-diameter packing 21 . Small diameter chamber 3
0 is communicated with the large diameter chamber 22 through a water channel 31 formed in the piston small diameter section 17 and a suction valve 32 formed at the tip of the water channel 31, respectively. Further, the small diameter portion chamber 30 is communicated with a discharge passage 34 via a discharge valve 33 formed at the tip of the cylinder small diameter portion 14, and a discharge port 35 is formed at the end of the discharge passage 34. Further, the spillage port 37 is opened via a pressure regulating valve 36 which is branched from the discharge path 34 and disposed.
この考案による往復ポンプは以上に述べたよう
であるから、クランク軸の回転によるピストン大
径部１６及びピストン小径部１７の往復動によ
り、吸入口２５から流体が吸入室２３内に吸入さ
れ、かつ吸入弁２４から大径部室２２内に吸入さ
れる。そして大径部室２２内に流入された流体
は、吐出弁２６及び調圧弁２８を通つて余水口２
８に排出されるか又は、水路３１を通つて吸入弁
３２から小径部室３０内に吸入される。この際大
径部室２２の容積変化をQ1とする。 Since the reciprocating pump according to this invention is as described above, fluid is sucked into the suction chamber 23 from the suction port 25 by the reciprocating movement of the piston large diameter portion 16 and the piston small diameter portion 17 due to the rotation of the crankshaft, and The air is sucked into the large diameter chamber 22 from the suction valve 24 . The fluid that has flowed into the large diameter chamber 22 passes through the discharge valve 26 and the pressure regulating valve 28 and then flows through the spillway 22.
8 or sucked into the small diameter chamber 30 from the suction valve 32 through the water channel 31. At this time, the change in volume of the large-diameter chamber 22 is defined as Q1.
また前記小径部室３０内の流体を吐出弁３３か
ら吐出路３４に吐出され、吐出路３４に吐出され
た流体は、調圧弁３６から余水口３７に流通され
るか又は吐出口３５から外部に吐出される。この
際小径部室３０の容積変化をQ2とする。 Further, the fluid in the small diameter chamber 30 is discharged from the discharge valve 33 to the discharge passage 34, and the fluid discharged to the discharge passage 34 is passed through the pressure regulating valve 36 to the spillway 37 or discharged to the outside from the discharge port 35. be done. At this time, the change in volume of the small diameter chamber 30 is defined as Q2.
ここで、前記調圧弁２７をハンドル２７ａの回
転操作によりP1（例えば500Kg／cm2）に、また調
圧弁３６をハンドル３６ａの回転操作により０以
上P1以下（例えば０Kg／cm2以上500Kg／cm2以下）
にそれぞれ圧力設定する。前記ピストン手段１８
の往復動により、大径部室２２内への流体の吸入
量Q1は、調圧弁２７が閉塞されて余水口２８か
ら外方へ排出できないため、前記小径部室３０内
への吸入量Q2と共にすべて小径部室３０へ吸入
されて、吐出弁３３を通つて吐出口３５から吐出
される。このときの吐出量はQ1＋Q2（圧力０
Kg／cm2以上500Kg／cm2以下）となる。 Here, the pressure regulating valve 27 is set to P1 (for example, 500 Kg/cm 2 ) by rotating the handle 27a, and the pressure regulating valve 36 is set to 0 to P1 (for example, 0 Kg/cm 2 to 500 Kg/cm 2 ) by rotating the handle 36a. below)
Set the pressure for each. Said piston means 18
Due to the reciprocating motion of The liquid is sucked into the chamber 30, passes through the discharge valve 33, and is discharged from the discharge port 35. The discharge amount at this time is Q1 + Q2 (pressure 0
Kg/ cm2 or more and 500Kg/ cm2 or less).
また前記調圧弁２７をP1（例えば500Kg／cm2）
に、調圧弁３６をP2（例えば1000Kg／cm2）にそれ
ぞれ圧力設定すると、前記ピストン手段１８の往
復動により、大径部室２２内の圧力がP1（500
Kg／cm2）以上になると、一部の流体α（＜Q1）が
吐出弁２６及び調圧弁２７を通つて余水口２８か
ら外方へ吐出されると共に、大径部室２２内は圧
力P1（500Kg／cm2）に保持され、また他の一部の
流体β（＜Q1）は水路３１及び吸入弁３２を通つ
て小径部室３０内へ吸入量Q2と共に吸入され、
この小径部室３０内の圧力がP2（1000Kg／cm2）に
保持されて、吐出弁３３から吐出路３４を通つて
吐出口３５から吐出される。このときの吐出量は
Q2＋β（圧力1000Kg／cm2）となる。なおQ1＝α
＋βとする。この際、パツキング２１はその大径
部室２２側が圧力P1（500Kg／cm2）で支えられる
ため、正味受け止める圧力はP2−P1（500Kg／cm2）
となり、より耐久性を増大でき、ポンプは組立時
の公差及び製造工程での精度も従来通りでより高
圧に耐えうるものとすることができる。 In addition, the pressure regulating valve 27 is set to P1 (for example, 500Kg/cm 2 ).
When the pressure regulating valve 36 is set to P2 (for example, 1000 kg/cm 2 ), the pressure inside the large diameter chamber 22 is reduced to P1 (500 kg/cm 2 ) due to the reciprocating movement of the piston means 18.
Kg/cm 2 ) or more, a part of the fluid α (<Q1) is discharged outward from the spillway port 28 through the discharge valve 26 and the pressure regulating valve 27, and the pressure inside the large diameter chamber 22 increases to P1 ( 500Kg/cm 2 ), and another part of the fluid β (<Q1) is sucked into the small diameter chamber 30 through the water channel 31 and the suction valve 32 along with the suction amount Q2,
The pressure inside this small diameter chamber 30 is maintained at P2 (1000 Kg/cm 2 ), and the fluid is discharged from the discharge port 35 through the discharge valve 33 and the discharge passage 34 . The discharge amount at this time is
Q2 + β (pressure 1000Kg/cm 2 ). Note that Q1=α
+β. At this time, the packing 21 is supported by the pressure P1 (500Kg/cm 2 ) on its large diameter chamber 22 side, so the net pressure it receives is P2 - P1 (500Kg/cm 2 ).
As a result, durability can be further increased, and the pump can withstand higher pressures while maintaining the same tolerances during assembly and precision during the manufacturing process as before.
［考案の効果］
この考案による往復ポンプによれば以上に述べ
たようであるから、以下のような効果を有するも
のである。[Effects of the invention] As described above, the reciprocating pump according to this invention has the following effects.
(1) 一台の往復ポンプのみで低圧大吐出量（P1，
Q1＋Q2）と高圧小吐出量（P2，Q2＋β）のよ
り巾の広い使用をすることができる。(1) Low-pressure large discharge volume with only one reciprocating pump (P1,
Q1 + Q2) and high pressure and small discharge amount (P2, Q2 + β) can be used in a wider range.
(2) ピストン小径部１７のパツキング２１は大径
部室２２の圧力P1が背圧として作用するため、
漏れ防止に寄与すると共に、パツキング２１の
高圧側と低圧側との間の圧力勾配をより小とす
ることができ、パツキング２１の耐久性をより
向上することができる。(2) Since the pressure P1 in the large diameter chamber 22 acts as back pressure on the packing 21 of the small diameter portion 17 of the piston,
In addition to contributing to leakage prevention, the pressure gradient between the high pressure side and the low pressure side of the packing 21 can be made smaller, and the durability of the packing 21 can be further improved.
(3) パツキング２０及び２１はそねぞれ高低圧両
側から揚液で潤滑されるのでより耐久性が向上
する。(3) Since the packings 20 and 21 are lubricated by pumped liquid from both high and low pressure sides, durability is further improved.
第１図はこの考案による往復ポンプを示す要部
断面図で、第２図は従来の往復ポンプの一部を示
す断面図である。
なお図において、１１……クランクケース、１
２……連接棒、１３……シリンダ大径部、１４…
…シリンダ小径部、１５……シリンダ、１６……
ピストン大径部、１７……ピストン小径部、１８
……ピストン手段、２０……大径パツキング手段
（大径パツキング）、２１……小径パツキング手段
（小径パツキング）、２２……大径部室、２３……
吸入室、２４，３２……吸入弁、２５……吸入
口、２６，３３……吐出弁、２７，３６……調圧
弁、２８，３７……余水口、３０……小径部室、
３１……水路、３５……吐出口である。
FIG. 1 is a sectional view of a main part of a reciprocating pump according to this invention, and FIG. 2 is a sectional view of a part of a conventional reciprocating pump. In the figure, 11... crankcase, 1
2...Connecting rod, 13...Cylinder large diameter part, 14...
...Cylinder small diameter part, 15...Cylinder, 16...
Piston large diameter part, 17...Piston small diameter part, 18
...Piston means, 20... Large diameter packing means (large diameter packing), 21... Small diameter packing means (small diameter packing), 22... Large diameter chamber, 23...
Suction chamber, 24, 32... Suction valve, 25... Suction port, 26, 33... Discharge valve, 27, 36... Pressure regulating valve, 28, 37... Spill port, 30... Small diameter chamber,
31...water channel, 35...discharge port.
Claims (1)
備えてなる往復ポンプであつて、前記シリンダ体
に互いに連通可能のシリンダ大径部とシリンダ小
径部とを備え、これらシリンダ大径部及びシリン
ダ小径部には、前記ピストン手段を構成するピス
トン大径部とピストン小径部とをそれぞれ大径パ
ツキング手段及び小径パツキング手段を介して水
気密状態で摺設させ、前記シリンダ大径部に前記
大径パツキング手段によつて互いに分離される大
径部室及び吸入口を備える吸入室を形成し、これ
ら大径部室及び吸入室を吸入弁を介して互いに連
通させ、この大径部室を吐出弁及び設定圧調整可
能の調圧弁を介して余水口に連通させ、前記ピス
トン小径部に前記小径パツキング手段を介して前
記大径部室と分離される小径部室を画設し、この
小径部室を吸入弁を介して前記大径部室に連通さ
せるとともに吐出弁を介して吐出口を連通させ、
かつ吐出弁及び設定圧調整可能の調圧弁を介して
余水口に連通させ、もつて前記両調圧弁に対する
適宜の圧力設定により、高圧時前記小径パツキン
グ手段の保持を容易にするとともに、低圧大吐出
量から高圧小吐出量のポンプ作用を可能としてな
る往復ポンプ。 A reciprocating pump comprising a piston means capable of reciprocating sliding in a cylinder body, wherein the cylinder body is provided with a cylinder large diameter part and a cylinder small diameter part that can communicate with each other, and the cylinder large diameter part and the cylinder small diameter part are connected to each other. The piston large diameter part and the piston small diameter part constituting the piston means are respectively slid in a watertight state via the large diameter packing means and the small diameter packing means, and the cylinder large diameter part is connected to the large diameter packing means. Thus, a suction chamber including a large diameter chamber and a suction port which are separated from each other is formed, and the large diameter chamber and the suction chamber are communicated with each other via a suction valve, and this large diameter chamber is connected to a discharge valve and a set pressure adjustable chamber. A small diameter chamber is separated from the large diameter chamber by the small diameter packing means in the small diameter section of the piston, and the small diameter chamber is connected to the large diameter chamber through the suction valve. communicates with the chamber and communicates the discharge port via the discharge valve,
It also communicates with the spillway through a discharge valve and a pressure regulating valve whose set pressure can be adjusted, and by setting appropriate pressures for both of the pressure regulating valves, it is possible to easily hold the small diameter packing means at high pressure, and also to provide a large discharge at low pressure. A reciprocating pump that can perform pumping operations ranging from small volumes to high pressures and small discharge volumes.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985009244U JPH0320550Y2 (en) | 1985-01-26 | 1985-01-26 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985009244U JPH0320550Y2 (en) | 1985-01-26 | 1985-01-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61125684U JPS61125684U (en) | 1986-08-07 |
| JPH0320550Y2 true JPH0320550Y2 (en) | 1991-05-02 |
Family
ID=30489279
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985009244U Expired JPH0320550Y2 (en) | 1985-01-26 | 1985-01-26 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0320550Y2 (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1551522A (en) * | 1977-04-05 | 1979-08-30 | Syndicat Des Coproprietaires D | Free-stroke compressor having a high compression ratio |
| JPS5554683A (en) * | 1978-10-17 | 1980-04-22 | Mitsuwa Seiki Co Ltd | Minimal discharge fluid pump |
| JPS5819864A (en) * | 1981-07-30 | 1983-02-05 | Matsushita Electric Ind Co Ltd | Manufacture of electrode for lead storage battery |
-
1985
- 1985-01-26 JP JP1985009244U patent/JPH0320550Y2/ja not_active Expired
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1551522A (en) * | 1977-04-05 | 1979-08-30 | Syndicat Des Coproprietaires D | Free-stroke compressor having a high compression ratio |
| JPS5554683A (en) * | 1978-10-17 | 1980-04-22 | Mitsuwa Seiki Co Ltd | Minimal discharge fluid pump |
| JPS5819864A (en) * | 1981-07-30 | 1983-02-05 | Matsushita Electric Ind Co Ltd | Manufacture of electrode for lead storage battery |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61125684U (en) | 1986-08-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR880001938A (en) | Drive | |
| JP2018525564A (en) | Dual pumping fluid pump | |
| CA2674961C (en) | Positive displacement pump apparatus | |
| CA1122479A (en) | Double-acting differential piston supply pump | |
| JPS6137465B2 (en) | ||
| US3285182A (en) | Diaphragm metering pump | |
| JPH0320550Y2 (en) | ||
| CA2041511A1 (en) | Dual-acting, reciprocating piston pump | |
| JPH0427392B2 (en) | ||
| EP1152149A3 (en) | Injector | |
| JPH0442530Y2 (en) | ||
| JPH07189887A (en) | Axial piston type pump | |
| JPH0437270Y2 (en) | ||
| JPH0645664Y2 (en) | Reciprocating pump | |
| US330540A (en) | worthington | |
| SU1613676A1 (en) | Sealed piston pump | |
| JPH0313586Y2 (en) | ||
| JPH075258Y2 (en) | Pump device | |
| US20150204320A1 (en) | Diaphragm pump | |
| RU2395717C1 (en) | Gas and gas-liquid injection unit | |
| SU1758285A1 (en) | Method and piston pump for delivery of liquid | |
| JP2517427Y2 (en) | Piston pump | |
| RU2266429C1 (en) | Hydraulic compression booster pump | |
| CN118224133A (en) | Active pressurizing hydraulic oil tank for lifting load of tractor | |
| JP2714870B2 (en) | Diaphragm pump |