JPS58135383A - Hydraulic piston pump - Google Patents

Hydraulic piston pump

Info

Publication number
JPS58135383A
JPS58135383A JP57165120A JP16512082A JPS58135383A JP S58135383 A JPS58135383 A JP S58135383A JP 57165120 A JP57165120 A JP 57165120A JP 16512082 A JP16512082 A JP 16512082A JP S58135383 A JPS58135383 A JP S58135383A
Authority
JP
Japan
Prior art keywords
piston
pistons
pump
pressure chamber
port
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
Application number
JP57165120A
Other languages
Japanese (ja)
Inventor
Efu Keraa Uiriamu
ウイリアム・エフ・ケラ−
Dee Shiburei Richiyaado
リチヤ−ド・デ−・シブレイ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KOUSOU SERVICE KK
Original Assignee
KOUSOU SERVICE KK
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by KOUSOU SERVICE KK filed Critical KOUSOU SERVICE KK
Publication of JPS58135383A publication Critical patent/JPS58135383A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0531—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with cam-actuated distribution members
    • F04B1/0533—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with cam-actuated distribution members each machine piston having channels that coact with the cylinder and serve as distribution members for another piston-cylinder unit

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

PURPOSE:To enable to reduce the hammering noise of a hydraulic piston pump, by forming a diameter-reduced portion in each of a pair of pistons so that the pistons function as slide valves, and opening and closing an intake port and a discharge port alternately by said pair of pistons. CONSTITUTION:As a pump shaft 8 continues to turn in a clockwise direction, a piston 15 is moved upward and a piston 2 is moved further downward, so that a diameter-reduced portion 4 is communicated with an intake port 3 and then with a pressure chamber 14 of the piston 15 via a conduit 16. Resultantly, oil is drawn into the pressure chamber 14 from the intake port 3 of the piston 2. On the other hand, while the piston 2 is moved downward, oil in a pressure chamber 18 of the piston 2 is pressurized by the piston 2 and discharged to the outside via a conduit 17, a diameter-reduced portion 13 and an outlet port 12.

Description

【発明の詳細な説明】 本発明は、チェツキ弁等の補助バルプヲ使用せずに、ピ
ストンの往復運動のみで油圧を発生させるピストンポン
プに関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a piston pump that generates hydraulic pressure only by reciprocating movement of a piston without using an auxiliary valve such as a check valve.

一般にピストンの運動に同期して、吸入と吐出の切換を
行うパルプの形式にはいろいろあるが、第１図の吸入弁
ボート形、吸入弁組込形、チェツキパルプ形に関する従
来の油圧ピストンポンプは、ピストンの他にバルブ機構
として、チェツキバルブを利用した補助パルプを要して
いた。In general, there are various types of pulp that switch between suction and discharge in synchronization with the movement of the piston, but the conventional hydraulic piston pumps related to the suction valve boat type, suction valve built-in type, and Czech pulp type shown in Figure 1 are as follows: In addition to the piston, the valve mechanism required an auxiliary pulp using a check valve.

この補助パルプは長時間運転中、弁座とのあたりによる
傷等が進行し、油漏れによる容積効率が低下し、チェツ
キバルブが弁座にあたることによる打撃騒音が非常に高
くなる欠点を有していた。During long-term operation, this auxiliary pulp developed scratches due to contact with the valve seat, decreased volumetric efficiency due to oil leakage, and had the disadvantages of extremely high impact noise due to the check valve hitting the valve seat. .

本発明の油圧ピストンポンプは、補助パルプを一切使わ
ず一対のピストンの中央部に縦組軸部を配設して、弁部
を形成させ、該弁部と対応する吸入口、吐出口全配設す
ることにより、前記の補助パルプ付油圧ポンプの諸欠点
を解消することを目的とするものである。The hydraulic piston pump of the present invention does not use any auxiliary pulp and has a vertically assembled shaft section arranged in the center of a pair of pistons to form a valve section, and the entire intake port and discharge port are connected to the valve section. By providing this, the purpose is to eliminate the various drawbacks of the above-mentioned hydraulic pump with auxiliary pulp.

本発明の実施の一例を図面に基づいて説明する。An example of implementation of the present invention will be described based on the drawings.

第２図は、本発明である油圧ピストンボンプの原理説明
図である。FIG. 2 is an explanatory diagram of the principle of the hydraulic piston pump according to the present invention.

第２図（Ａ）に於いて該油圧ピストンポンプのポンプ軸
８はポンプボディ１にベアリングＣ，Ｄで保持されてい
る。In FIG. 2(A), the pump shaft 8 of the hydraulic piston pump is held in the pump body 1 by bearings C and D.

このベアリングＣＸＤ間に、ポンプ軸８の中心から偏る
偏心ローラー９が、キーＥ等で固定されている。Between the bearings CXD, an eccentric roller 9 offset from the center of the pump shaft 8 is fixed with a key E or the like.

一方、ポンプボディ１内に一対のピストン２．１５がｘ
−ｘ’組線上有り、ポンプ軸８の中心軸上に、９０°の
角度で配設されている。On the other hand, inside the pump body 1, a pair of pistons 2.15 x
-x' is on the set line, and is arranged on the central axis of the pump shaft 8 at an angle of 90°.

第２図（８）に於いて、ピストンの頭部のピストンヘッ
ド２’、　　１５’とポンプボディ１間にはそれぞれス
プリング６．１０が間挿されており、ピストンヘッド２
’、１５’は常に偏心ローラー９に対向して、スプリン
グ６．１０で押しつけられている。In FIG. 2 (8), springs 6 and 10 are inserted between the piston heads 2' and 15' at the head of the piston and the pump body 1, respectively, and the piston head 2
', 15' are always pressed against the eccentric roller 9 by a spring 6.10.

各々のピストンで、２．１５は、ピストンの中央部に超
細軸部４．１３に形成し、吸入口３，１１、吐出口５，
１２及び管路１６，１７から成る圧油日と対応して三方
スプール弁を形成する。In each piston, 2.15 is formed in an ultra-thin shaft part 4.13 in the center of the piston, and has suction ports 3, 11, discharge ports 5,
12 and conduits 16 and 17 to form a three-way spool valve.

一対のピストンの超細軸部の面間部４，１３の長すＬは
、吸入口３，１１と吐出口５．１２の孔の内側間の長す
Ｓにほぼ等しくなっている。The length L of the inter-face portions 4, 13 of the ultra-thin shaft portions of the pair of pistons is approximately equal to the length S between the inner sides of the holes of the suction ports 3, 11 and the discharge ports 5.12.

今、なんらかの回転力源、例えば電動モーターをポンプ
軸８に直結し、ポンプ軸８を第２図（Ｂ）の矢印７に示
した時計方向に回転すると、ポンプ軸８に対して、偏心
ローラー９が同期回転し、ピスト７２，１５が往復運動
するっ 各々のピストンの吸入口３．１１は油全吸入できるよう
に油槽につないでいる。Now, when some kind of rotational power source, such as an electric motor, is directly connected to the pump shaft 8 and the pump shaft 8 is rotated clockwise as shown by the arrow 7 in FIG. 2(B), the eccentric roller 9 The pistons 72 and 15 rotate synchronously, and the pistons 72 and 15 reciprocate.The suction ports 3 and 11 of each piston are connected to an oil tank so that all of the oil can be sucked in.

第３回込）〜０）は、偏心ローラー９が回転して、９０
°位相差ヲ持つ一対のピストンの各々の角度に於ける往
復運動を表わした説明図であり、第３図に示した番号は
第２図と同じものの番号で表わしている。3rd round) to 0), the eccentric roller 9 rotates and the 90
It is an explanatory view showing the reciprocating motion of a pair of pistons having a phase difference at each angle, and the numbers shown in FIG. 3 are the same as those in FIG. 2.

各々のピストンは、上死点と下死点との間を往復運動し
、一つのピストンが上死点か、又は下死点にある時、他
方のピストンは中間行程にある。Each piston reciprocates between top dead center and bottom dead center, and when one piston is at top dead center or bottom dead center, the other piston is on an intermediate stroke.

ピストン２または１５が中間行程にある時に、ピストン
の超細軸部の面間部４，１３の長すＬが吸入口３，１１
と吐出口５，１２間の長すＳにほぼ等しくなるように配
置される。When the piston 2 or 15 is in the middle stroke, the length L of the surface portions 4, 13 of the ultra-thin shaft portion of the piston is the suction port 3, 11.
and the length S between the discharge ports 5 and 12.

従って、ピストンの超細軸部の面間部の端面、４′、４
ｉ１３’、１３１１によって吸入口３．１１と吐出口５
．１２が閉じられる。Therefore, the end surfaces of the ultra-thin shaft portion of the piston, 4', 4
Inlet port 3.11 and outlet port 5 by i13', 1311
．． 12 is closed.

ピストン２．１５が上死点又は下死点へ行く行程に於い
て、前記ピストン軸の端面、４′、４ζ　１３′、１３
′、が吸入口３，１１及び吐出口５．１２ｅ交互に開閉
する。During the stroke of the piston 2.15 to the top dead center or bottom dead center, the end faces of the piston shaft, 4', 4ζ 13', 13
', the suction ports 3 and 11 and the discharge ports 5 and 12e are alternately opened and closed.

第３図ＩＡ）は、ピストン１５が、上死点にある時’ｉ
ｏ’　とするとピストン２は、ピストン１５より９０°
位相が進んだ中間行程にあることを表わしている。この
時、ピストン２の超細軸部４は吸入口３及び吐出口５か
らの管路を閉じ、ピストン１５の超細軸部１３は、吐出
口１２及び管路１７を通過して、ピストン２の圧力室１
８に導びかれている。偏心ローラー９を固定したポンプ
軸８が時計方向に回転しつつけると、ピストン１５は上
死点より吸入行程に入って上昇し、ピストン２は中間行
程からさらに下降して超細軸部４は吸入口３に導通し、
管路１６を通過（−て、ピストン１５の圧力室１４に通
じる。Fig. 3 IA) is when the piston 15 is at the top dead center.
o', piston 2 is 90° from piston 15
This indicates that the phase is in an intermediate stage where the phase is advanced. At this time, the ultra-thin shaft part 4 of the piston 2 closes the pipe from the suction port 3 and the discharge port 5, and the super-fine shaft part 13 of the piston 15 passes through the discharge port 12 and the pipe line 17, and the piston 2 pressure chamber 1
It is guided by 8. When the pump shaft 8 to which the eccentric roller 9 is fixed continues to rotate clockwise, the piston 15 enters the suction stroke from top dead center and rises, the piston 2 further descends from the middle stroke, and the ultra-thin shaft portion 4 moves upward. conducts to the suction port 3,
It passes through a conduit 16 (-) and communicates with the pressure chamber 14 of the piston 15.

従って、圧力室１４には、ピストン２の吸入口３より油
が吸込まれる。Therefore, oil is sucked into the pressure chamber 14 from the suction port 3 of the piston 2.

一方、ピストン２が下降している間ピストン２の圧力室
１８内の油はピストン２に押されて圧力がかかり、管路
１７、超細軸部１３及び吐出口１２を通って、吐出され
る。On the other hand, while the piston 2 is descending, the oil in the pressure chamber 18 of the piston 2 is pushed by the piston 2, pressure is applied, and the oil is discharged through the pipe line 17, the ultra-thin shaft portion 13, and the discharge port 12. .

偏心ローラーが、９０°の位置に来ると、ピストン２は
上死点となり、ピストン２の圧力室１８内の油は、吐出
口１２より、吐き出されて、ピストン１５は中間行程に
なるため超細軸部１３は、吸入口１１及び吐出口１２を
閉じる。When the eccentric roller reaches the 90° position, the piston 2 is at the top dead center, the oil in the pressure chamber 18 of the piston 2 is discharged from the discharge port 12, and the piston 15 is in the middle stroke, so it becomes ultra-thin. The shaft portion 13 closes the suction port 11 and the discharge port 12.

さらに、ポンプ軸８が回転して偏４ｓ　口−ラ−が１８
０°の位置に来ると、ピストン２は、吸入行程に入る。Furthermore, the pump shaft 8 rotates and the deviation is 4s.
Once at the 0° position, the piston 2 enters the suction stroke.

ピストン１５は、中間行程から上昇しつづけて線維軸部
１３は、吸入口１１を開き、管路１７を通って圧力室１
８に導ひかれる。ピストン２は上昇しつづけるので、吸
入口１１から、圧力室１８に油が吸入される。The piston 15 continues to rise from the middle stroke, and the fiber shaft portion 13 opens the suction port 11 and passes through the conduit 17 to the pressure chamber 1.
I am guided by 8. Since the piston 2 continues to rise, oil is sucked into the pressure chamber 18 from the suction port 11.

このようにして、ポンプ軸８が回転を続けると、ピスト
ンは往復運動を続け、油は吸入口３．１１から吐出口５
，１２へ流出する。In this way, as the pump shaft 8 continues to rotate, the piston continues its reciprocating motion, and the oil flows from the suction port 3.11 to the discharge port 5.
, 12.

以上の説明は、ポンプ軸８金時計方向に回転した場合の
実施例であるが、反時計方向に回転した場合に於いても
、吸入口３，１１が吐出口となり、吐出口５，１２が吸
入口となるだけで本説明の動作と同様な作用が得られる
。The above explanation is an example in which the pump shaft is rotated clockwise, but even when the pump shaft is rotated counterclockwise, the suction ports 3 and 11 become the discharge ports, and the discharge ports 5 and 12 become the discharge ports. Just by serving as an inlet, the same effect as that described in this explanation can be obtained.

ピストンの他にチェツキバルブを補助バルブとして備え
た従来の油圧ピストンポンプは長時間運転中、チェツキ
バルブが弁座とのあたりによって傷等が進行し、ピスト
ンが吸入行程中、吐出した油をピストン圧力室に吸込み
同様に吐出行程中、吐出するべき油を吸入弁を通って、
油槽に漏れる等の容積効率の低Ｆ並びに、チェツキバル
ブが弁座にあたることによる打撃、騒音が著るしく高い
。特に高圧時に於いては、この機械的な騒音が一段と高
くなる。Conventional hydraulic piston pumps, which are equipped with a check valve as an auxiliary valve in addition to the piston, are operated for long periods of time, and the check valve gets damaged due to contact with the valve seat, causing oil discharged by the piston to flow into the piston pressure chamber during the suction stroke. Similar to suction, during the discharge stroke, the oil to be discharged passes through the suction valve,
The volumetric efficiency is low due to leakage into the oil tank, and the impact and noise caused by the check valve hitting the valve seat are extremely high. Particularly at high pressures, this mechanical noise becomes even higher.

これらの問題点に対し、本発明は補助パルプを１史わす
、ピストンに線維軸部を形成して吸入口と吐出口を交互
開閉することができ、ポンプ動作ヲキせることができる
。In order to solve these problems, the present invention allows the piston to contain the auxiliary pulp and has a fiber shaft portion, so that the suction port and the discharge port can be alternately opened and closed, and the pump operation can be controlled.

これによりポンプに傷等が発生せず、長期間に亘って容
績効惠が低下せず、壕だ、高圧時に於いても容積効率の
低下は少ない。As a result, the pump will not be damaged, the volumetric efficiency will not decrease over a long period of time, and there will be little decrease in volumetric efficiency even in trenches or under high pressure.

−ｙのチェツキバルブを使用した油圧ピストンポンプと
比較して、発生騒音の一因である機械系の振動に基づく
打撃騒首がなく騒音の低い、画期的な油圧ピストンポン
プの出現が得られるものである。-Compared to hydraulic piston pumps using check valves of y, it is possible to create an innovative hydraulic piston pump with low noise and no impact noise due to mechanical system vibrations, which is a cause of noise generation. It is.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図（４）〜（Ｃ）は、チェツキバルブ全補助ノくル
ブとして具備した従来の油圧ピストンポンプの構造図で
ある。イは吸入弁口は吐出弁である。 第２図（Ａ）は偏心ローラ一部の断面図、第２図（Ｂ）
は第２図（Ａ）のｘ　−ｘ’部の断面図で本発明である
油圧ピストンポンプの原理説明図である。 第３図体）〜のンは、本発明である油圧ピストンポンプ
の動作説明図である。 ２．１５・・・ピストン ３．１１・・・吸入口 ４．１３・・・線維軸部 ５．１２・・・吐出口 ９・・・偏心ローラー １４．１８・・・圧力室 １６．１７・・・管路 Ａ）啜六邦ボート形 υ Ｃ）チェツキバルブ形 手続補正書（方式） 昭和５８年３月１０日 特許庁長官　若杉和夫　殿 １、事件の表示 特願昭５７−１６５１２０号 ２、発明の名称 油圧ピストンポンプ ３　補正をする者 事件との関係　　　特許出願人 名称　　工装サービス株式会社 ４、代理人 住　所　　東京都港区西新橋１−８−８中銀虎ノ門ビル
氏名　（６１７Ｂ）弁理士相良省三 ５、補正命令の日付 昭和５８年２月２２日（発送日） ６、補正の対象 明細書の「図面の簡単な説明」の欄及び図面（第１図）
。 ７、補正の内容 （１）明細書９頁５行の「構造図である。」の次に下記
を加入する。 「（Ａ）は吸入弁ボート形を、（Ｂ）はチェツキパルプ
形を、（Ｃ）は吸入弁組込形を示す。」（２）図面の第
１図を別紙のとおり補正する。 （２） （Ｃ） 図 （Ａ＞ Ｕ （８）FIGS. 1(4) to 1(C) are structural diagrams of a conventional hydraulic piston pump equipped with a check valve as a full auxiliary knob. In A, the suction valve port is the discharge valve. Figure 2 (A) is a cross-sectional view of a part of the eccentric roller, Figure 2 (B)
2(A) is a sectional view taken along the line x-x' of FIG. Figures 3) to 3 are explanatory views of the operation of the hydraulic piston pump according to the present invention. 2.15...Piston 3.11...Suction port 4.13...Fiber shaft portion 5.12...Discharge port 9...Eccentric roller 14.18...Pressure chamber 16.17... ... Pipeline A) Surokuho boat type υ C) Check valve type Procedural amendment (method) March 10, 1980 Commissioner of the Japan Patent Office Kazuo Wakasugi 1. Indication of case Patent application No. 165120/1982 2. Invention Name of Hydraulic Piston Pump 3 Relationship with the person making the amendment Name of patent applicant Koso Service Co., Ltd. 4 Address of agent Nakagin Toranomon Building, 1-8-8 Nishi-Shinbashi, Minato-ku, Tokyo Name (617B) Patent attorney Sho Sagara 35. Date of amendment order: February 22, 1982 (dispatch date) 6. "Brief explanation of drawings" column and drawings of the specification subject to amendment (Figure 1)
. 7. Contents of amendment (1) The following is added next to "This is a structural diagram" on page 9, line 5 of the specification. "(A) shows the suction valve boat type, (B) shows the checkered pulp type, and (C) shows the suction valve built-in type." (2) Figure 1 of the drawings is amended as shown in the attached sheet. (2) (C) Figure (A> U (8)

Claims (1)

【特許請求の範囲】[Claims] 偏心ローラー等を回転することによって、ピストン全往
復運動に変換する型のポンプに於いて、一対のピストン
に、該ピストンの中間部にピストン径よりも縦組軸部分
を形成し、該縦組軸部の面間部の距離と対応する位置に
吸入口と吐出口全本体に穿孔し、該吸入口と吐出口の中
間部に管路を配設して、該管路を相手ピストン下部の圧
力室に導通させて、該一対のピストンが位相差を９０°
になるように本体に配設してなる油圧ピストンポンプ。In a type of pump that converts the entire reciprocating motion of the pistons by rotating an eccentric roller or the like, a pair of pistons has a vertical assembly shaft portion formed in the middle part of the pistons, which is longer than the piston diameter, and the vertical assembly shaft A hole is made in the entire body of the suction port and the discharge port at a position corresponding to the distance between the surfaces of the piston, and a pipe is provided in the middle part between the suction port and the discharge port, and the pipe is connected to the pressure at the bottom of the mating piston. conduction to the chamber, and the pair of pistons have a phase difference of 90°.
A hydraulic piston pump that is installed in the main body so that
JP57165120A 1981-11-16 1982-09-24 Hydraulic piston pump Pending JPS58135383A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US32144281A 1981-11-16 1981-11-16
US6/321442 1981-11-16

Publications (1)

Publication Number Publication Date
JPS58135383A true JPS58135383A (en) 1983-08-11

Family

ID=23250626

Family Applications (1)

Application Number Title Priority Date Filing Date
JP57165120A Pending JPS58135383A (en) 1981-11-16 1982-09-24 Hydraulic piston pump

Country Status (1)

Country Link
JP (1) JPS58135383A (en)

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