JPH06167277A - Pump with partially hollow piston - Google Patents
Pump with partially hollow pistonInfo
- Publication number
- JPH06167277A JPH06167277A JP5178299A JP17829993A JPH06167277A JP H06167277 A JPH06167277 A JP H06167277A JP 5178299 A JP5178299 A JP 5178299A JP 17829993 A JP17829993 A JP 17829993A JP H06167277 A JPH06167277 A JP H06167277A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- fluid
- chamber
- pressure chamber
- high 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.)
- Pending
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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
- F04B53/125—Reciprocating valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Compressor (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、ポンプ特に高圧ポンプ
又は超高圧ポンプに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump, especially a high pressure pump or an ultra high pressure pump.
【０００２】[0002]
【従来の技術】かかるポンプは石油関連工業、産業洗浄
工業および土木工業に利用されている。これらのポンプ
は、その出力が非常に大きく、一般には約３７３０００
〜７４６０００又は８９５２００ジュール／ｓ（即ち５
００〜１０００又は１２００ＣＶ）であること、および
非常に腐食性のある流体（例えば酸性の強い流体）、摩
耗性の強い流体（油井をコンクリート打ちするためのセ
メントスラリ）、支持作用材（砂）が充填されている石
油工業における破砕性ゲルのような特殊な流体、あるい
は他の特別な流体を搬送しなければならないことによっ
て特色づけられる。2. Description of the Related Art Such pumps are used in petroleum related industries, industrial cleaning industries and civil engineering industries. These pumps have very high power output, typically around 373000.
~ 746000 or 895200 Joules / s (ie 5
0 to 1000 or 1200 CV), and a highly corrosive fluid (for example, a strongly acidic fluid), a highly abrasive fluid (cement slurry for concrete pouring an oil well), and a support working material (sand). It is characterized by having to carry special fluids, such as frangible gels in the petroleum industry being filled, or other special fluids.
【０００３】更に石油工業は非常に精確な寸法および重
量の仕様を要求し、これは明らかに機械的な強度、出
力、およびそのようなポンプに対して要求される耐摩耗
性および耐摩滅性に対して矛盾している。In addition, the petroleum industry requires very precise dimensional and weight specifications, which are apparently due to mechanical strength, power output, and wear and abrasion resistance required for such pumps. Contrary to that.
【０００４】改良しなければならない多数のポンプが知
られている。A large number of pumps are known which must be improved.
【０００５】この種のポンプは概略的には「出力端部」
と「流体端部」とを有している。出力端部はピストンを
変位するために必要なすべての要素を有している。This type of pump is generally referred to as the "output end".
And “fluid end”. The output end has all the necessary elements to displace the piston.
【０００６】流体端部は非常に高圧の端部であり、概略
的にはその入口弁と出口弁とを持つピストン室を形成す
る本体と、流体放出要素とを有している。The fluid end is a very high pressure end, which generally has a body forming a piston chamber with its inlet valve and outlet valve, and a fluid discharge element.
【０００７】一般的なポンプにおいて室は一つ（あるい
は複数）の入口弁と一つ（あるいは複数）の出口弁とを
有している。In a typical pump, the chamber has one (or more) inlet valve and one (or more) outlet valve.
【０００８】一般にこれらの弁はピストンの自由端と反
対側における室の端部に位置されている。Generally, these valves are located at the end of the chamber opposite the free end of the piston.
【０００９】このようなポンプの構造および運転は従来
において非常によく知られている。The construction and operation of such pumps is very well known in the prior art.
【００１０】また「インライン」としても知られてい
る。It is also known as "inline".
【００１１】[0011]
【発明が解決しようとする課題】本発明はこのような
「インライン」流体端部の改良に関し、質量の低下およ
び重量の低下を可能とし、容積効率を向上することにあ
る。SUMMARY OF THE INVENTION The present invention is directed to improving such "in-line" fluid ends and is capable of lowering mass and weight and improving volumetric efficiency.
【００１２】[0012]
【課題を解決するための手段】本発明によればこの目的
は、各ピストンの自由端が中空となっており室を形成
し、この室が一方では室の壁に形成されている一つある
いは複数の開口を通して流体入口管に連通し、他方では
各ピストンの高圧室に入口弁の助けによって連通し、入
口弁はピストンが高圧室から戻るときに開いて入口管と
室を高圧室に連通し、ピストンが高圧室の中に入り込む
ときに閉じて室を密閉し、出口弁によって制御して放出
管を通して流体を噴出することによって達成される。According to the invention, the object is one or more of which the free end of each piston is hollow to form a chamber, which on the one hand is formed in the wall of the chamber. It communicates with the fluid inlet pipe through a plurality of openings, on the other hand, with the help of an inlet valve to the high-pressure chamber of each piston, which opens when the piston returns from the high-pressure chamber and connects the inlet pipe and the chamber with the high-pressure chamber. , By closing the piston as it enters the high pressure chamber to seal the chamber and ejecting fluid through a discharge tube controlled by an outlet valve.
【００１３】[0013]
【実施例】図１に示されている従来における「インライ
ン」ポンプは、高圧本体９、高圧室２および中実ピスト
ン８を含んでいる。その本体９およびピストン８は高圧
室２の高圧を受けるフィラ（詰め物）継手７を有してい
る。図１には簡略化のためにポンプの出力端は示されて
いない。DESCRIPTION OF THE PREFERRED EMBODIMENT The conventional "in-line" pump shown in FIG. 1 includes a high pressure body 9, a high pressure chamber 2 and a solid piston 8. The body 9 and the piston 8 have a filler joint 7 that receives the high pressure of the high pressure chamber 2. The output of the pump is not shown in FIG. 1 for simplicity.
【００１４】ポンプの流体端は高圧室２のピストン８に
近い側の端部における復帰ばね５で付勢されているリン
グ状の入口弁１と、同様に復帰ばね４で付勢されている
出口弁３とを含んでいる。この出口弁３は高圧室２の反
対側端に位置しており、これを気密に閉鎖できる。The fluid end of the pump is a ring-shaped inlet valve 1 that is biased by a return spring 5 at the end of the high-pressure chamber 2 near the piston 8, and an outlet that is also biased by a return spring 4. Valve 3 is included. The outlet valve 3 is located at the opposite end of the high pressure chamber 2 and can be closed airtightly.
【００１５】ピストン８が流入方向Ａに変位するとき、
流体は公知のようにして入口管６を通して吸引によって
引き込まれる。この入口管６は流体を対称に分配するた
めに円環状をしている。その際入口弁１は後方に押圧さ
れ、流体入口を閉鎖していない。ピストン８が停止位置
に到達したとき、高圧室２は流体で満たされ、この流体
は復帰ばね４によってその弁座に押しつけられている出
口弁３で保持されている。When the piston 8 is displaced in the inflow direction A,
The fluid is drawn in by suction through the inlet tube 6 in a known manner. The inlet pipe 6 has an annular shape for symmetrically distributing the fluid. The inlet valve 1 is then pushed rearward and does not close the fluid inlet. When the piston 8 reaches the stop position, the high-pressure chamber 2 is filled with fluid, which is retained by the outlet valve 3 which is pressed against its valve seat by the return spring 4.
【００１６】ピストン８が方向Ｄに押し戻されるとき、
入口弁１は閉鎖し、流体は高圧室２の中に圧送され、出
口弁３は開いて、流体は放出管１１を通って放出され
る。When the piston 8 is pushed back in the direction D,
The inlet valve 1 is closed, the fluid is pumped into the high pressure chamber 2, the outlet valve 3 is opened and the fluid is discharged through the discharge pipe 11.
【００１７】この種の「インライン」流体端は次の二つ
の欠点を有する。即ち一つにはフィラ継手７は高圧に耐
えられないかあるいは不十分であり、これは重大な問題
である。もう一つには入口管６の入口における流体の循
環が大きな摩耗作用を行い、特に領域１２において機械
的に破損する危険がある。更には流体が方向Ａに流入し
て反対方向Ｄに放出されることはポンプ性能を悪くす
る。This type of "in-line" fluid end has two drawbacks. That is, in part, the filler joint 7 cannot withstand high pressure or is insufficient, which is a serious problem. On the other hand, the circulation of the fluid at the inlet of the inlet pipe 6 has a large wear effect, with the risk of mechanical damage, especially in the region 12. Further, the fact that the fluid flows in the direction A and is discharged in the opposite direction D deteriorates the pump performance.
【００１８】本発明に基づいてピストン自体が図２に示
されているように変更され、「インライン」流体端と共
働する。即ち本発明に基づくポンプ装置は、高圧室端本
体２１、ピストン１６と共に低圧室２４を境界づける低
圧室本体２２、流体入口管２６および放出管２０を含ん
でいる。In accordance with the present invention, the piston itself is modified as shown in FIG. 2 to cooperate with the "in-line" fluid end. That is, the pump device according to the present invention includes a high pressure chamber end body 21, a low pressure chamber body 22 that bounds the low pressure chamber 24 together with the piston 16, a fluid inlet pipe 26 and a discharge pipe 20.
【００１９】高圧室本体２１はピストン１６と共に高圧
室１３を境界づけている。ピストン１６はその放出管２
０の前に位置する延長部１７（ピストン１６の自由端）
が部分的に中空となっている。この延長部１７はピスト
ン１６本体の中に高圧室１９を形成しており、高圧室１
９は後部において一つ（あるいは複数）の開口で低圧室
２４に連通しており、頭部において（例えば放出管２０
に対して）入口弁１５を有している。The high pressure chamber body 21 bounds the high pressure chamber 13 together with the piston 16. Piston 16 is its discharge tube 2
Extension 17 located in front of 0 (free end of piston 16)
Is partially hollow. This extension 17 forms a high pressure chamber 19 in the body of the piston 16 and
9 communicates with the low pressure chamber 24 through one (or a plurality of) openings at the rear portion, and at the head portion (for example, the discharge pipe 20).
(For) the inlet valve 15.
【００２０】更には入口管２６は低圧室２４に開口し、
放出管２０は出口弁１４を有している。Further, the inlet pipe 26 opens into the low pressure chamber 24,
The discharge pipe 20 has an outlet valve 14.
【００２１】高圧継手２３はピストン１６の周りで高圧
室１３と低圧室２４との間の領域を密封している。低圧
継手２５は低圧室２４を密封している。The high pressure joint 23 seals around the piston 16 in the region between the high pressure chamber 13 and the low pressure chamber 24. The low pressure joint 25 seals the low pressure chamber 24.
【００２２】入口弁１５と出口弁１４の復帰ばねは簡略
化のために図示されておらず、その作用は一般的であり
後述する運転モードの説明から明らかである。The return springs for the inlet valve 15 and the outlet valve 14 are not shown for the sake of simplicity, their operation is general and will be apparent from the description of the operating modes described below.
【００２３】ピストン１６が流入方向Ａに変位されたと
き、周知の現象が高圧室１３における圧力を低下する。
入口弁１５は開き、出口弁１４は閉じ、流体は低圧室２
４から開口あるいはポート１８を通って高圧室１９に流
入し、最終的に高圧室１３に流入する。When the piston 16 is displaced in the inflow direction A, a known phenomenon reduces the pressure in the high pressure chamber 13.
The inlet valve 15 is open, the outlet valve 14 is closed, the fluid is in the low pressure chamber 2
4 to the high pressure chamber 19 through the opening or the port 18 and finally to the high pressure chamber 13.
【００２４】運転中においてすべての室は明らかに永久
的に流体で満たされている。During operation, all chambers are obviously permanently filled with fluid.
【００２５】ピストン１６が方向Ｄに押し戻されると
き、入口弁１５は閉じ、高圧室１３における流体は、流
体が満たされ入口弁１５で閉じられている延長部１７で
形成されているピストンによって圧縮され、出口弁１４
は開き、流体は放出管２０を通って放出される。When the piston 16 is pushed back in the direction D, the inlet valve 15 closes and the fluid in the high pressure chamber 13 is compressed by the piston formed by the extension 17 which is filled with fluid and closed by the inlet valve 15. , Outlet valve 14
Opens and fluid is discharged through the discharge tube 20.
【００２６】本発明は幾つかの利点を有し、これらはす
べて非常に重要であるだけでなく決定的なものである。The present invention has several advantages, all of which are crucial as well as crucial.
【００２７】デッドスペースが非常に小さな容積に実質
的に零に低減されることは評価されねばならない。これ
は明らかに高圧ポンプの容積効率に積極的な効果を有す
る。It has to be appreciated that the dead space is reduced to substantially zero in a very small volume. This obviously has a positive effect on the volumetric efficiency of the high pressure pump.
【００２８】現在の技術において上述したように高圧継
手２３が正確に気密作用を行わないという問題をしばし
ば生ずるが、本発明においてはこれは、損失流体が何ら
の公害を生ずることなしに低圧室２４において容易に回
収されるのでほとんど問題とならない（これはすべての
オイル分野において特に決定的な価値がある）。低圧継
手に関する限りでは現在の技術は容易に漏洩を無くする
ことができ、公害発生の危険を除去でき、更にそのよう
な大気／低圧継手の保守も容易である。As mentioned above in the state of the art, the problem often arises that the high-pressure fitting 23 does not perform a precise sealing, but in the present invention this means that the low-pressure chamber 24 does not cause any pollution of the lost fluid. It is of little concern as it is easily recovered in (which is of decisive value in all oil fields). As far as low-pressure fittings are concerned, current technology is easy to eliminate leaks, eliminates the risk of pollution, and is also easy to maintain for such atmosphere / low-pressure fittings.
【００２９】入口管２６／低圧室２４／高圧室１９／高
圧室１３／放出管２０の順序の流体循環は流体力学的な
観点から特に理想的である。特に流体はその流れ方向を
極端に変化させる必要がない。これは明らかに特に粘性
流体および大きな流量に伴って生ずるキャビテーション
並びに摩耗過程を減少する。The fluid circulation in the order of inlet pipe 26 / low pressure chamber 24 / high pressure chamber 19 / high pressure chamber 13 / discharge pipe 20 is particularly ideal from a hydrodynamic point of view. In particular, the fluid does not need to change its flow direction extremely. This obviously reduces the cavitation and wear processes that occur especially with viscous fluids and high flow rates.
【００３０】ピストン１６によって引き起こされる慣性
力は非常に有効な時点で正確に入口弁１５の開閉と共働
する。これは有利に容積効率を高い値に維持し、キャビ
テーションを避けるという利点を生ずる。The inertial force caused by the piston 16 exactly cooperates with the opening and closing of the inlet valve 15 at very effective times. This advantageously keeps the volumetric efficiency high and avoids cavitation.
【００３１】更に、軸線に関して対称な高圧要素構造は
応力集中過程を低下し、質量の低下および重量の低下を
可能とし、これは考慮される工業における別の重要なパ
ラメータである。Furthermore, the high-pressure element structure, which is symmetrical about the axis, reduces the stress concentration process and allows a reduction in mass and weight, which is another important parameter in the industry under consideration.
【００３２】明らかに１本あるいは複数の出口管２６が
存在し、これは環状の噴出部あるいは多点噴出部並びに
適当な形状の一つあるいは複数の開口１８を持った管を
含んでいる。Clearly there is one or more outlet tubes 26, which include annular or multipoint jets as well as tubes with one or more openings 18 of suitable shape.
【００３３】ピストン１６の数は特に今まで三ピストン
形ポンプが利用されているけれども重要なことではな
い。The number of pistons 16 is not particularly important, although three piston type pumps have been used up to now.
【００３４】これは特にすべての工業におけるすべての
高圧ポンプに適用できる。This applies in particular to all high-pressure pumps in all industries.
【００３５】[0035]
【発明の効果】本発明によれば軽量で容積効率の高いポ
ンプが得られる。According to the present invention, a lightweight pump having high volume efficiency can be obtained.
【図１】従来における「インライン」流体端の断面図。FIG. 1 is a cross-sectional view of a conventional “in-line” fluid end.
【図２】本発明に基づく「インライン」流体端の断面
図。FIG. 2 is a cross-sectional view of an “in-line” fluid end according to the present invention.
１３ 高圧室 １４ 出口弁 １５ 入口弁 １６ ピストン １７ ピストン延長部（中空） １８ 開口 １９ 高圧室 ２０ 放出管 ２４ 低圧室 ２６ 入口管 13 High Pressure Chamber 14 Outlet Valve 15 Inlet Valve 16 Piston 17 Piston Extension (Hollow) 18 Opening 19 High Pressure Chamber 20 Discharge Pipe 24 Low Pressure Chamber 26 Inlet Pipe
Claims (3)
空となっており室（１９）を形成し、この室（１９）が
一方では室（１９）の壁（１７）に形成されている一つ
あるいは複数の開口（１８）を通して流体入口管（２
６）に連通し、他方では各ピストン（１６）の高圧室
（１３）に入口弁（１５）の助けによって連通し、入口
弁（１５）はピストン（１６）が高圧室（１３）から戻
るときに開いて入口管（２６）と室（１９）を高圧室
（１３）に連通し、ピストン（１６）が高圧室（１３）
の中に入り込むときに閉じて室（１９）を密閉し、出口
弁（１４）によって制御して放出管（２０）を通して流
体を噴出することを特徴とする「インライン」と呼ばれ
る流体端部を有するポンプ。1. The free end (17) of each piston (16) is hollow to form a chamber (19), which on the one hand is formed in the wall (17) of the chamber (19). Fluid inlet tube (2) through one or more openings (18)
6) and, on the other hand, to the high pressure chamber (13) of each piston (16) with the help of an inlet valve (15), the inlet valve (15) when the piston (16) returns from the high pressure chamber (13). Open to open the inlet pipe (26) and the chamber (19) to the high pressure chamber (13), and the piston (16) to the high pressure chamber (13).
Has a fluid end called "in-line" characterized by closing on entry into the chamber to seal the chamber (19) and ejecting fluid through the discharge pipe (20) controlled by the outlet valve (14) pump.
数の開口（１８）、流体入口管（２６）および一つある
いは複数の開口（１８）が連通する低圧室（２４）を通
して流入することを特徴とする請求項１記載のポンプ。2. Fluid through a low pressure chamber (24) communicating with one or more openings (18), a fluid inlet pipe (26) and one or more openings (18) into the chamber (19). The pump according to claim 1, which flows in.
業に利用されることを特徴とする請求項１又は２記載の
ポンプ。3. The pump according to claim 1, which is used in petroleum-related industries, industrial cleaning industries and civil engineering industries.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR9209022 | 1992-07-20 | ||
| FR9209022A FR2693771B1 (en) | 1992-07-20 | 1992-07-20 | Pump comprising a partially hollow piston, and its applications in particular in the petroleum industry. |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06167277A true JPH06167277A (en) | 1994-06-14 |
Family
ID=9432125
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5178299A Pending JPH06167277A (en) | 1992-07-20 | 1993-07-19 | Pump with partially hollow piston |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0580196B1 (en) |
| JP (1) | JPH06167277A (en) |
| CA (1) | CA2100837A1 (en) |
| DE (1) | DE69304002T2 (en) |
| FR (1) | FR2693771B1 (en) |
| NO (1) | NO306223B1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006329007A (en) * | 2005-05-24 | 2006-12-07 | Meika Ryu | Current control reciprocating fluid pressure feeding unit |
| JP2009082867A (en) * | 2007-10-02 | 2009-04-23 | Takubo Engineering Co Ltd | Coating supply syringe |
| CN102777373A (en) * | 2012-07-10 | 2012-11-14 | 镇江长城注浆设备有限公司 | Double-liquid synchronous grouting pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR599965A (en) * | 1925-06-20 | 1926-01-27 | C I Ingg Audoli Bertola Ab | Low flow pump for domestic installations |
| CH257522A (en) * | 1943-12-27 | 1948-10-15 | Anonyme Messier Societe | Hydraulic pump. |
| GB672173A (en) * | 1949-08-06 | 1952-05-14 | Siam | Improvements in or relating to reciprocating pumps |
-
1992
- 1992-07-20 FR FR9209022A patent/FR2693771B1/en not_active Expired - Fee Related
-
1993
- 1993-06-18 DE DE69304002T patent/DE69304002T2/en not_active Expired - Fee Related
- 1993-06-18 EP EP93201766A patent/EP0580196B1/en not_active Expired - Lifetime
- 1993-07-19 CA CA002100837A patent/CA2100837A1/en not_active Abandoned
- 1993-07-19 JP JP5178299A patent/JPH06167277A/en active Pending
- 1993-07-19 NO NO932609A patent/NO306223B1/en not_active IP Right Cessation
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006329007A (en) * | 2005-05-24 | 2006-12-07 | Meika Ryu | Current control reciprocating fluid pressure feeding unit |
| JP2009082867A (en) * | 2007-10-02 | 2009-04-23 | Takubo Engineering Co Ltd | Coating supply syringe |
| CN102777373A (en) * | 2012-07-10 | 2012-11-14 | 镇江长城注浆设备有限公司 | Double-liquid synchronous grouting pump |
| US20230075447A1 (en) * | 2019-05-02 | 2023-03-09 | Kerr Machine Co. | Fracturing pump with in-line fluid end |
| US20230193884A1 (en) * | 2019-05-02 | 2023-06-22 | Kerr Machine Co. | Fracturing pump with in-line fluid end |
| US11952986B2 (en) * | 2019-05-02 | 2024-04-09 | Kerr Machine Co. | Fracturing pump arrangement using a plunger with an internal fluid passage |
| US11952990B2 (en) * | 2019-05-02 | 2024-04-09 | Kerr Machine Co. | Fracturing pump arrangement using a plunger with an internal fluid passage |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2693771A1 (en) | 1994-01-21 |
| DE69304002T2 (en) | 1997-03-13 |
| NO932609D0 (en) | 1993-07-19 |
| DE69304002D1 (en) | 1996-09-19 |
| FR2693771B1 (en) | 1994-09-23 |
| NO932609L (en) | 1994-01-21 |
| CA2100837A1 (en) | 1994-01-21 |
| EP0580196B1 (en) | 1996-08-14 |
| EP0580196A1 (en) | 1994-01-26 |
| NO306223B1 (en) | 1999-10-04 |
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