JPS60198397A - Spiral jet pump - Google Patents
Spiral jet pumpInfo
- Publication number
- JPS60198397A JPS60198397A JP5545584A JP5545584A JPS60198397A JP S60198397 A JPS60198397 A JP S60198397A JP 5545584 A JP5545584 A JP 5545584A JP 5545584 A JP5545584 A JP 5545584A JP S60198397 A JPS60198397 A JP S60198397A
- Authority
- JP
- Japan
- Prior art keywords
- pump
- throat section
- nozzle
- head
- venturi pipe
- 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
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
（イ） 産業上の利用分野
この発明は、渦巻ポンプとこの渦巻ポンプの吸込側にジ
ェットポンプを設けてなる渦巻ジェットポンプに関する
。DETAILED DESCRIPTION OF THE INVENTION (A) Field of Industrial Application This invention relates to a centrifugal pump and a centrifugal jet pump having a jet pump provided on the suction side of the centrifugal pump.
（ロ）従来技術
従来の渦巻ジェットポンプでは、第１図及び第２図に示
す様に、渦巻ポンプ（１）の吸込側にジェットポンプ（
２）を設け、両ポンプ（１）（２）による揚水を圧力タ
ンク（３）及び水栓（４）を経て吐出させており、具体
的には、渦巻ポンプ（１）のモータ（５〉によりインペ
ラ（６）を回転して揚水し、この揚水を、ガイドベーン
（７〉を経てケーシング（８）内に放出し更に吐出側調
整弁（９）をそのスプリング力に抗して押開いて吐出側
（１０）に吐出しその後前記圧力タンク（３）及び水栓
（４）を経て吐出している。また、前記インペラ（６）
からケーシング（８）内に放出きれた水の一部は、圧力
水口（１１）から循環水路（１２）を経てジＪ、ットボ
ンブ（２）の７′スル（１３）内に帰還して高速噴流と
なりベンチより一管（１４）内を流れその際にベンチュ
リー管（１４〉の流入口近傍で負圧を発生しこの負圧に
より吸込側の流体を揚水してインペラ（６）に送り込む
様に機能する。以−Ｆの動作をくり返ず従来の渦巻ジェ
ットポンプでは、高揚程の場合に吐出側調整弁（９〉を
調整ネジ（９ａ）により閉成方向に締め付けているが、
低揚程大水量の場合にもこの調整弁（９）の開成抵抗に
より水の一部が不必要に押戻きれて圧力水口（１１）及
び循環水路＜１２）を経てシェツトポンプ（２）に循環
するためその循環水の分たけモータ（５）の消費電力が
増大して効率が低下する不都合がある。(B) Prior Art In a conventional volute jet pump, as shown in Figs. 1 and 2, a jet pump (
2), and the water pumped by both pumps (1) and (2) is discharged through the pressure tank (3) and water faucet (4). Specifically, the motor (5> of the centrifugal pump (1) The impeller (6) is rotated to pump up water, and this pumped water is discharged into the casing (8) through the guide vane (7>), and then the discharge side adjustment valve (9) is pushed open against its spring force to be discharged. It is discharged to the side (10) and then discharged through the pressure tank (3) and the water tap (4).Also, the impeller (6)
A part of the water discharged into the casing (8) from the pressure water port (11) passes through the circulation channel (12) and returns to the 7' hole (13) of the bomb (2) where it is formed into a high-speed jet. The fluid flows from the bench through the pipe (14), which generates negative pressure near the inlet of the Venturi pipe (14), which functions to lift the fluid on the suction side and send it to the impeller (6). In a conventional centrifugal jet pump, the discharge side regulating valve (9) is tightened in the closing direction with the regulating screw (9a) when the head is high.
Even in the case of a large amount of water with a low head, a part of the water is pushed back unnecessarily due to the opening resistance of this regulating valve (9) and circulates to the shed pump (2) via the pressure water port (11) and the circulation channel <12). Therefore, there is an inconvenience that the power consumption of the circulating water dividing motor (5) increases and the efficiency decreases.
この不都合を解消するために、従来の渦巻ジェットポン
プでは、第３図及び第４図に示す様に、へ〉′チュリー
管り１５）に一体に、ノズル制限弁（１６〉を設け（特
公昭５４−１８７６２号公報参照）、高揚程運転時には
第３図に示す様に圧縮スブリ〉・グ（１７）によりヘン
グーユリ−管（１５）及びノズル制限弁（１６）を押圧
してノズル（１３）の開成位置に変位せしめて通常のシ
エント作用を生じさけ、一方、低揚程大水量時には第４
図に示す様にインペラ〈６）の吸込側直前の真空度がベ
ンチュリー管（１５〉の吸込側より大きくなるためこの
差圧によりベンチュリー管（１５）が圧縮スプリング（
１７）に抗し１渦巻ポンプく１）側に移動し、これに伴
なってノズル制限弁（１６）もノズル（１３〉の開成位
置に変位して循環水を阻止して効率の低下を防止してい
る。In order to eliminate this inconvenience, in conventional centrifugal jet pumps, as shown in Figs. 54-18762), during high-head operation, as shown in Figure 3, the compressor valve (17) presses the hengyu lily tube (15) and the nozzle restriction valve (16) to close the nozzle (13). The 4th position is moved to the open position to avoid normal sient action, while the 4th
As shown in the figure, the degree of vacuum immediately before the suction side of the impeller (6) is greater than the suction side of the Venturi tube (15), so this differential pressure causes the Venturi tube (15) to compress the compression spring (
17), the nozzle restriction valve (16) also moves to the open position of the nozzle (13), blocking the circulating water and preventing a drop in efficiency. are doing.
しかしながら、前述の渦巻ジェットポンプでは、低揚程
大水量時の効率の損失を少なくすることはできるが、ジ
ェット水流がベンチュリー管（１５）のスロート部（１
５ａ）で規制されてしまうため、高揚程運転時の揚程ア
ップ及び低揚程運転時の水量アップは望めないと云う欠
点があった。However, in the above-mentioned centrifugal jet pump, although it is possible to reduce the loss of efficiency when the head is low and the amount of water is large, the jet water flow is
Since it is regulated by 5a), there is a drawback that it is not possible to increase the head during high head operation or increase the amount of water during low head operation.
（ハ） 発明の目的
この発明は斯る点に鑑み、高揚程運転時には更に揚程を
アップでき又低揚程運転時には水量をアップできる渦巻
シェツトポンプを提供するものである。(c) Purpose of the Invention In view of the above, the present invention provides a centrifugal shet pump that can further increase the head during high head operation and increase the amount of water during low head operation.
（ニ）発明の構成
この発明は、渦巻ポンプとこの渦巻ポンプの吸込側にジ
ェットポンプを設け、渦巻ポンプの吐出側とジェットポ
ンプのノスル内を循環水路で連通ずると共に、前記ノズ
ルに対向するベンチュリー管をその吐出側と吸込側の圧
力差により摺動可能に設け、前記ベンチュリー管に連動
するノズル制限弁を前記ノズルに挿入したものに於て、
前記ジェットポンプのベンチュリー管のスロート部を弾
性素材で形成すると共に、前記スロート部の周囲に、前
記循環水路に連通ずる圧力室を設けたものである。(d) Structure of the Invention This invention provides a swirl pump and a jet pump on the suction side of the swirl pump, and communicates the discharge side of the swirl pump with the inside of the nozzle of the jet pump through a circulation waterway, and a venturi facing the nozzle. A pipe is provided to be slidable due to the pressure difference between its discharge side and suction side, and a nozzle restriction valve interlocked with the venturi pipe is inserted into the nozzle,
The throat portion of the venturi tube of the jet pump is formed of an elastic material, and a pressure chamber communicating with the circulation waterway is provided around the throat portion.
くホ〉 実施例
以下この発明の−・実施例を、第５図及び第６図を参照
してその要部についてだけ説明し、特に説Ｌｕ１ｌしな
いその他の部分については前述の従来例と同様に構成さ
れ、同一番号を付してその説明を省略する。〉Example: Hereinafter, only the main parts of the embodiment of the present invention will be explained with reference to FIGS. They are designated by the same numbers and their explanations will be omitted.
この実施例では、ベンチュリー管（１８）のスロート部
（１９〉を合成ゴム等の弾性素材で形成すると共に、前
記スロート部（１９〉の周囲に、循環水路（１２）に連
通ずる圧力室（２０）を設けている。スロート部（１９
）は、その吸込側縁部（１９ａ）でスペーサ（２１）に
てシェツトケース（２２）に抑圧固定され、持続側縁部
（１９ｂ）でへンチュリー管吐出側部（２３）に嵌着し
ている。このベンチュリー管（１８）は、支持リング（
２４）と縁部（２５）の間に介在する圧縮スプリング（
２６）により、ベンチュリー管の吸込側方向に付勢され
ている。ベンチュリー管（１８）の吐出側部＜２３）に
は１、取付具（２７）によりノ、スル（１３）の制限弁
（１６〉が取付けられている。前記圧力室＜２０〉は、
連通孔（２８）を介して循環水路〈１２）に連通し、か
つ、スロート部（１９）の１状突起（１９ｃ）でシール
されている。In this embodiment, the throat part (19> of the Venturi tube (18) is formed of an elastic material such as synthetic rubber, and a pressure chamber (20 ) is provided.The throat part (19
) is pressed and fixed to the shed case (22) by a spacer (21) at its suction side edge (19a), and fitted into the Henture tube discharge side (23) at its sustaining side edge (19b). . This Venturi tube (18) has a support ring (
A compression spring (24) interposed between the edge (25)
26), the Venturi tube is biased toward the suction side. A restriction valve (16) of the through (13) is attached to the discharge side (23) of the Venturi pipe (18) by a fitting (27).The pressure chamber (20)
It communicates with the circulation waterway (12) through the communication hole (28) and is sealed by the uniform protrusion (19c) of the throat part (19).
次に前記ポンプの動作について説明する。Next, the operation of the pump will be explained.
高揚程運転時には、吐出側調整弁（９）の調整ネジ（９
ａ）を締付は方向に調整する。すると前記ポンプでは、
第５図に示す様に、循環水量が増大して、循環水路（１
２）が高圧となり、連通孔（２８〉を介じで圧力室（２
０）も高圧となり、弾性素ネ（のス１１−ト部（１９〉
の径が非付勢状態の値（Ｄ）から（Ｄｌ）に縮小する。During high-pressure operation, tighten the adjustment screw (9) of the discharge side adjustment valve (9).
a) Adjust the tightening in the direction. Then, in the pump,
As shown in Figure 5, the amount of circulating water increases and the circulation channel (1
2) becomes high pressure, and the pressure chamber (2) becomes high pressure through the communication hole (28>).
0) also becomes high pressure, and the start part (19) of the elastic element (
The diameter of is reduced from the value (D) in the non-energized state to (Dl).
スロート部（１９）が縮径するため前記ポンプでは、ジ
ェット機能が一段と高まり、その強力な吸引力により揚
程がアップする。Since the diameter of the throat portion (19) is reduced, the jet function of the pump is further enhanced, and its powerful suction force increases the pump head.
また、低揚程大水量運転時には、前記ポンプでは、吐出
側調整力（９）の調整ネジ（９ａ）を緩める方向に調整
する。すると前記ポンプでは、第６図に示す様に、渦巻
ポンプ（１〉の吸込側に負圧を発生し、との負圧により
ベンチュリー管吐出側部（２３〉が渦巻ポンプ（１）側
に移動し、これにより、ノズル（１３〉は制限弁（１６
）で閉本され、スロート部（１９）も引張されその径が
（Ｄ２）の値に拡大する。そのため前記ポンプでは、不
要な循環水流が阻止され運転効率がアップすると共に、
スロート径の拡大分たけ吐出水量がアップする。Furthermore, during low lift and high water flow operation, the pump is adjusted in the direction of loosening the adjustment screw (9a) of the discharge side adjustment force (9). Then, in the pump, as shown in Fig. 6, negative pressure is generated on the suction side of the centrifugal pump (1), and due to the negative pressure, the venturi tube discharge side (23) moves toward the centrifugal pump (1). As a result, the nozzle (13) is connected to the restriction valve (16).
), the throat portion (19) is also pulled and its diameter expands to the value (D2). Therefore, in the pump, unnecessary circulating water flow is prevented, operational efficiency is increased, and
The amount of water discharged increases as the throat diameter increases.
第７図に、その横軸及び縦軸に夫々流量（Ｑ）及び揚程
（Ｈ）、効率（１，）をとって示す様に、前記ポンプに
よれは、従来例に比較して、Ｑ−Ｈ特性及びＱ−ｚ、特
性が夫々実線で示す状態から点線でポリ−状態に改曽す
る二とが実験で確認され又いる。As shown in FIG. 7, with the flow rate (Q), head (H), and efficiency (1,) plotted on the horizontal and vertical axes, respectively, the pump has a Q- It has been experimentally confirmed that the H characteristic and the Q-z characteristic change from the state shown by the solid line to the poly state shown by the dotted line.
くべ〉 発明の効果
この発明は以−ヒの様に構成したから、高揚程運転時に
は圧力室が高圧となり、弾性素材のスロート部か周囲か
ら締め（ｔ ｌ′Ｊられて縮径し、ジェット機能が一段
と高まり、揚程を更にアップでき、また低揚程大水量運
転時には渦巻ポンプの吸込側の負圧によりベンチュリー
管が引かれ、弾性素材のスロート部も引かれてその径が
拡大し拡大分だけ吐出水量をアップでき、従って広い制
御範囲にわたって高効率なポンプを提供できる。Effects of the Invention Since this invention is constructed as described below, during high-head operation, the pressure chamber becomes high pressure, and the throat portion of the elastic material is tightened (tl'J) from the periphery to reduce its diameter, and the jet function is activated. This further increases the pump head and further increases the pump head.Also, during low lift and high water flow operation, the negative pressure on the suction side of the centrifugal pump pulls the Venturi tube, which also pulls the throat section made of elastic material, expanding its diameter and discharging the expanded amount. The amount of water can be increased, thus providing a highly efficient pump over a wide control range.
第１図及び第２図は従来のポンプを示し、第１図は概略
的構成図、第２図は一部の拡大断面図、第３図及び第４
図は従来の可動ヘンチュリータイプのポンプを示し、第
３図は高揚程時の断面図、第４図は低揚程時の断面図、
第５図及び第６図はこの発明の一実施例を示し、第５図
は高揚程時の断面図、第６図は低揚程時の断面図、第７
図は従来例と比較して示す本発明一実施例のポンプ性能
特性図である。
（１）・・・渦巻ポンプ、（２）・・ ジェットポンプ
、（１２）・・・循環水路、（１３）・ ノズル、（１
６）・・ノズル制限弁、（１８）・・・ベンチュリー管
、（１９）・・・スロート部、（２０）・・・圧力室。
出願人 三洋電機株式会社
代理人 弁理士 佐野静夫
第１囚
第８図Figures 1 and 2 show conventional pumps, with Figure 1 being a schematic configuration diagram, Figure 2 being a partially enlarged sectional view, and Figures 3 and 4.
The figure shows a conventional movable Henturi type pump, Fig. 3 is a sectional view at high head, Fig. 4 is a sectional view at low head,
5 and 6 show an embodiment of the present invention, FIG. 5 is a sectional view at high head, FIG. 6 is a sectional view at low head, and FIG. 7 is a sectional view at low head.
The figure is a diagram showing pump performance characteristics of an embodiment of the present invention in comparison with a conventional example. (1)...Spiral pump, (2)...Jet pump, (12)...Circulation waterway, (13)・Nozzle, (1
6)...Nozzle restriction valve, (18)...Venturi tube, (19)...throat portion, (20)...pressure chamber. Applicant Sanyo Electric Co., Ltd. Agent Patent Attorney Shizuo Sano Prisoner 1 Figure 8
Claims (1)
ンプを設け、渦巻ポンプの吐出側とジェットポンプのノ
ズル内を循環水路で連通ずると共に、前記ノズルに対向
するベンチュリー管をその吐出側と吸込側の圧力差によ
り摺動可能に設け、前記べ〉・チュリー管に連動するノ
ズル制限弁を前記ノズルに挿入したものに於て、前記ジ
ェットポンプのベンチュリー管のスロート部を弾性素材
で形成すると共に、ｌ￥ｉＩ記スロート部の周囲に、前
記循環水路に連通する圧力室を設けたことを特徴とする
渦巻シェツトポンプ。l) A whirlpool pump and a jet pump are provided on the suction side of the whirlpool pump, and the discharge side of the whirlpool pump and the inside of the nozzle of the jet pump are communicated through a circulation waterway, and a Venturi tube facing the nozzle is connected between the discharge side and the suction side. A nozzle restriction valve is inserted into the nozzle so as to be slidable due to a pressure difference between the venturi pipe and the venturi pipe, and the throat part of the venturi pipe of the jet pump is formed of an elastic material; A spiral shet pump characterized in that a pressure chamber communicating with the circulation waterway is provided around the throat portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5545584A JPS60198397A (en) | 1984-03-22 | 1984-03-22 | Spiral jet pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5545584A JPS60198397A (en) | 1984-03-22 | 1984-03-22 | Spiral jet pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60198397A true JPS60198397A (en) | 1985-10-07 |
Family
ID=12999076
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5545584A Pending JPS60198397A (en) | 1984-03-22 | 1984-03-22 | Spiral jet pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60198397A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005240624A (en) * | 2004-02-25 | 2005-09-08 | Matsushita Electric Ind Co Ltd | Self-priming pump |
| CN106351848A (en) * | 2016-10-21 | 2017-01-25 | 杭州激湍流体科技有限公司 | Low-noise injection pump |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5418762A (en) * | 1977-06-24 | 1979-02-13 | Unisearch Ltd | Radiation convergence and divergence device |
-
1984
- 1984-03-22 JP JP5545584A patent/JPS60198397A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5418762A (en) * | 1977-06-24 | 1979-02-13 | Unisearch Ltd | Radiation convergence and divergence device |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005240624A (en) * | 2004-02-25 | 2005-09-08 | Matsushita Electric Ind Co Ltd | Self-priming pump |
| CN106351848A (en) * | 2016-10-21 | 2017-01-25 | 杭州激湍流体科技有限公司 | Low-noise injection pump |
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