JPH0431660A - Circumferential flow type liquid pump - Google Patents
Circumferential flow type liquid pumpInfo
- Publication number
- JPH0431660A JPH0431660A JP13667290A JP13667290A JPH0431660A JP H0431660 A JPH0431660 A JP H0431660A JP 13667290 A JP13667290 A JP 13667290A JP 13667290 A JP13667290 A JP 13667290A JP H0431660 A JPH0431660 A JP H0431660A
- Authority
- JP
- Japan
- Prior art keywords
- pump
- impeller
- channel
- flow path
- vent hole
- 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.)
- Granted
Links
- 239000007788 liquid Substances 0.000 title claims abstract description 35
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 239000000446 fuel Substances 0.000 abstract description 15
- 238000005192 partition Methods 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 32
- 239000012530 fluid Substances 0.000 description 6
- 239000003502 gasoline Substances 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、車両用内燃機関において例えば燃料タンク
よりガソリンのような液体燃料を汲み上げる燃料ポンプ
として用いられる円周流式液体ホ゛ンプの、特にポンプ
内に発生する気泡などによるポンプ性能低下を軽減する
構造に関するものであるＯ
〔従来の技術〕
第３図は例えは特開昭６０−’７９１９３号公報に示さ
れたような従来の円周流式液体ポンプを示す断面図、第
４図は第３図の線■−ｍＶに沿うポンプ組立体部の縦断
面図、第５図は第４図の線ｖ−ｖｉｃ沿う横断面図であ
る０
図において、（１）はポンプ組立体であシ、該組立体は
ポンプケーシング（２）とポンプカバー（３）トにより
構成されているｏ（４）はインペラであり、外周縁部に
対称に羽根溝部（５）が設けられており、ポンプ組立体
（１）内に軸（６）によってポンプ組立体（１）に対し
て自身の中心軸線の周りに回転可能に支持されている０
ポンプ組立体（１）はインペラ（４）の外周縁部に沿っ
て延在する円弧帯状のポンプ流路（７）及び該ポンプ流
路の両端部に開口する吸入口（８）と吐出口（９）とを
郭定し、ポンプ流路（７）にインペラ（４）の羽根溝部
（５）を受は入れている。羽根溝部（５）はポンプケー
シング（２）およびポンプカバー（３）Ｋそれぞれ対向
スる同じ深さの羽根溝（５ａ）でＬｌ−Ｌ２に形成され
ている。Detailed Description of the Invention [Field of Industrial Application] The present invention relates to a circumferential flow liquid pump used as a fuel pump for pumping liquid fuel such as gasoline from a fuel tank in a vehicle internal combustion engine, and particularly to a pump. [Prior art] Figure 3 is an example of a conventional circumferential flow system as shown in Japanese Patent Application Laid-Open No. 1987-79193. Figure 4 is a longitudinal cross-sectional view of the pump assembly section taken along the line - mV in Figure 3, and Figure 5 is a cross-sectional view taken along the line v-vic in Figure 4. In the figure, (1) is a pump assembly, which is composed of a pump casing (2) and a pump cover (3), and o (4) is an impeller, which is symmetrically arranged around the outer periphery. A vane groove (5) is provided, and the vane is rotatably supported in the pump assembly (1) by a shaft (6) about its own central axis relative to the pump assembly (1).
The pump assembly (1) includes an arc belt-shaped pump channel (7) extending along the outer peripheral edge of the impeller (4), and an inlet port (8) and a discharge port (8) that are open at both ends of the pump channel. 9), and the blade groove (5) of the impeller (4) is inserted into the pump channel (7). The blade groove portion (5) is formed in Ll-L2 with blade grooves (5a) having the same depth and facing each other in the pump casing (2) and the pump cover (3) K.
ポンプ流路（７）はポンプケーシング（２）およびポン
プカバー（３）に設けられた同じ深さの凹部（マＣ）に
よ抄Ｌ３−ＩＪ４に構成され、ポンプ流路（７）の吸入
口（８）側に拡大流路（７＆）が吸入口（８）から始ま
って所定長を有する円弧状に形成されている。該拡大流
路（γａ）はポンプ流路（７）の他の部分よりポンプ流
路断面積が大きく形成され、該拡大流路（ハ）の終端で
ある反吸入口側に流路断面積を縮小する段差部（７ｂ）
が設けられている。The pump flow path (7) is configured by a concave portion (maC) of the same depth provided in the pump casing (2) and pump cover (3) to form L3-IJ4, and the suction port of the pump flow path (7) On the (8) side, an enlarged flow path (7&) is formed in an arc shape having a predetermined length starting from the suction port (8). The expanded flow path (γa) is formed to have a larger cross-sectional area than other parts of the pump flow path (7), and the cross-sectional area of the expanded flow path (γa) is larger on the side opposite to the suction port, which is the end of the expanded flow path (c). Shrinking step part (7b)
is provided.
この段差部（ツｂ）から吐出口（９）にわたって拡大流
路（７＆）よりもポンプ流路断面積が小さいポンプ流路
（７）の高圧部分が設けられている。拡大流路（）１）
の終端部に段差部（７ｂ）に隣接してポンプ流路（７）
とポンプ組立体（１）外とを連通ずる小孔状の気体抜き
孔Ｏがポンプカバー（３）側の凹部（’Ｆｏ ）Ｉｃ設
けられている。A high-pressure portion of the pump flow path (7) having a smaller cross-sectional area of the pump flow path than the enlarged flow path (7&) is provided extending from the step portion (b) to the discharge port (9). Expanded channel ()1)
A pump flow path (7) adjacent to the stepped portion (7b) at the terminal end of the
A small gas vent hole O communicating between the pump assembly (1) and the outside of the pump assembly (1) is provided in the recess ('Fo) Ic on the pump cover (3) side.
語は電動機であり、ポンプ組立体（１）と互いに連結さ
れておシ、電動機部の回転子（至）の軸（６）はその両
端部を軸受的と［相］とによって回転可能に支持され、
インペラ（４）を回転させる。α９はエンドカバーであ
り、エンジン等（図示せず）に給送するだめのポンプ吐
出口（１９ａ）が設けられている０ωはヨークであり、
内部に回転子（至）を収容し且つポンプ組立体（１）と
エンドカバーαｇとの間に吐出口（９）より吐出される
例えはガソリンのような液体燃料を貯容する液体室匹を
郭定し、内部に固定子として作用する永久磁石＠、回転
子苗の整流子□□□に摺接する給電用ブラシ勿とを有し
ている。The term refers to an electric motor, which is connected to the pump assembly (1), and the shaft (6) of the rotor (to) of the electric motor section is rotatably supported at both ends by bearings and [phases]. is,
Rotate the impeller (4). α9 is an end cover, and 0ω is a yoke provided with a pump discharge port (19a) for feeding to an engine etc. (not shown).
A liquid chamber housing a rotor therein and storing a liquid fuel such as gasoline, which is discharged from a discharge port (9) between the pump assembly (1) and the end cover αg, is defined. It has a permanent magnet inside that acts as a stator, and a power supply brush plate that slides into contact with the commutator of the rotor.
次に動作について説明する。上記のように構成された円
周流式液体ポンプにおいて、電動機部によってインペラ
（４）が第３図で見て時計廻り方向に駆動回転されるこ
とにより吸入口（８）より液体燃料がポンプ流路（７）
の拡大流路（７ａ）Ｋｇ＆人される０液体燃料はポンプ
流路（７）内のインペラ（４）の羽根溝部（５）が高速
で回転することにより生じる流体摩擦抵抗により昇圧さ
れ、ポンプ流路（７）を第４図で見て時計筒υ方回へ流
れて吐出口（９）より液体室０へ流出され、吐出口を通
じてエンジン等（図示せず）に給送される。Next, the operation will be explained. In the circumferential flow type liquid pump configured as described above, the impeller (4) is driven and rotated by the electric motor in the clockwise direction as seen in FIG. Road (7)
The liquid fuel in the enlarged flow path (7a) is increased in pressure by the fluid frictional resistance caused by the high speed rotation of the blade groove (5) of the impeller (4) in the pump flow path (7), and the pump flow is increased. As seen in FIG. 4, the liquid flows through the passage (7) in the direction of the clock cylinder υ, flows out from the discharge port (9) into the liquid chamber 0, and is fed to an engine, etc. (not shown) through the discharge port.
従来の円周流式液体ポンプは、上記中にポンプ流路（７
）内のインペラ（４）の羽根溝部（５）と液体との接触
面で発生する燃料蒸気による気泡がポンプ流路（７）に
溜ると、いわゆるベーパロックが生じ、液体燃料の流れ
が阻害され、ポンプ性能が著しく低下する恐れがある０
そのため燃料蒸気による気泡を拡大流路（７ａ）内の段
差部（７ｂ）に隣接して設けられた気体抜き孔［相］に
よりボンブ組立体（１）外へ排出されるようになってい
る。しかしながら、従来の円周流式液体ポンプはポンプ
組立体（１）外へ連通せしめる気体抜き孔Ｏがポンプ流
路（７）の拡大流路（）ａ）終端部の一方の凹部（７ｃ
）に設けられているため、気体抜き孔りの設けられてい
ない側の凹部（）Ｃ）ではポンプ流路（７）内のインペ
ラ（４）の羽根溝部（５）と液体との接触面で発生した
気泡は遠心力と液体との比重差によりポンプ流路（７）
の内周部のインペラ（４）近傍に集まって流れ、ますま
す流体摩擦抵抗が小さくなってしまう。従って、ポンプ
流路（７）の底面部近傍に存在する気泡および気体をポ
ンプ組立体（１）外へ充分排出することができなくなり
、ベーノくロックが発生する恐れがあるという課題があ
った。A conventional circumferential flow liquid pump has a pump flow path (7
) When bubbles due to fuel vapor generated at the contact surface between the impeller (4) in the impeller (4) and the liquid contact surface accumulate in the pump channel (7), a so-called vapor lock occurs, and the flow of liquid fuel is obstructed. There is a risk that the pump performance will be significantly reduced. Therefore, the air bubbles caused by fuel vapor are expanded and removed from the bomb assembly (1) by the gas vent hole [phase] provided adjacent to the stepped portion (7b) in the flow path (7a). It is designed to be discharged to However, in conventional circumferential flow liquid pumps, the gas vent O that communicates with the outside of the pump assembly (1) is located in one recess (7c) at the end of the enlarged flow path (a) of the pump flow path (7).
), the concave part ()C) on the side where the gas vent hole is not provided is the contact surface between the blade groove part (5) of the impeller (4) in the pump channel (7) and the liquid. The generated bubbles flow through the pump flow path (7) due to centrifugal force and the difference in specific gravity of the liquid.
The fluid gathers near the impeller (4) on the inner periphery of the fluid, and the fluid friction resistance becomes smaller and smaller. Therefore, there is a problem in that the bubbles and gas existing near the bottom of the pump flow path (7) cannot be sufficiently discharged to the outside of the pump assembly (1), and there is a possibility that a valve lock may occur.
本発明は上記のような課題を解決するためになされたも
ので、ポンプ流路（７）内に発生した燃料蒸気による気
泡のような気体が確実にポンプ流路（７）よりポンプ組
立体（１）外へ排出されるよう構成されベーパロックが
発生しにくい円周流式液体ポンプを提供することを目的
としている０
〔課題を解決するための手段〕
本発明の請求項１に係る円周流式液体ポンプは、ポンプ
ケーシングおよびポンプカバーに設けられた凹部により
形成されたポンプ流路の吸入口側に設けられた拡大流路
と、ポンプ組立体外部へ連通する気体抜き孔を拡大流路
終端部の前記ポンプケーシング及びポンプカバーの双方
の凹部に設けたものである。The present invention has been made to solve the above-mentioned problems, and it ensures that gas such as bubbles due to fuel vapor generated in the pump flow path (7) is transferred from the pump flow path (7) to the pump assembly ( 1) The object is to provide a circumferential flow type liquid pump configured to discharge the liquid to the outside and hardly cause vapor lock. type liquid pump has an expanded flow path provided on the suction side of the pump flow path formed by a recess provided in the pump casing and pump cover, and a gas vent hole that communicates with the outside of the pump assembly at the end of the enlarged flow path. This is provided in the recessed portions of both the pump casing and the pump cover.
本発明の請求項２に係る円周流式液体ポンプは、ポンプ
ケーシングおよびポンプカバーに設けられた凹部により
形成されたポンプ流路の吸入口側に設けられた拡大流路
と、拡大流路終端部の前記ポンプケーシングまたはポン
プカバーのいずれか一方の凹部に設けられ該ポンプ組立
体外部へ連通する気体抜き孔とを備え、インペラの羽根
溝部に対向する流路凹部の深さが前記気体抜き孔が配設
された側の凹部の深さが他方より浅く、且つ前記気体抜
き孔が配設された側の四部に対抗する前記インペラの羽
根□溝部の溝深さも他方より浅く形成したものである。The circumferential flow liquid pump according to claim 2 of the present invention includes an expanded flow path provided on the suction port side of the pump flow path formed by the recess provided in the pump casing and the pump cover, and an enlarged flow path terminal end. a gas vent hole that is provided in a recess in either the pump casing or the pump cover and communicates with the outside of the pump assembly, and the depth of the flow path recess facing the impeller blade groove is equal to the gas vent hole. The depth of the concave portion on the side where the gas vent hole is provided is shallower than the other side, and the groove depth of the groove portion of the blade of the impeller opposing the four portions on the side where the gas vent hole is provided is also shallower than the other side. .
本発明の請求項１における円周流式液体ポンプは、拡大
流路終端部のポンプケーシングおよびポンプカバーの両
凹部に気体抜き孔を設けているので、気泡のような気体
を気体抜き孔からポンプ流路外へ確実に排出される０
本発明の請求項２における円周流式液体ポンプは、気体
抜き孔を設けている側の拡大流路の凹部を浅くシ、且つ
気体抜き孔が配設された側の凹部に対抗するインペラの
羽根溝部の溝深さも他方より浅く形成されているので、
拡大流路の気体抜き孔が配設された側はインペラの羽根
溝部で発生する流体摩擦力を凹部底部まで充分伝達でき
、気泡のような気体を気体抜き孔からポンプ流路外へ確
実に排出しインペラが常に液体燃料と接するのでｌ２１
作用を維持する。In the circumferential flow liquid pump according to claim 1 of the present invention, gas vent holes are provided in both the recesses of the pump casing and the pump cover at the end of the enlarged flow path, so that gas such as bubbles can be pumped from the gas vent hole. In the circumferential flow liquid pump according to claim 2 of the present invention, the concave portion of the enlarged flow path on the side where the gas vent hole is provided is made shallow, and the gas vent hole is provided. The groove depth of the impeller blade groove that opposes the recess on the side that has been removed is also shallower than the other side, so
The side of the enlarged flow path where the gas vent hole is installed can sufficiently transmit the fluid friction force generated in the impeller blade groove to the bottom of the recess, ensuring that gas such as bubbles is discharged from the gas vent hole to the outside of the pump flow path. Since the impeller is always in contact with liquid fuel, l21
maintain its action.
第１図は本発明の請求項１による円周流式液体ポンプの
一実施例を示すポンプ組立体部の横断面図、第２図は本
発明の請求項２による円周流式液体ポンプの他の実施例
を示すポンプ組立体部の横断面図であシ、第１図、第２
図とも従来例のポンプ組立体部の横断面図（第５図）に
相当する。FIG. 1 is a cross-sectional view of a pump assembly showing an embodiment of a circumferential flow liquid pump according to claim 1 of the present invention, and FIG. 2 is a cross-sectional view of a circumferential flow liquid pump according to claim 2 of the present invention. 1 and 2 are cross-sectional views of the pump assembly showing other embodiments.
Both figures correspond to a cross-sectional view (FIG. 5) of a conventional pump assembly.
第１１３１１：オイテ、（２） 〜（５） 、 （７）
、 （１３Ｆｉ上記従来例において説明し良ものと同
様である。α４は第２の気体抜き孔であり、ポンプケー
シング（２）側の拡大流路（）＆）終端部の凹部（７ｏ
）にあって、気体抜き孔りに対抗する位置に設けられ拡
大流路（７＆）終端部とポンプ組立体（１）外を連通し
ている。なお、上記以外の他の構成は従来技術と同一で
あるので説明を省略する。No. 11311: Oite, (2) ~ (5), (7)
, (13Fi is the same as the good one explained in the above conventional example. α4 is the second gas vent hole, and the concave part (7o
), it is provided at a position opposite to the gas vent hole and communicates the terminal end of the enlarged flow path (7&) with the outside of the pump assembly (1). Note that the other configurations other than those described above are the same as those of the prior art, so explanations will be omitted.
上記のように構成された円周流式液体ポンプにおいては
、ポンプケーシング（２）側およびポンプカバー（３）
側の両凹部（７ｃ）の燃料蒸気などの気泡のような気体
が気体抜き孔０および第２の気体抜き孔α４から排出さ
れるので、インペラ（４）は常に液体燃料と接しベーパ
ロックの発生が抑制されポンプ作用を維持することがで
きる。In the circumferential flow liquid pump configured as above, the pump casing (2) side and the pump cover (3)
Since bubble-like gas such as fuel vapor in both side recesses (7c) is discharged from the gas vent hole 0 and the second gas vent hole α4, the impeller (4) is always in contact with the liquid fuel and vapor lock is prevented from occurring. The pumping action can be maintained by being suppressed.
第２図において、（２）〜（４） 、 （７） ＄ ０
３は上記従来例において説明したものと同様である。ａ
Ｏはインペラ（４）の外周縁部に非対称に設けられた羽
根溝部であり、該羽根溝部αＧは一方の羽根溝部（１０
ａ）と他方の羽根溝部（ｍｏｂ ）の溝部の深さはそれ
ぞれＬ５、Ｌ６ であシＬ！１＞１１６に形成されてい
る０（）ｄ）はポンプ流路（７）の拡大流路（ツ１）を
形成する一方の凹部であり、ポンプケーシング（２）に
設けられておシ、その深さはＬ７である。（）・）はポ
ンプ流路（７）の拡大流路（７１）を形成する他方の凹
部でありポンプカバー（３）に設けられており、その深
さはＬ８であり、Ｉ、７＞Ｌ８に構成されている０
力お、上記以外の他の構成は従来技術と同一であるので
説明を省略する〇一般に、円周流式液体ポンプではポン
プ流路（７）の断面積が大きいと吐出量は多く、断面積
が小さいと吐出圧が高くなる０上述のような構成により
なる円周流式液体ポンプにおいては、電動模似によって
インペラ（４）が駆動回転されることにより吸入口（８
）より液体燃料がポンプ流路（７）の一端部に吸入され
、ポンプ流路（７）へ流れてその他端部の吐出口（９）
より液体室（２）へ流出する。このポンプ作用時におい
て、気体抜き孔りの設けられた側の他方の凹部（７・）
および羽根溝部（１ｏｂ）が浅く形成されているので、
この部分の圧力は一方の四部（）ｄ）側より高くなる０
従って、流体摩擦力も強く気体抜き孔［相］からの燃料
蒸気などの気泡のような気体の排出が十分なされ、イン
ペラ（４）ハ常にポンプカバー（３）側の凹部（７ｅ）
では液体燃料と接するのでベーノ（ロックが発生しにく
くなり、ポンプ作用が維持される０
〔発明の効果〕
以上説明したように、この発明の請求項１では、ポンプ
ケーシングおよびポンプカバーに設けられた凹部により
形成されたポンプ流路の拡大流路終端部の両凹部にポン
プ組立体外部へ連通する気体抜き孔を設け、この発明の
請求項２では、気体抜き孔を設けた側のポンプ流路凹部
を浅く、これに対抗するインペラの羽根溝深さも浅く形
成することにより、燃料蒸気のような気体が効率よく気
体抜き孔から排出されるので、ベーノくロックか発生し
にくい円周流式液体ポンプを得ることができる０In Figure 2, (2) to (4), (7) $0
3 is the same as that explained in the above conventional example. a
O is a blade groove part provided asymmetrically on the outer peripheral edge of the impeller (4), and the blade groove part αG is one blade groove part (10
The groove depths of a) and the other blade groove (mob) are L5 and L6, respectively. 1>116 is one recess that forms the enlarged flow path (1) of the pump flow path (7), and is provided in the pump casing (2). The depth is L7. ()・) is the other recess forming the enlarged flow path (71) of the pump flow path (7) and is provided in the pump cover (3), and its depth is L8, and I, 7>L8 Since the other configurations other than those described above are the same as those of the prior art, their explanation will be omitted. In general, in a circumferential flow liquid pump, if the cross-sectional area of the pump channel (7) is large, the discharge will be reduced. If the volume is large and the cross-sectional area is small, the discharge pressure will be high.
), the liquid fuel is sucked into one end of the pump flow path (7), flows to the pump flow path (7), and flows to the discharge port (9) at the other end.
The liquid flows out into the liquid chamber (2). During this pump action, the other recess (7) on the side where the gas vent hole is provided
And since the blade groove part (1ob) is formed shallowly,
The pressure in this part is higher than that in one part () d)0
Therefore, the fluid frictional force is strong, and gases such as fuel vapor and other bubbles are sufficiently discharged from the gas vent hole [phase], and the impeller (4) is always connected to the recess (7e) on the pump cover (3) side.
As explained above, in claim 1 of the present invention, the pump is provided in the pump casing and the pump cover. Gas vent holes communicating with the outside of the pump assembly are provided in both of the concave portions at the end portions of the enlarged flow channel of the pump flow channel formed by the concave portions, and in claim 2 of the present invention, the pump flow channel on the side where the gas vent holes are provided is provided. By making the recess shallow and the opposing impeller blade groove depth shallow, gases such as fuel vapor can be efficiently discharged from the gas vent hole, making it possible to reduce the possibility of locking. 0 you can get the pump
第１図は本発明の一実施例を示すポンプ組立体部の横断
面図、第２図は本発明の他の実施例を示すポンプ組立体
部の横断面図、第３図は円周流式液体ポンプを示す断面
図、第４図は第３図の■−■に沿うポンプ組立体部の縦
断面図、第５図は第４図の線■−■に沿う従来のポンプ
組立体部の横断面図である０
図において、（１）はポンプ組立体、（２）はポンプケ
ーシング、（３）はポンプカバー、（４）はインペラ、
（５）、αＧは羽根溝部、（７）はポンプ流路、（ハ）
は拡大流路部、（７ｂ）は段差部、（”）ｊ（）ｄ）、
（）ｅ）は四部、（８）は吸入口、α３．α４は気体抜
き孔、［相］は電動機である。
なお、各図中、同一符号は同一または相当部分を示す。
第１図FIG. 1 is a cross-sectional view of a pump assembly showing one embodiment of the present invention, FIG. 2 is a cross-sectional view of a pump assembly showing another embodiment of the present invention, and FIG. 3 is a circumferential flow diagram. Figure 4 is a longitudinal cross-sectional view of the pump assembly taken along line ■-■ in Figure 3, and Figure 5 is a conventional pump assembly taken along line ■-■ in Figure 4. In Figure 0, which is a cross-sectional view of
(5), αG is the blade groove, (7) is the pump flow path, (c)
is the enlarged channel part, (7b) is the step part, ('')j()d),
()e) is the four parts, (8) is the inlet, α3. α4 is a gas vent hole, and [phase] is an electric motor. In each figure, the same reference numerals indicate the same or corresponding parts. Figure 1
Claims (2)
、前記インペラを回転可能に支持し前記インペラの外周
縁部に沿つて延在する円弧帯状のポンプ流路及び該ポン
プ流路の両端部に吸入口と吐出口が配設されたポンプ組
立体とを有する円周流式液体ポンプにおいて、前記ポン
プ流路はポンプケーシングおよびポンプカバーに設けら
れた凹部により形成されており、前記ポンプ流路の吸入
口側に所定の長さで且つ前記ポンプ流路より広い断面積
に設けられた拡大流路と、この拡大流路終端部の前記ポ
ンプケーシング及びポンプカバーの双方の凹部に設けら
れ該ポンプ組立体外部へ連通する気体抜き孔とを備えた
ことを特徴とする円周流式液体ポンプ。(1) An impeller having blade grooves symmetrically on the outer circumferential edge, an arcuate belt-shaped pump channel that rotatably supports the impeller and extends along the outer circumferential edge of the impeller, and both ends of the pump channel In a circumferential flow liquid pump having a pump assembly having a suction port and a discharge port, the pump flow path is formed by a recess provided in a pump casing and a pump cover, and the pump flow path is formed by a recess provided in a pump casing and a pump cover. an enlarged channel provided on the inlet side of the channel with a predetermined length and a larger cross-sectional area than the pump channel; and an expanded channel provided in the recesses of both the pump casing and the pump cover at the end of the enlarged channel. A circumferential flow liquid pump characterized by having a gas vent communicating with the outside of the pump assembly.
、前記インペラを回転可能に支持し前記インペラの外周
縁部に沿つて延在する円弧帯状のポンプ流路及び該ポン
プ流路の両端部に吸入口と吐出口が配設されたポンプ組
立体とを有する円周流式液体ポンプにおいて、前記ポン
プ流路はポンプケーシングおよびポンプカバーに設けら
れた凹部により形成されており、前記ポンプ流路の吸入
口側に所定の長さで且つ前記ポンプ流路より広い断面積
に設けられた拡大流路と、この拡大流路終端部の前記ポ
ンプケーシングまたはポンプカバーのいずれか一方の凹
部に設けられ該ポンプ組立体外部へ連通する気体抜き孔
とを備え、前記インペラの羽根溝部に対向する凹部の探
さが前記気体抜き孔が配設された側の凹部の深さが他方
より浅く、且つ前記気体抜き孔が配設された側の流路凹
部に対抗する前記インペラの羽根溝部の溝深さも他方よ
り浅く形成されていることを特徴とする円周流式液体ポ
ンプ。(2) An impeller having blade grooves symmetrically on the outer peripheral edge, an arcuate belt-shaped pump passage that rotatably supports the impeller and extends along the outer peripheral edge of the impeller, and both ends of the pump passage. In a circumferential flow liquid pump having a pump assembly having a suction port and a discharge port, the pump flow path is formed by a recess provided in a pump casing and a pump cover, and the pump flow path is formed by a recess provided in a pump casing and a pump cover. an enlarged channel provided on the inlet side of the channel with a predetermined length and a wider cross-sectional area than the pump channel; and a recess provided in either the pump casing or the pump cover at the end of the enlarged channel. and a gas vent hole communicating with the outside of the pump assembly, and a recess facing the blade groove of the impeller is provided such that the depth of the recess on the side where the gas vent hole is provided is shallower than the other side, and A circumferential flow type liquid pump characterized in that the groove depth of the blade groove portion of the impeller opposing the flow path recess portion on the side where the gas vent hole is provided is also formed to be shallower than the other groove depth.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2136672A JP2536665B2 (en) | 1990-05-24 | 1990-05-24 | Circular flow type liquid pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2136672A JP2536665B2 (en) | 1990-05-24 | 1990-05-24 | Circular flow type liquid pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0431660A true JPH0431660A (en) | 1992-02-03 |
| JP2536665B2 JP2536665B2 (en) | 1996-09-18 |
Family
ID=15180781
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2136672A Expired - Fee Related JP2536665B2 (en) | 1990-05-24 | 1990-05-24 | Circular flow type liquid pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2536665B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5375970A (en) * | 1991-05-14 | 1994-12-27 | Mitsubishi Denki Kabushiki Kaisha | Circumferential flow type liquid pump |
| US6283704B1 (en) * | 1998-04-14 | 2001-09-04 | Mitsubishi Denki Kabushiki Kaisha | Circumferential flow type liquid pump |
| US7290979B2 (en) * | 2004-12-03 | 2007-11-06 | Mitsubishi Denki Kabushiki Kaisha | Circumferential flow pump |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60108795U (en) * | 1983-12-27 | 1985-07-24 | トヨタ自動車株式会社 | Circumferential flow liquid pump |
-
1990
- 1990-05-24 JP JP2136672A patent/JP2536665B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60108795U (en) * | 1983-12-27 | 1985-07-24 | トヨタ自動車株式会社 | Circumferential flow liquid pump |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5375970A (en) * | 1991-05-14 | 1994-12-27 | Mitsubishi Denki Kabushiki Kaisha | Circumferential flow type liquid pump |
| US6283704B1 (en) * | 1998-04-14 | 2001-09-04 | Mitsubishi Denki Kabushiki Kaisha | Circumferential flow type liquid pump |
| US7290979B2 (en) * | 2004-12-03 | 2007-11-06 | Mitsubishi Denki Kabushiki Kaisha | Circumferential flow pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2536665B2 (en) | 1996-09-18 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |