JP3115332B2 - Cooling water pump for water-cooled engine - Google Patents
Cooling water pump for water-cooled engineInfo
- Publication number
- JP3115332B2 JP3115332B2 JP02415646A JP41564690A JP3115332B2 JP 3115332 B2 JP3115332 B2 JP 3115332B2 JP 02415646 A JP02415646 A JP 02415646A JP 41564690 A JP41564690 A JP 41564690A JP 3115332 B2 JP3115332 B2 JP 3115332B2
- Authority
- JP
- Japan
- Prior art keywords
- cooling water
- impeller
- rotating shaft
- pump
- boss
- 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 - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、水冷エンジンにおいて
冷却水を循環させるための冷却水ポンプに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cooling water pump for circulating cooling water in a water-cooled engine.
【０００２】[0002]
【従来の技術】図４に従来の冷却水ポンプ１０１の断面
図を示すが、該冷却水ポンプ１０１はエンジン本体１１
１とポンプカバ−１０２との間に形成されるポンプ室１
０４に回転軸１０５の端部１０５ａを臨ませ、この端部
１０５ａにインペラ１０６を螺着して構成されている。2. Description of the Related Art FIG. 4 is a sectional view of a conventional cooling water pump 101.
Pump chamber 1 formed between pump cover 1 and pump cover 102
The end portion 105a of the rotating shaft 105 faces the end portion 04, and the impeller 106 is screwed to the end portion 105a.
【０００３】而して、エンジン動力の一部で回転軸１０
５が回転駆動されると、該回転軸１０５に結着されたイ
ンペラ１０６もポンプ室１０４内で一体的に回転し、不
図示のラジエ−タからの冷却水は冷却水パイプ１１５を
流れて冷却水ポンプ１０１の軸方向に吸引され、インペ
ラ１０６によって遠心方向の運動を与えられて昇圧され
た後、エンジン本体１１１に形成された冷却水通路１２
０を経て各エンジンシリンダに供給され、各部の冷却に
供される。[0003] The rotation shaft 10
When the rotary shaft 5 is driven to rotate, the impeller 106 connected to the rotary shaft 105 also rotates integrally in the pump chamber 104, and the cooling water from a radiator (not shown) flows through the cooling water pipe 115 to cool. After being sucked in the axial direction of the water pump 101 and given a centrifugal motion by the impeller 106 to be pressurized, a cooling water passage 12 formed in the engine body 111 is formed.
After passing through 0, it is supplied to each engine cylinder and used for cooling of each part.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、上記従
来の冷却水ポンプ１０１にあっては、回転軸１０５がエ
ンジン本体１１１を貫通する部位（軸貫通部）はメカニ
カルシ−ル１１０にてシ−ルされていたため、冷却水の
ポンプ室１０４側から回転軸１０５の表面に沿う漏れを
防ぐためにインペラ１０６を袋ナットの形態で回転軸１
０５の端部１０５ａに螺着しなければならなかった。こ
のため、インペラ１０６の頂部（袋ナットの袋部）１０
６ａの高さが高くなり、図４に示すようにインペラ頂部
１０６ａとポンプカバ−１０２との間の冷却水通路１２
１が狭くなり、冷却水通路１２１を流れる冷却水の流動
抵抗が大きくなってその円滑な流動が阻害されるという
問題があった。そして、この問題を解消するにはポンプ
カバ−１０２を高くしなければならず、このようにポン
プカバ−１０２を高くすると機器のレイアウトが制約を
受けるという問題が生じる。However, in the above-described conventional cooling water pump 101, a portion (shaft penetrating portion) where the rotating shaft 105 passes through the engine body 111 is sealed by a mechanical seal 110. In order to prevent the cooling water from leaking along the surface of the rotary shaft 105 from the pump chamber 104 side, the impeller 106 is connected to the rotary shaft 1 in the form of a cap nut.
05 had to be screwed to the end 105a. Therefore, the top of the impeller 106 (the bag portion of the bag nut) 10
The height of the cooling water passage 12 between the impeller top 106a and the pump cover 102 is increased as shown in FIG.
1, the flow resistance of the cooling water flowing through the cooling water passage 121 becomes large, and the smooth flow is hindered. In order to solve this problem, the pump cover 102 must be raised, and when the pump cover 102 is raised in this way, there is a problem that the layout of the device is restricted.
【０００５】本発明は上記問題に鑑みてなされたもの
で、その目的とする処は、ポンプ室内の冷却水通路面積
に余裕を与えて冷却水の流動抵抗を小さく抑え、冷却水
の円滑な流動を可能とする水冷エンジン用冷却水ポンプ
を提供することにある。The present invention has been made in view of the above problems, and an object thereof is to provide a margin for the area of a cooling water passage in a pump chamber so as to reduce the flow resistance of the cooling water and to make the flow of the cooling water smooth. It is an object of the present invention to provide a cooling water pump for a water-cooled engine that enables the above.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するた
め、本発明は、ポンプカバ−とエンジン本体との間に形
成されるポンプ室内に回転軸の端部を臨ませ、該回転軸
の端部にインペラを結着して成る水冷エンジン用冷却水
ポンプにおいて、前記エンジン本体の軸貫通部をオイル
シ−ルにてシ−ルするとともに、前記インペラのベ−ン
を径方向外方に向かって高さが低くなるようにその端面
を傾斜させ、インペラのボス部を前記ベ−ンの端面の外
側端付近まで突出させてその高さをベ−ンの中心側の高
さよりも低く設定するとともに、該ボス部にねじ孔を貫
設してインペラを前記回転軸の端部に螺着し、前記イン
ペラのボス部より前記回転軸の先端を露出させ、その先
端をカットして円錐面を形成し、前記インペラのボス部
に前記回転軸の先端の円錐面に連続するテ−パ面を形成
し、前記回転軸の先端の円錐面と該円錐面に連続する前
記インペラボス部のテーパ面と、前記ベーンの傾斜した
端面とを略平行に形成したことを特徴とする。In order to achieve the above object, the present invention is directed to a pump chamber formed between a pump cover and an engine body. In a cooling water pump for a water-cooled engine, an impeller is sealed with an oil seal, and a vane of the impeller is raised radially outward. And the boss of the impeller is protruded to the vicinity of the outer end of the end face of the vane so that its height is set lower than the height on the center side of the vane. A screw hole is provided in the boss portion, and an impeller is screwed to an end of the rotating shaft, a tip of the rotating shaft is exposed from the boss portion of the impeller, and the tip is cut to form a conical surface. , The tip of the rotating shaft on the boss of the impeller A tapered surface continuous with the conical surface is formed, and the conical surface at the tip of the rotating shaft, the tapered surface of the impeller boss portion continuous with the conical surface, and the inclined end surface of the vane are formed substantially in parallel. It is characterized by.
【０００７】[0007]
【作用】本発明によれば、回転軸がエンジン本体を貫通
する部位（軸貫通部）はオイルシ−ルにてシ−ルされる
ため、冷却水のポンプ室側から回転軸表面に沿う流れは
オイルシ−ルによって確実に阻止される。従って、イン
ペラを袋ナットの形態で回転軸に螺着する必要がなく、
インペラのボス部にはねじ孔を貫設することができる。
この結果、インペラのボス部の高さを低く抑えて該ボス
部とポンプカバ−との間の冷却水通路面積に余裕を与え
ることができ、冷却水通路を流れる冷却水の流動抵抗を
小さく抑えて冷却水の円滑な流動を実現することができ
る。又、回転軸とインペラの各端部をカットして連続し
たテ−パ面を形成したため、インペラのボス部への回転
軸の嵌合ねじ長を十分確保しながらポンプ室内の冷却水
通路面積に余裕を与えて冷却水の流動抵抗を小さく抑
え、冷却水の円滑な流動を実現することができる。According to the present invention, since the portion where the rotating shaft penetrates the engine body (shaft penetrating portion) is sealed by the oil seal, the flow of the cooling water from the pump chamber side along the rotating shaft surface is reduced. It is reliably prevented by the oil seal. Therefore, there is no need to screw the impeller to the rotating shaft in the form of a cap nut,
A screw hole can be provided through the boss of the impeller.
As a result, the height of the boss portion of the impeller can be kept low to allow a margin for the area of the cooling water passage between the boss portion and the pump cover, and the flow resistance of the cooling water flowing through the cooling water passage can be reduced. The smooth flow of the cooling water can be realized. In addition, since a continuous taper surface is formed by cutting each end of the rotary shaft and the impeller, the screw thread of the rotary shaft to the boss portion of the impeller is sufficiently secured while keeping the cooling water passage area in the pump chamber. With a margin, the flow resistance of the cooling water can be suppressed small, and a smooth flow of the cooling water can be realized.
【０００８】[0008]
【実施例】以下、本発明の一実施例を添付図面に基づい
て説明する。An embodiment of the present invention will be described below with reference to the accompanying drawings.
【０００９】図１は本発明に係る冷却水ポンプを示す断
面図、図２は自動二輪車用水冷エンジンの冷却水配管を
示す側面図、図３は同平面図である。FIG. 1 is a sectional view showing a cooling water pump according to the present invention, FIG. 2 is a side view showing a cooling water pipe of a motorcycle water-cooled engine, and FIG. 3 is a plan view thereof.
【００１０】先ず、図２及び図３に基づいてエンジン冷
却系のレイアウトを概説すると、図中、１１はエンジン
本体であって、これの前部には平面視で車幅方向にオフ
セットされた互いに直交する上シリンダ１２と下シリン
ダ１３が立設されている。そして、エンジン本体１１の
前方上部にはラジエ−タ１４が配され、エンジン本体１
１の側部であって、下シリンダ１３の後方位置には本発
明に係る冷却水ポンプ１が設けられている。First, an outline of the layout of the engine cooling system will be described with reference to FIGS. 2 and 3. In the drawings, reference numeral 11 denotes an engine main body. An orthogonal upper cylinder 12 and lower cylinder 13 are provided upright. A radiator 14 is provided at an upper front portion of the engine main body 11.
1, a cooling water pump 1 according to the present invention is provided at a position behind the lower cylinder 13.
【００１１】而して、ラジエ−タ１４の一側端下部から
延出する冷却水パイプ１５は前記冷却水ポンプ１の吸込
口に接続されている。A cooling water pipe 15 extending from a lower end of one end of the radiator 14 is connected to a suction port of the cooling water pump 1.
【００１２】又、前記上シリンダ１２から延出する冷却
水パイプ１６と下シリンダ１３から延出する冷却水パイ
プ１７は上シリンダ１２の斜め上方位置に配されるサ−
モスタット１８に接続されており、サ−モスタット１８
から延出する冷却水パイプ１９はラジエ−タ１４の他側
端上部に連結されている。A cooling water pipe 16 extending from the upper cylinder 12 and a cooling water pipe 17 extending from the lower cylinder 13 are provided at a position obliquely above the upper cylinder 12.
The thermostat 18 is connected to the thermostat 18.
A cooling water pipe 19 extending from the radiator 14 is connected to an upper end on the other side of the radiator 14.
【００１３】次に、本発明に係る冷却水ポンプ１の構成
の詳細を図１に基づいて説明する。Next, the configuration of the cooling water pump 1 according to the present invention will be described in detail with reference to FIG.
【００１４】図１において１１は前記エンジン本体であ
って、該エンジン本体１１にはポンプカバ−２がボルト
３・・・によって結着されており、ポンプカバ−２内に
はポンプ室４が形成されている。そして、ポンプカバ−
２の吸入口２ａには前記ラジエ−タ１４（図２及び図３
参照）から延出する冷却水パイプ１５が接続されてい
る。In FIG. 1, reference numeral 11 denotes the engine main body, and a pump cover-2 is connected to the engine main body 11 by bolts 3,..., And a pump chamber 4 is formed in the pump cover-2. I have. And the pump cover
2 is provided with the radiator 14 (FIGS. 2 and 3).
) Is connected.
【００１５】又、前記ポンプ室４にはエンジン本体１１
を貫通する回転軸５の端部５ａが臨んでおり、この端部
５ａにはインペラ６が間にワッシャ−７を介在させて螺
着されている。ここで、インペラ６はボス部６ａの周囲
に複数枚のベ−ン６ｂを一体に形成して構成されるが、
各ベ−ン６ｂは径方向外方に向かって高さが低くなるよ
うにその端面が傾斜しており、ボス部６ａは各ベ−ン６
ｂの端面の外側端付近まで突出され、その高さはベ−ン
６ｂの中心側の高さよりも低く設定されている。そし
て、インペラ６はボス部６ａにはねじ孔８が貫設されて
おり、このねじ孔８に回転軸５のねじ状端部５ａが螺
合、挿通している。尚、回転軸端部５ａの先端はカット
された円錐面５ａ−１を構成しており、インペラ６はボ
ス部６ａの端部もカットされた円錐面５ａ−１に連続す
るテ−パ面６ａ−１が形成されている。The pump chamber 4 contains an engine body 11.
The end 5a of the rotating shaft 5 penetrating through the shaft 5 faces, and an impeller 6 is screwed to the end 5a with a washer 7 interposed therebetween. Here, the impeller 6 is configured by integrally forming a plurality of vanes 6b around the boss portion 6a.
The end face of each vane 6b is inclined so that its height decreases radially outward, and the boss portion 6a is
b is protruded to the vicinity of the outer end of the end face, and the height thereof is set lower than the height of the vane 6b on the center side. The impeller 6 has a threaded hole 8 formed in the boss 6a, and the threaded end 5a of the rotating shaft 5 is screwed and inserted into the threaded hole 8. The tip of the rotating shaft end 5a forms a cut conical surface 5a-1, and the impeller 6 has a tapered surface 6a that is continuous with the cut conical surface 5a-1 at the end of the boss 6a. -1 is formed.
【００１６】一方、エンジン本体１１の回転軸５が貫通
する部位（軸貫通部）には軸封室９が形成されており、
この軸封室９には２列のオイルシ−ル１０が収納されて
おり、該オイルシ−ル１０は回転軸５の外周面に所定の
圧力で摺設する２列のリップ１０ａ、１０ａを有してい
る。On the other hand, a shaft sealing chamber 9 is formed at a portion (shaft penetrating portion) of the engine body 11 through which the rotating shaft 5 penetrates.
The shaft sealing chamber 9 accommodates two rows of oil seals 10, which have two rows of lips 10 a, 10 a slidably mounted on the outer peripheral surface of the rotating shaft 5 at a predetermined pressure. ing.
【００１７】而して、冷却水ポンプ１において回転軸５
がエンジン動力の一部で回転駆動され、該回転軸５の端
部に結着されたインペラ６がポンプ室４内で回転駆動さ
れると、ラジエ−タ１４にて冷却された冷却水は冷却水
パイプ１５を通ってポンプ室４内に導入され、回転する
インペラ６によって昇圧されて冷却水通路２０に吐出さ
れる。そして、この冷却水はエンジン本体１１に形成さ
れた不図示の冷却水通路を通って前記上シリンダ１２及
び下シリンダ１３に達して各部を冷却し、前記冷却水パ
イプ１６、１７、サ−モスタット１８及び冷却水パイプ
１９を通ってラジエ−タ１４に導入され、ラジエ−タ１
４における外気との熱交換によって冷却され、以後は以
上と同様の経路を経て循環し、各部を継続的に冷却す
る。Thus, in the cooling water pump 1, the rotating shaft 5
Is driven to rotate by a part of the engine power, and when the impeller 6 connected to the end of the rotary shaft 5 is driven to rotate in the pump chamber 4, the cooling water cooled by the radiator 14 is cooled. The water is introduced into the pump chamber 4 through the water pipe 15, pressurized by the rotating impeller 6, and discharged to the cooling water passage 20. The cooling water passes through a cooling water passage (not shown) formed in the engine body 11 and reaches the upper cylinder 12 and the lower cylinder 13 to cool the respective parts, thereby cooling the cooling water pipes 16 and 17 and the thermostat 18. And the cooling water pipe 19 is introduced into the radiator 14 and the radiator 1
The cooling unit 4 is cooled by heat exchange with the outside air, and thereafter circulates through the same route as described above to continuously cool each unit.
【００１８】ところで、本実施例ではエンジン本体１１
の軸貫通部のシ−ルはオイルシ−ル１０によってなされ
ているため、冷却水のポンプ室４側から回転軸５の表面
に沿う漏れはオイルシ−ル１０によって確実に阻止され
る。このため、インペラ６と回転軸５との螺合部におけ
る冷却水の漏れが許容され、従って、従来のようにイン
ペラ６を袋ナットの形態で回転軸５に螺着する必要がな
く、本実施例のようにインペラにねじ孔８を貫設し、イ
ンペラ６を通常のナットの形態で回転軸５の端部５ａに
螺着することができる。この結果、図１に示すようにイ
ンペラ６のボス部６ａの高さをベ−ン６ｂ・・・の高さ
よりも低く抑えることができ、該ボス部６ａとポンプカ
バ−２の間の冷却水通路２１の面積を拡大することがで
きる。従って、ポンプ室４内を流れる冷却水の冷却水通
路２１での流動抵抗は小さく抑えられ、冷却水の円滑な
流動が可能となる。又、前述のように回転軸端部５ａの
先端及びインペラボス部６ａの先端をカットして円錐面
５ａ−１、テ−パ面６ａ−１を形成したため、冷却水は
冷却水通路２１をより滑らかに流れることができる。In this embodiment, the engine body 11
Is sealed by the oil seal 10 so that leakage of the cooling water from the pump chamber 4 side along the surface of the rotary shaft 5 is reliably prevented by the oil seal 10. For this reason, the leakage of the cooling water at the threaded portion between the impeller 6 and the rotating shaft 5 is allowed. Therefore, it is not necessary to screw the impeller 6 to the rotating shaft 5 in the form of a cap nut as in the related art. As in the example, the screw hole 8 is provided through the impeller, and the impeller 6 can be screwed to the end 5a of the rotating shaft 5 in the form of a normal nut. As a result, as shown in FIG. 1, the height of the boss 6a of the impeller 6 can be kept lower than the height of the vanes 6b..., And the cooling water passage between the boss 6a and the pump cover-2. 21 can be enlarged. Accordingly, the flow resistance of the cooling water flowing through the pump chamber 4 in the cooling water passage 21 is suppressed to be small, and the cooling water can flow smoothly. Further, as described above, since the conical surface 5a-1 and the tapered surface 6a-1 are formed by cutting the tip of the rotary shaft end 5a and the tip of the impeller boss 6a, the cooling water flows through the cooling water passage 21 more smoothly. Can flow to
【００１９】[0019]
【発明の効果】以上の説明で明らかなように、本発明に
よれば、ポンプカバ−とエンジン本体との間に形成され
るポンプ室内に回転軸の端部を臨ませ、該回転軸の端部
にインペラを結着して成る水冷エンジン用冷却水ポンプ
において、前記エンジン本体の軸貫通部をオイルシ−ル
にてシ−ルするとともに、前記インペラのベ−ンを径方
向外方に向かって高さが低くなるようにその端面を傾斜
させ、インペラのボス部を前記ベ−ンの端面の外側端付
近まで突出させてその高さをベ−ンの中心側の高さより
も低く設定するとともに、該ボス部にねじ孔を貫設して
インペラを前記回転軸の端部に螺着し、前記インペラの
ボス部より前記回転軸の先端を露出させ、その先端をカ
ットして円錐面を形成し、前記インペラのボス部に前記
回転軸の先端の円錐面に連続するテ−パ面を形成したた
め、インペラのボス部への回転軸の嵌合ねじ長を十分確
保しながらポンプ室内の冷却水通路面積に余裕を与えて
冷却水の流動抵抗を小さく抑え、冷却水の円滑な流動を
実現することができるという効果が得られる。また、回
転軸の先端の円錐面と該円錐面に連続するインペラのボ
ス部のテーパ面と、前記ベーンの傾斜した端面とを略平
行に形成したことで、前記ベーンの傾斜した端面は、ポ
ンプ効率向上のために通常、ポンプカバー部の内面の傾
斜面と近接し、略平行であるから、回転軸の先端の円錐
面と該円錐面に連続するインペラのボス部のテーパ面が
ポンプカバー部内面の傾斜面と略平行になる。したがっ
て、回転軸の先端の円錐面と該円錐面に連続するインペ
ラのボス部のテーパ面とポンプカバー部内面の傾斜面と
の間の流路の通路断面積が流れ方向において一定で変化
がないから、この流路における通路抵抗の変化はなく、
したがって、冷却水の流れが安定する。As is apparent from the above description, according to the present invention, the end of the rotating shaft faces the pump chamber formed between the pump cover and the engine body, and the end of the rotating shaft is exposed. In a cooling water pump for a water-cooled engine, an impeller is sealed with an oil seal, and a vane of the impeller is raised radially outward. And the boss of the impeller is protruded to the vicinity of the outer end of the end face of the vane so that its height is set lower than the height on the center side of the vane. A screw hole is provided in the boss portion, and an impeller is screwed to an end of the rotating shaft, a tip of the rotating shaft is exposed from the boss portion of the impeller, and the tip is cut to form a conical surface. A circle at the tip of the rotating shaft on the boss of the impeller Since the taper surface is continuous with the surface, a sufficient screw thread length of the rotating shaft to the impeller boss is ensured, while allowing room for the cooling water passage area in the pump chamber to reduce the flow resistance of the cooling water. Thus, the effect that the smooth flow of the cooling water can be realized is obtained. Further, by forming the conical surface at the tip of the rotating shaft, the tapered surface of the boss portion of the impeller connected to the conical surface, and the inclined end surface of the vane substantially parallel to each other, the inclined end surface of the vane is a pump. In order to improve efficiency, the inner surface of the pump cover is usually close to and substantially parallel to the inclined surface, so that the conical surface at the tip of the rotating shaft and the tapered surface of the boss of the impeller connected to the conical surface are formed in the pump cover. It becomes substantially parallel to the inclined surface of the inner surface. Therefore, the cross-sectional area of the flow path between the conical surface at the tip of the rotating shaft, the tapered surface of the boss portion of the impeller connected to the conical surface, and the inclined surface of the inner surface of the pump cover portion is constant in the flow direction and does not change. Therefore, there is no change in the passage resistance in this flow path,
Therefore, the flow of the cooling water is stabilized.
【図１】本発明に係る冷却水ポンプを示す断面図であ
る。FIG. 1 is a sectional view showing a cooling water pump according to the present invention.
【図２】自動二輪車用水冷エンジンの冷却水配管を示す
側面図である。FIG. 2 is a side view showing a cooling water pipe of the motorcycle water-cooled engine.
【図３】自動二輪車用水冷エンジンの冷却水配管を示す
平面図である。FIG. 3 is a plan view showing a cooling water pipe of the motorcycle water-cooled engine.
【図４】従来の冷却水ポンプを示す断面図である。FIG. 4 is a sectional view showing a conventional cooling water pump.
１・・・冷却水ポンプ ２・・・ポンプカバー ４・・・ポンプ室 ５・・・回転軸 ５ａ・・・回転軸端部 ６・・・インペラ ８・・・ねじ孔 １０・・・オイルシ−ル １１・・・エンジン本体 DESCRIPTION OF SYMBOLS 1 ... Cooling water pump 2 ... Pump cover 4 ... Pump chamber 5 ... Rotating shaft 5a ... Rotating shaft end part 6 ... Impeller 8 ... Screw hole 10 ... Oil seal Le 11 ・ ・ ・ Engine body
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F01P 5/10 F01P 5/12 F04D 29/10 ──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. 7 , DB name) F01P 5/10 F01P 5/12 F04D 29/10
Claims (1)
されるポンプ室内に回転軸の端部を臨ませ、該回転軸の
端部にインペラを結着して成る水冷エンジン用冷却水ポ
ンプにおいて、 前記エンジン本体の軸貫通部をオイルシ−ルにてシ−ル
するとともに、前記インペラのベ−ンを径方向外方に向
かって高さが低くなるようにその端面を傾斜させ、イン
ペラのボス部を前記ベ−ンの端面の外側端付近まで突出
させてその高さをベ−ンの中心側の高さよりも低く設定
するとともに、該ボス部にねじ孔を貫設してインペラを
前記回転軸の端部に螺着し、前記インペラのボス部より
前記回転軸の先端を露出させ、その先端をカットして円
錐面を形成し、前記インペラのボス部に前記回転軸の先
端の円錐面に連続するテ−パ面を形成し、前記回転軸の
先端の円錐面と該円錐面に連続する前記インペラボス部
のテーパ面と、前記ベーンの傾斜した端面とを略平行に
形成したことを特徴とする水冷エンジン用冷却水ポン
プ。1. A cooling water pump for a water-cooled engine, wherein an end of a rotating shaft faces a pump chamber formed between a pump cover and an engine body, and an impeller is connected to the end of the rotating shaft. The shaft penetrating portion of the engine body is sealed with an oil seal, and the end face of the impeller vane is inclined so that its height decreases radially outward, so that the impeller boss is formed. The protruding part is protruded to the vicinity of the outer end of the end face of the vane so that its height is set lower than the height on the center side of the vane. Screwed to the end of the shaft, exposing the tip of the rotating shaft from the boss of the impeller, cutting the tip to form a conical surface, and forming the conical surface of the tip of the rotating shaft on the boss of the impeller. To form a tapered surface that is continuous with A cooling water pump for a water-cooled engine, wherein a conical surface at an end, a tapered surface of the impeller boss portion continuous with the conical surface, and an inclined end surface of the vane are formed substantially in parallel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP02415646A JP3115332B2 (en) | 1990-12-28 | 1990-12-28 | Cooling water pump for water-cooled engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP02415646A JP3115332B2 (en) | 1990-12-28 | 1990-12-28 | Cooling water pump for water-cooled engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04232398A JPH04232398A (en) | 1992-08-20 |
| JP3115332B2 true JP3115332B2 (en) | 2000-12-04 |
Family
ID=18523983
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP02415646A Expired - Fee Related JP3115332B2 (en) | 1990-12-28 | 1990-12-28 | Cooling water pump for water-cooled engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3115332B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6419981B1 (en) | 1998-03-03 | 2002-07-16 | Ppg Industries Ohio, Inc. | Impregnated glass fiber strands and products including the same |
| US6593255B1 (en) | 1998-03-03 | 2003-07-15 | Ppg Industries Ohio, Inc. | Impregnated glass fiber strands and products including the same |
| US8062746B2 (en) | 2003-03-10 | 2011-11-22 | Ppg Industries, Inc. | Resin compatible yarn binder and uses thereof |
| US8105690B2 (en) | 1998-03-03 | 2012-01-31 | Ppg Industries Ohio, Inc | Fiber product coated with particles to adjust the friction of the coating and the interfilament bonding |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6378641B2 (en) * | 2015-03-27 | 2018-08-22 | 株式会社クボタ | Engine water cooling system |
-
1990
- 1990-12-28 JP JP02415646A patent/JP3115332B2/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6419981B1 (en) | 1998-03-03 | 2002-07-16 | Ppg Industries Ohio, Inc. | Impregnated glass fiber strands and products including the same |
| US6593255B1 (en) | 1998-03-03 | 2003-07-15 | Ppg Industries Ohio, Inc. | Impregnated glass fiber strands and products including the same |
| US8105690B2 (en) | 1998-03-03 | 2012-01-31 | Ppg Industries Ohio, Inc | Fiber product coated with particles to adjust the friction of the coating and the interfilament bonding |
| US8062746B2 (en) | 2003-03-10 | 2011-11-22 | Ppg Industries, Inc. | Resin compatible yarn binder and uses thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04232398A (en) | 1992-08-20 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| LAPS | Cancellation because of no payment of annual fees |