JPH0629512Y2 - Water pump - Google Patents
Water pumpInfo
- Publication number
- JPH0629512Y2 JPH0629512Y2 JP1988046960U JP4696088U JPH0629512Y2 JP H0629512 Y2 JPH0629512 Y2 JP H0629512Y2 JP 1988046960 U JP1988046960 U JP 1988046960U JP 4696088 U JP4696088 U JP 4696088U JP H0629512 Y2 JPH0629512 Y2 JP H0629512Y2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- pump
- cylindrical portion
- pump body
- fixed
- 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 - Lifetime
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims description 14
- 230000002093 peripheral effect Effects 0.000 claims description 9
- 238000004519 manufacturing process Methods 0.000 description 8
- 229910052751 metal Inorganic materials 0.000 description 6
- 239000002184 metal Substances 0.000 description 6
- 238000003466 welding Methods 0.000 description 6
- 238000001816 cooling Methods 0.000 description 4
- 229910052782 aluminium Inorganic materials 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- 230000004323 axial length Effects 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000003014 reinforcing effect Effects 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000004512 die casting Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【考案の詳細な説明】 産業上の利用分野 本考案は内燃機関の水冷式冷却装置に用いられるウォー
タポンプに関する。TECHNICAL FIELD The present invention relates to a water pump used in a water-cooled cooling device for an internal combustion engine.
従来の技術 周知のように、例えば自動車用内燃機関の水冷式冷却装
置には、シリンダブロックやシリンダヘッドに冷却水を
強制循環させるウォータポンプが設けられており、第７
図はその一例を示している（特開昭６１−７９８９９号
公報等参照）。As is well known in the prior art, for example, a water cooling type cooling device for an internal combustion engine for an automobile is provided with a water pump for forcibly circulating cooling water in a cylinder block or a cylinder head.
The figure shows an example thereof (see Japanese Patent Laid-Open No. 61-79899).
概略を説明すれば、従来のウォータポンプは、アルミニ
ウム鋳物製のポンプボディ１の後端側に円筒状のボス部
１ａが一体に形成されていると共に、このボス部１ａ内
にベアリング２の外壁２ａの延在部３が圧入固定されて
いる。また、このポンプボディ１内には、ベアリング２
を介して回転軸４が軸受されていると共に、この回転軸
４の一端に固定されたポンプロータ５が収納され、ま
た、このポンプロータ５とベアリング２との間には、ポ
ンプ室６を密封するメカニカルシール７が配設されてい
る。更に、回転軸４の他端には、機関のクランク軸から
駆動力が伝達されるプーリ８が固定されている。Briefly described, in a conventional water pump, a cylindrical boss portion 1a is integrally formed on the rear end side of a pump body 1 made of aluminum casting, and an outer wall 2a of a bearing 2 is formed in the boss portion 1a. The extended portion 3 of is fixed by press fitting. In addition, in this pump body 1, a bearing 2
The rotary shaft 4 is supported by the rotary shaft 4 and a pump rotor 5 fixed to one end of the rotary shaft 4 is housed. A pump chamber 6 is sealed between the pump rotor 5 and the bearing 2. A mechanical seal 7 is provided. Further, a pulley 8 to which the driving force is transmitted from the crankshaft of the engine is fixed to the other end of the rotary shaft 4.
考案が解決しようとする課題 然し乍ら、上記従来のウォータポンプにあっては、ポン
プボディ１とベアリング２とが上述のようにボス部１ａ
内へ延在部３を圧入固定して連結するようになっている
ため、圧入した部分の確実な固着状態と確実なシール性
を得る必要上、両者１ａ，３の圧入の締め代を比較的大
きく設定しなければならない。即ち、ポンプボディ１を
アルミニウムのダイカスト等で製作する場合は、鉄系金
属からなるベアリング２の外壁２ａとの線膨張係数の差
に基づく高温雰囲気中の締め代の低下を補うために、圧
入の締め代を大きく設定しているのでベアリング２をポ
ンプボディ１に圧入する際に、ポンプボディ１を加熱し
ボス部１ａの内径を拡径した状態で圧入する。この結
果、冷機時には延在部３側のベアリングボール２ｂに偏
荷重が発生して偏摩耗などによりベアリング２の耐久性
が低下する。また、組立の自動化を図る上でも圧入する
ことが障害になっている。However, in the conventional water pump described above, the pump body 1 and the bearing 2 have the boss portion 1a as described above.
Since the extension portion 3 is press-fitted and fixed and connected to the inside, the press-fitting margins of the both 1a and 3 are relatively large in order to obtain a secure fixed state of the press-fitted portion and a reliable sealability. Must be set large. That is, when the pump body 1 is manufactured by die casting of aluminum or the like, in order to compensate for the reduction of the interference in the high temperature atmosphere due to the difference in the linear expansion coefficient between the bearing 2 made of iron-based metal and the outer wall 2a, the press-fitting is performed. Since the tightening allowance is set to a large value, when the bearing 2 is press-fitted into the pump body 1, the pump body 1 is heated and press-fitted with the inner diameter of the boss portion 1a being expanded. As a result, the bearing ball 2b on the side of the extending portion 3 is subjected to an eccentric load during cooling, and the durability of the bearing 2 is reduced due to eccentric wear. Also, press fitting is an obstacle in automating the assembly.
更に、ボス部１ａと延在部３ときお圧入部位相互の寸法
公差を厳格に管理しなければならず、高精度な加工が要
求され、したがって製造コストの高騰が余儀なくされ
る。Further, the dimensional tolerance between the boss portion 1a and the extension portion 3 and the press-fitted portion must be strictly controlled, which requires high-precision processing, which inevitably increases the manufacturing cost.
更にまた、ポンプボディ１が、厚肉のアルミニウム鋳物
製であるため、重量が大きくなり、車体軽量化の要請を
十分に満足することができない。Furthermore, since the pump body 1 is made of a thick cast aluminum product, the weight of the pump body 1 becomes large, and the demand for weight reduction of the vehicle body cannot be sufficiently satisfied.
そこで、例えば実開昭５９−１０７９９９号公報に記載
された考案のように、ポンプボディを構成する金属製の
主部材とカップ状の副部材とをプレス成形によって形成
すると共に、主部材の段差状円筒部の小径部にベアリン
グユニットを挿入し、かつ円筒部の大径部に圧入固定さ
れた前記副部材にメカニカルユニットを保持するように
したものも提供されている。Therefore, for example, as in the invention disclosed in Japanese Utility Model Laid-Open No. 59-107999, a main metal member and a cup-shaped sub member that form a pump body are formed by press molding, and the main member has a stepped shape. There is also provided one in which a bearing unit is inserted into a small diameter portion of a cylindrical portion and the mechanical unit is held by the sub member press-fitted and fixed to the large diameter portion of the cylindrical portion.
しかし、この公報記載の従来例は、ベアリングユニット
の外輪を円筒部で完全に被うようになっているので、ポ
ンプの外径寸法が必然的に大きくなってしまう。また、
主部材の他に、副部材を別個に設けているため、部品点
数が増加し、重量の増加を招いていると共に、製造作業
能率の低下やコストの高騰が余儀なくされている。However, in the conventional example described in this publication, since the outer ring of the bearing unit is completely covered with the cylindrical portion, the outer diameter dimension of the pump inevitably becomes large. Also,
Since the auxiliary member is separately provided in addition to the main member, the number of parts is increased, the weight is increased, and the manufacturing work efficiency is reduced and the cost is increased.
しかも、円筒部が軸方向へ長尺に形成されかつ大小径の
段差状になっているため、プレス成形時に深絞り加工を
行わなければならないばかりか、絞り加工による公差管
理が困難になる。この結果、製造作業能率がさらに悪化
する。また、副部材を円筒部内に圧入により固定するた
め、圧入代の管理も必要となり、製造作業能率の著しい
低下は否めない。Moreover, since the cylindrical portion is formed to be long in the axial direction and has a stepped shape with large and small diameters, not only must deep drawing be performed at the time of press forming, but tolerance control by drawing becomes difficult. As a result, the manufacturing work efficiency further deteriorates. Further, since the sub member is fixed in the cylindrical portion by press fitting, it is necessary to control the press fitting margin, and it is undeniable that the manufacturing work efficiency is significantly reduced.
課題を解決するための手段 本考案は、前記従来の問題点に鑑みて案出されたもの
で、とりわけプレス成形されたポンプボディの後端側略
中央部に回転軸の軸方向に沿って折曲された円筒部を形
成する一方、ベアリングの外輪の一端部を軸方向へ延長
形成すると共に、該延長部の先端部を上記円筒部の内周
面に嵌入固定し、かつ上記メカニカルシールを延長部の
先端部に固定したことを特徴としている。Means for Solving the Problems The present invention has been devised in view of the above-mentioned conventional problems, and in particular, folds along the axial direction of the rotating shaft at the rear end side substantially central portion of the press body that is press-molded. While forming a curved cylindrical portion, one end of the outer ring of the bearing is formed to extend in the axial direction, the tip of the extended portion is fitted and fixed to the inner peripheral surface of the cylindrical portion, and the mechanical seal is extended. It is characterized in that it is fixed to the tip of the part.
作用 前記構成の本考案によれば、組み立て時において延長部
の先端部を円筒部に中間ばめまたすきまばめ程度に嵌入
した後、溶接等によって接合するため、ベアリングの外
輪に対する緊締力が作用しなくなり、外輪内のベアリン
グボール等に対する偏荷重の発生が防止される。According to the present invention having the above-mentioned structure, since the tip end of the extension portion is inserted into the cylindrical portion at the time of the intermediate fit or the clearance fit at the time of assembly and then joined by welding or the like, the tightening force on the outer ring of the bearing acts. This prevents the occurrence of an eccentric load on the bearing balls in the outer ring.
また、延長部が、ポンプボディへのベアリング固定用と
メカニカルシールの固定用の両方の機能を兼用している
ため、部品点数の増加が防止される。Further, since the extension part has both the function of fixing the bearing to the pump body and the function of fixing the mechanical seal, an increase in the number of parts is prevented.
更に、上記円筒部は、短尺でかつその形状も均一径の単
純な円筒形であるため、該円筒部の絞り加工作業も容易
になる。Furthermore, since the cylindrical portion is a short cylinder and the shape thereof is a simple cylindrical shape having a uniform diameter, the work of drawing the cylindrical portion is facilitated.
実施例 以下、本考案の実施例を図面に基づいて詳述する。Embodiment Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.
第１図は本考案に係るウォータポンプの第１実施例を示
し、このウォータポンプは、略円形状のポンプボディ１
１と、該ポンプボディ１１の後端側に固定されたベアリ
ング１２と、該ベアリング１２の内部に軸受され、かつ
機関のクランク軸により（図外の）プーリ及びプーリシ
ート１３を介して回転力が伝達される回転軸１４と、該
回転軸１４の一端に固定されたポンプロータ１５とを備
えている。FIG. 1 shows a first embodiment of a water pump according to the present invention, which is a substantially circular pump body 1
1, a bearing 12 fixed to the rear end side of the pump body 11, a bearing inside the bearing 12, and a rotational force generated by a crankshaft of the engine via a pulley (not shown) and a pulley seat 13. The rotary shaft 14 to be transmitted and the pump rotor 15 fixed to one end of the rotary shaft 14 are provided.
上記ポンプボディ１１は、比較的薄肉な金属板をプレス
成形して形成され、第２図に示すように内燃機関の端部
に取付けられる前端部の外周にフランジ部１６が形成さ
れており、このフランジ部１６には、周方向４ケ所にボ
ルト孔１７が形成されていると共に、前面に液体パッキ
ン等を充填する凹溝１８が略周方向に沿って形成されて
いる。また、ポンプボディ１１の外方へ膨出した後端部
中央には、第１図に示すように回転軸１４の軸方向へ沿
って内側へ折曲されてなる円筒部１９を有し、この円筒
部１９の内部に固定用孔２０が形成されている。即ち、
この円筒部１９は、均一径の単純な円筒形に形成されて
いると共に、その軸方向の長さが後述する延長部２１の
みを被う程度の短い長さに設定されている。The pump body 11 is formed by press-molding a relatively thin metal plate, and as shown in FIG. 2, a flange portion 16 is formed on the outer periphery of the front end portion attached to the end portion of the internal combustion engine. Bolt holes 17 are formed in the flange portion 16 at four locations in the circumferential direction, and concave grooves 18 for filling a liquid packing or the like are formed in the front surface along the substantially circumferential direction. Further, as shown in FIG. 1, at the center of the rear end portion which bulges outward of the pump body 11, there is provided a cylindrical portion 19 which is bent inward along the axial direction of the rotary shaft 14, A fixing hole 20 is formed inside the cylindrical portion 19. That is,
The cylindrical portion 19 is formed in a simple cylindrical shape having a uniform diameter, and its axial length is set to be short enough to cover only the extension portion 21 described later.
一方、ベアリング１２は、第１図に示すように回転軸１
４の外周面に有する２連のベアリング溝１４ａ，１４ａ
に案内される複数のベアリングボール１２ａ，１２ａ
と、該ベアリングボール１２ａ，１２ａを保持する円筒
状の外輪１２ｂとを備えており、この外輪１２ｂの固定
端側には、軸方向へ突出し、かつ、焼入れした剛性の高
い円筒状の延長部２１が連続して形成されている。この
延長部２１は、外径が上記固定用孔２０の内径と同じか
または僅かに小さい寸法に設定されて固定用孔２０内に
中間ばめまたはすきまばめ程度に挿通嵌合されている。
また、この延長部２１とポンプロータ１５との間には、
メカニカルシール２２が配設されており、このメカニカ
ルシール２２は、外周部が延長部２１の先端部に固定さ
れた保持金具２１ｂと、スプリング２２ａによって保持
金具２２ｂ側に付勢された可撓シール部２２ｃと、この
シール部２２ｃに接着されかつカーボン等で成形した摺
動材２２ｆと、例えばセラミックスで成形したスラスト
ワッシャ２２ｄと、ポンプロータ１５との間に配置され
たフローティングシート部２２ｅとによってベアリング
１２内側への冷却水の漏出を防止するようになってい
る。On the other hand, the bearing 12 has a rotating shaft 1 as shown in FIG.
4 bearing grooves 14a, 14a on the outer peripheral surface
Bearing balls 12a, 12a guided by
And a cylindrical outer ring 12b for holding the bearing balls 12a, 12a. The fixed end side of the outer ring 12b has a cylindrical extension portion 21 which is axially projected and has high hardness. Are continuously formed. The outer diameter of the extension portion 21 is set to be equal to or slightly smaller than the inner diameter of the fixing hole 20, and is inserted and fitted in the fixing hole 20 to the extent of an intermediate fit or a clearance fit.
Further, between the extension portion 21 and the pump rotor 15,
A mechanical seal 22 is provided. The mechanical seal 22 includes a holding metal fitting 21b whose outer peripheral portion is fixed to the tip of the extension portion 21 and a flexible sealing portion urged toward the holding metal fitting 22b by a spring 22a. 22c, a sliding member 22f bonded to the seal portion 22c and formed of carbon or the like, a thrust washer 22d formed of, for example, ceramics, and a floating seat portion 22e arranged between the pump rotor 15 and the bearing 12 It is designed to prevent leakage of cooling water to the inside.
そして、上記延長部２１と固定用孔２０の内周面つまり
円筒部１９の内周面とは、熱影響の少ないレーザ溶接に
よって接合されている。The extension portion 21 and the inner peripheral surface of the fixing hole 20, that is, the inner peripheral surface of the cylindrical portion 19 are joined by laser welding, which has a small thermal effect.
したがって、この実施例によれば上述のように延長部２
１を円筒部１９の固定用孔２０に圧入固定するのではな
く、中間ばめまたはすきまばめ程度に嵌入した後、溶接
によって接合する。このように、焼き入れした剛性の高
い延長部２１を薄肉な円筒部１９の固定用孔２０に嵌入
する際には、該円筒部１９側が僅かに拡径するので、外
輪１２ｂ側に強い緊締力が作用しない。このため、ベア
リング１２ａに対する偏荷重の発生が確実に防止され、
常時最適なクリアランスが確保される。また、延長部２
１が、ポンプボディ１１へのベアリング固定用と、メカ
ニカルシール２２の固定用の両方の機能を兼備している
ため、部品点数の増加が防止される。この結果、重量の
増加を防止できると共に、製造作業能率の向上とコスト
の低廉化が図れる。Therefore, according to this embodiment, as described above, the extension 2
1 is not press-fitted and fixed in the fixing hole 20 of the cylindrical portion 19, but is fitted to an intermediate fit or a clearance fit and then joined by welding. In this way, when the hardened extension portion 21 having a high rigidity is fitted into the fixing hole 20 of the thin-walled cylindrical portion 19, the cylindrical portion 19 side slightly expands in diameter, so that a strong tightening force is exerted on the outer ring 12b side. Does not work. For this reason, the occurrence of an unbalanced load on the bearing 12a is reliably prevented,
The optimum clearance is always secured. Also, the extension 2
Since 1 has both the function of fixing the bearing to the pump body 11 and the function of fixing the mechanical seal 22, the increase in the number of parts is prevented. As a result, it is possible to prevent an increase in weight, improve manufacturing work efficiency, and reduce costs.
しかも、円筒部１９は、軸方向の長さが短く設定され、
その形状も均一径の単純な円筒形になっているので、円
筒部１９の絞り加工作業等も容易になる。Moreover, the cylindrical portion 19 is set to have a short axial length,
Since the shape thereof is also a simple cylindrical shape having a uniform diameter, the drawing work of the cylindrical portion 19 and the like become easy.
また、上記延長部２１と円筒部１９とをレーザ溶接では
なく通常のアーク溶接を行う場合は、予め円筒部１９と
延長部２１とを溶接して接合した後に、延長部２１の仕
上加工を行い、その後ベアリング１２を組付ければ、該
ベアリング１２に対する溶接による熱的影響を回避でき
る。Further, when the above-mentioned extension portion 21 and the cylindrical portion 19 are not subjected to laser welding but ordinary arc welding, the cylindrical portion 19 and the extension portion 21 are previously welded and joined, and then the extension portion 21 is finished. By assembling the bearing 12 thereafter, the thermal influence of the welding on the bearing 12 can be avoided.
尚、図中２３はベアリング外輪１２ｂの自由端側と回転
軸１４との間をシールする環状シール部材、２４は延長
部２１の外輪１２ｂ側周壁に形成されたドレン孔であ
る。Reference numeral 23 in the drawing denotes an annular seal member that seals between the free end side of the bearing outer ring 12b and the rotary shaft 14, and 24 denotes a drain hole formed in a peripheral wall of the extension portion 21 on the outer ring 12b side.
第３図は本考案の第２実施例を示し、この実施例では、
ポンプボディ１１の円筒部１９を内側ではなく外側に折
曲形成して内部に固定用孔２０を形成するようになって
いる。したがって、第１実施例と同様な作用効果が得ら
れることは勿論のこと、斯る固定用孔２０付近のポンプ
ボディ１１の後端部を第１実施例の如く外方へ膨出させ
る必要がないので製造作業性が良好になる。FIG. 3 shows a second embodiment of the present invention. In this embodiment,
The cylindrical portion 19 of the pump body 11 is bent to the outside rather than the inside, and the fixing hole 20 is formed inside. Therefore, it is of course necessary to swell the rear end portion of the pump body 11 in the vicinity of the fixing hole 20 outwardly as in the first embodiment, in addition to obtaining the same effects as the first embodiment. Since it does not exist, manufacturing workability is improved.
第４図及び第５図は本考案の第２実施例を示し、この実
施例ではポンプボディ１１の円筒部１９が第１実施例と
同様に内側へ折曲され、その固定用孔２０の内周面に雌
ねじ部２０ａが形成されている。一方、ベアリング１２
の延長部２１外周面に、上記雌ねじ部２０ａに螺合する
雄ねじ部２１ａが形成されていると共に、該雄ねじ部２
１ａとドレン孔２４との間の外周に六角ねじ形のフラン
ジ部２５が形成されている。また、このフランジ部２５
の内端縁と円筒部１９の外端縁との間には、環状シール
部材２６が介装されている。4 and 5 show a second embodiment of the present invention. In this embodiment, the cylindrical portion 19 of the pump body 11 is bent inward as in the first embodiment and the fixing hole 20 is A female screw portion 20a is formed on the peripheral surface. On the other hand, bearing 12
On the outer peripheral surface of the extension portion 21 of the male screw portion 21a, which is screwed into the female screw portion 20a, is formed.
A hexagonal screw-shaped flange portion 25 is formed on the outer circumference between the 1a and the drain hole 24. Also, this flange portion 25
An annular seal member 26 is interposed between the inner end edge of the cylindrical portion 19 and the outer end edge of the cylindrical portion 19.
したがって、この実施例によれば、延長部２１の雄ねじ
部２１ａを固定用孔の雌ねじ部２０ａに螺合させてフラ
ンジ部２５が固定用孔２０の孔縁に突き当るまで螺じ込
めば、ポンプボディ１１にベアリング１２が確実かつ強
固に接合する。したがって、ベアリング１２には軸方向
の荷重は作用するものの軸心方向への緊締力が十分に抑
制され、ベアリングボール１２ａに対する偏荷重が防止
される。また、シール部材２６によって両者１１，１２
間がシールされ十分な液密性が得られる。また、両者１
１，１２は、雌雄ねじ部２０ａ，２１ａを螺着させるだ
けで接合できるのでその組付作業が極めて容易になる。Therefore, according to this embodiment, if the male screw portion 21a of the extension portion 21 is screwed into the female screw portion 20a of the fixing hole and screwed until the flange portion 25 abuts against the hole edge of the fixing hole 20, the pump The bearing 12 is securely and firmly joined to the body 11. Therefore, although a load in the axial direction acts on the bearing 12, the tightening force in the axial direction is sufficiently suppressed, and an unbalanced load on the bearing ball 12a is prevented. In addition, the sealing member 26 allows the both 11, 12
The space is sealed and sufficient liquid tightness is obtained. Also, both 1
Since 1 and 12 can be joined simply by screwing the male and female screw portions 20a and 21a, the assembling work becomes extremely easy.
第６図は本考案の第４実施例を示し、これは第１実施例
の構成を前提としてベアリング１２とポンプボディ１１
との外側に補強部材３０を設けたものである。具体的に
は、この補強部材３０は、板金をプレス成形したものが
好ましく、ベアリング１２の自由端部一帯を被覆状態に
嵌合する円筒部３１と、該円筒部３１の一端縁からポン
プボディ１１側へスカート状にした拡開した円錐部３２
と、該円錐部３２の外端部に一体に形成されてポンプボ
ディ１１の上面に溶接固定された円環部３３とから主と
して構成されている。上記円筒部３１は、他端壁３１ａ
の中央に回転軸１４を挿通する挿通孔３１ｂが穿設され
ており、また円錐部３２の外面には、周方向へ等間隔に
複数の凸状リブ３２ｂ…が軸方向へ沿って形成されてい
る。図中３４は円錐部３２の外端部付近に形成された水
抜き孔である。FIG. 6 shows a fourth embodiment of the present invention, which is based on the configuration of the first embodiment and which includes a bearing 12 and a pump body 11.
The reinforcing member 30 is provided outside the and. Specifically, the reinforcing member 30 is preferably formed by pressing a sheet metal, and includes a cylindrical portion 31 that fits the entire free end portion of the bearing 12 in a covered state, and the pump body 11 from one end edge of the cylindrical portion 31. Skirt-shaped flared cone 32 to the side
And an annular portion 33 integrally formed on the outer end of the conical portion 32 and welded and fixed to the upper surface of the pump body 11. The cylindrical portion 31 has the other end wall 31a.
An insertion hole 31b for inserting the rotary shaft 14 is bored in the center of the conical portion 32, and a plurality of convex ribs 32b are formed on the outer surface of the conical portion 32 at equal intervals in the circumferential direction along the axial direction. There is. Reference numeral 34 in the drawing denotes a water drain hole formed near the outer end of the conical portion 32.
したがって、この実施例によれば、補強部材３０によっ
てウォータポンプ全体の剛性が高くなるため、回転軸１
４及びポンプロータ１５の回転などに伴う振動や騒音を
十分に低減でき、特にウォータポンプの先端に例えばフ
ァンカップリング等を装着した場合にも、耐久性を十分
に維持できる。Therefore, according to this embodiment, since the rigidity of the entire water pump is increased by the reinforcing member 30, the rotating shaft 1
4 and the pump rotor 15 can be sufficiently reduced in vibration and noise, and especially when the tip of the water pump is equipped with, for example, a fan coupling, durability can be sufficiently maintained.
尚、上記ポンプボディ１１とベアリング１２との接合手
段は、上記実施例のものに限定されず、ろう付けや接着
材などを用いることも可能であり、その他巾広い手段を
適用することができる。The means for joining the pump body 11 and the bearing 12 to each other is not limited to that in the above embodiment, but brazing, an adhesive material or the like can be used, and other wide means can be applied.
考案の効果 以上の説明で明らかなように、本考案によれば、ポンプ
の組み立て時におけるベアリング外輪の強い緊締力が回
避されて、ベアリングボール等に対する偏荷重の発生が
防止されることは勿論のこと、延長部がポンプボディへ
の固定とメカニカルシールの固定の両方の機能を備えて
いるため、部品点数の増加を防止できる。この結果、ポ
ンプの重量増加が抑制されると共に、製造作業能率の向
上とコストの低廉化が図れる。Effects of the Invention As is clear from the above description, according to the present invention, the strong tightening force of the bearing outer ring during the assembly of the pump is avoided, and the occurrence of an eccentric load on the bearing balls is prevented. In addition, since the extension portion has both the function of fixing to the pump body and the function of fixing the mechanical seal, it is possible to prevent an increase in the number of parts. As a result, an increase in the weight of the pump can be suppressed, the manufacturing work efficiency can be improved, and the cost can be reduced.
しかも、上記円筒部は、軸方向の長さが短くかつ形状も
均一径の単純な円筒形になっているため、該円筒部の絞
り加工作業等も容易であり、製造作業能率がさらに向上
する。Moreover, since the cylindrical portion is a simple cylindrical shape having a short axial length and a uniform diameter, the drawing work of the cylindrical portion is easy and the manufacturing work efficiency is further improved. .
また、円筒部は、ベアリング外輪の外周全体に被嵌する
のではなく、延長部のみに被嵌するため、ポンプ外径を
小さくすることができる。Further, since the cylindrical portion is not fitted over the entire outer periphery of the bearing outer ring but only the extended portion, the pump outer diameter can be reduced.
【図面の簡単な説明】 第１図は本考案に係るウォータポンプの第１実施例を一
部断面して示す平面図、第２図は第１図のＡ矢視図、第
３図は本考案の第２実施例を一部断面して示す平面図、
第４図は本考案の第３実施例を一部断面して示す平面
図、第５図は第４図のＶ−Ｖ線断面図、第６図は本考案
の第４実施例を一部断面して示す平面図、第７図は従来
のウォータポンプを示す平面図である。 １１……ポンプボディ、１２……ベアリング、１２ｂ…
…外輪、１４……回転軸、１５……ポンプロータ、１９
……円筒部、２１……延長部、２２……メカニカルシー
ル。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a plan view showing a partial cross-section of a first embodiment of a water pump according to the present invention, FIG. 2 is a view on arrow A of FIG. 1, and FIG. The top view which shows the 2nd Example of a device in partial cross section,
FIG. 4 is a plan view showing a partial cross-section of a third embodiment of the present invention, FIG. 5 is a cross-sectional view taken along the line VV of FIG. 4, and FIG. 6 is a partial view of the fourth embodiment of the present invention. FIG. 7 is a plan view showing a cross section, and FIG. 7 is a plan view showing a conventional water pump. 11 ... Pump body, 12 ... Bearing, 12b ...
... outer ring, 14 ... rotating shaft, 15 ... pump rotor, 19
…… Cylindrical part, 21 …… Extended part, 22 …… Mechanical seal.
Claims (1)
たポンプロータを回転可能に収納したポンプボディと、
該ポンプボディの後端側に固定されて、内部に上記回転
軸を軸受するベアリングと、ポンプロータとベアリング
との間に介装されて、前記ポンプ室を密封するメカニカ
ルシールとを備えたウォータポンプにおいて、プレス成
形された前記ポンプボディの後端側略中央部に回転軸の
軸方向に沿って折曲された円筒部を形成する一方、上記
ベアリングの外輪の一端部を軸方向へ延長形成すると共
に、該延長部の先端部を上記円筒部の内周面に嵌入固定
し、かつ上記メカニカルシールを延長部の先端部に固定
したことを特徴とするウォータポンプ。1. A pump body in which a pump rotor fixed to one end of a rotary shaft is rotatably housed in an internal pump chamber,
A water pump having a bearing fixed to the rear end side of the pump body and bearing the rotating shaft therein, and a mechanical seal interposed between the pump rotor and the bearing to seal the pump chamber. In the above, a cylindrical portion bent along the axial direction of the rotary shaft is formed in the substantially central portion of the rear end side of the press-molded pump body, while one end portion of the outer ring of the bearing is formed to extend in the axial direction. At the same time, the water pump is characterized in that the tip portion of the extension portion is fitted and fixed to the inner peripheral surface of the cylindrical portion, and the mechanical seal is fixed to the tip portion of the extension portion.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1988046960U JPH0629512Y2 (en) | 1988-04-07 | 1988-04-07 | Water pump |
| KR2019880017008U KR960001238Y1 (en) | 1988-04-07 | 1988-10-19 | Water pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1988046960U JPH0629512Y2 (en) | 1988-04-07 | 1988-04-07 | Water pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01149594U JPH01149594U (en) | 1989-10-17 |
| JPH0629512Y2 true JPH0629512Y2 (en) | 1994-08-10 |
Family
ID=12761849
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1988046960U Expired - Lifetime JPH0629512Y2 (en) | 1988-04-07 | 1988-04-07 | Water pump |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH0629512Y2 (en) |
| KR (1) | KR960001238Y1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4687051B2 (en) * | 2004-09-27 | 2011-05-25 | アイシン精機株式会社 | Water pump |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59107999U (en) * | 1983-01-10 | 1984-07-20 | アイシン精機株式会社 | Press-molded water pump body |
-
1988
- 1988-04-07 JP JP1988046960U patent/JPH0629512Y2/en not_active Expired - Lifetime
- 1988-10-19 KR KR2019880017008U patent/KR960001238Y1/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| KR960001238Y1 (en) | 1996-02-09 |
| KR890021209U (en) | 1989-11-02 |
| JPH01149594U (en) | 1989-10-17 |
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