JPH0515592Y2

JPH0515592Y2 -

Info

Publication number: JPH0515592Y2
Application number: JP12440686U
Authority: JP
Priority date: 1986-08-12
Filing date: 1986-08-12
Publication date: 1993-04-23
Anticipated expiration: 2001-08-12
Also published as: JPS6331273U

Description

【考案の詳細な説明】［産業上の利用分野］本考案は歯車ポンプの内部に配されるシール材
の形状に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to the shape of a sealing material disposed inside a gear pump.

［従来の技術］歯車の側面と該歯車を内蔵するケースの内面と
の間に油膜を介して歯車側面と接する側板を設
け、この側板とケースとの間に高圧領域と低圧領
域を区分するシール板（ガスケツト）入れて、側
板が油圧的に歯車側面に一定の力で押しつけられ
るようにしたプレツシヤーローテイング式の高圧
歯車ポンプがある。この種の歯車ポンプのシール
材の形状は、ポンプの性能に大きく影響するの
で、できるだけ高性能が得られるよう種々工夫が
こらされているが、必ずしも満足できるものが得
られていないのが現状である。[Prior Art] A side plate that contacts the side surface of the gear via an oil film is provided between the side surface of the gear and the inner surface of the case housing the gear, and a seal is provided between the side plate and the case to separate a high-pressure area and a low-pressure area. There is a pressure rotating type high-pressure gear pump in which a plate (gasket) is inserted so that the side plate is hydraulically pressed against the side of the gear with a constant force. The shape of the sealing material in this type of gear pump has a large effect on the performance of the pump, so various efforts have been made to obtain the highest possible performance, but the current situation is that it is not always possible to achieve a satisfactory result. be.

例えば第５図に示すような断面円形のものは、
シール代を確保するためにツブシ代が大きくな
り、歯車側面への側板押付け力（プリロード）が
大きくなつてトルク損失が増大するという欠点を
もつていた。また、第６図に示すような断面角形
のものでも、中間圧部分が大きく高圧領域と低圧
領域の区分精度が悪いという問題点があるほか、
繰返し負荷に対しスキマからのはみ出しを防ぐた
めバツクアツプ用の補強部品Ｐを必要とすること
が多く、また、第７図に示すような端部の亀裂Ｃ
が生じることが多かつた。 For example, the one with a circular cross section as shown in Figure 5,
In order to secure the sealing allowance, the bushing allowance becomes large, and the pressing force (preload) of the side plate against the side surface of the gear becomes large, resulting in an increase in torque loss. In addition, even with a rectangular cross section as shown in Fig. 6, there is a problem that the intermediate pressure area is large and the accuracy of dividing the high pressure area and the low pressure area is poor.
A reinforcing part P for backup is often required to prevent it from protruding from the gap under repeated loads, and cracks C at the ends as shown in Figure 7 are often required.
often occurred.

そこで本考案は、プリロードが小さく、高圧領
域と低圧領域の区分精度が高く、しかも繰返し負
荷に強いシール材を提供することを目的としてい
る。 Therefore, an object of the present invention is to provide a sealing material that has a small preload, has high accuracy in dividing high-pressure regions and low-pressure regions, and is resistant to repeated loads.

［問題点を解決するための手段］上記問題点を解決するため本考案は次のような
構成を採用した。[Means for Solving the Problems] In order to solve the above problems, the present invention employs the following configuration.

すなわち、本考案にかかる歯車ポンプのシール
は、歯車ポンプの歯車とケースとの間にあつて油
膜をへだてて歯車の側面と接する側板のケース側
の側面とケース内面との間に介装され、高圧領域
と低圧領域とを区分するシール材であつて、両端
部が歯車の外形に沿う二つの円弧を組み合わせた
３の字状に形成されるとともに、この中間部は高
圧領域側が低く低圧領域側が高い概略Ｌ字状の断
面形状を有し、かつ、その両端部は中間部よりも
幅が広く、その幅方向の中央部に高圧領域に連通
する凹部が形成された概略Ｕ字状の断面形状を有
することを特徴としている。 That is, the gear pump seal according to the present invention is interposed between the case-side side surface of the side plate that is in contact with the side surface of the gear and the inner surface of the case by separating an oil film between the gear and the case of the gear pump, It is a sealing material that separates a high pressure area and a low pressure area, and both ends are formed in a figure 3 shape combining two circular arcs that follow the outer shape of the gear, and the middle part is lower on the high pressure area side and lower on the low pressure area side. A roughly U-shaped cross-sectional shape that has a tall, roughly L-shaped cross-sectional shape, whose both ends are wider than the middle part, and where a recess that communicates with the high-pressure region is formed in the center in the width direction. It is characterized by having the following.

［作用］中間部の断面形状が高圧側に低く低圧側に高い
Ｌ字状に形成されているので、シール材が側板と
ケースに高圧で押し付けられ、効果的なシールが
行なわれる。また、シール材がＬ字状に切り欠か
れているので、中間圧部の幅がその分だけ狭くな
り、高圧・低圧の区分精度が向上する。さらに、
端部がＵ字状に形成されており、その凹部に高圧
が導かれるので、端部が側板とシール材の隙間方
向と直角な方向に押し付けられる結果、端部のハ
ミ出しが少ない。また、この凹部が形成されてい
る分だけ長手方向に受ける力が小さくなり、繰返
し負荷に対する強度が高くなる。[Function] Since the cross-sectional shape of the intermediate portion is formed into an L-shape, which is lower on the high-pressure side and higher on the low-pressure side, the sealing material is pressed against the side plate and the case with high pressure, and effective sealing is performed. Furthermore, since the sealing material is cut out in an L-shape, the width of the intermediate pressure section becomes narrower by that amount, and the accuracy of classifying high pressure and low pressure is improved. moreover,
Since the end portion is formed in a U-shape and high pressure is guided to the recessed portion, the end portion is pressed in a direction perpendicular to the direction of the gap between the side plate and the sealing material, resulting in less protrusion of the end portion. Furthermore, the force received in the longitudinal direction is reduced by the amount of the recessed portion, and the strength against repeated loads is increased.

［実施例］第１図乃至第４図本考案の実施例をあらわすも
ので、図示例の歯車ポンプ１は、駆動歯車２と従
動歯車３とをそなえ、これら両歯車２，３がケー
ス５のギヤ室内に収容されている。ケース５はケ
ース本体６とフロントカバー７とで構成され両者
はボルト８，…で固定されている。駆動歯車２の
一方の軸１１は、フロントカバー７の軸穴１３に
ブツシユ１４を介して支承され、他方の軸１５は
ケース本体６の軸受穴１７にブツシユ１４を介し
て支承されている。上記軸１１は、フロントカバ
ー７から外方へ突出し、開口部１９に嵌装された
オイルシール２０によつてシールされている。従
動歯車３の両側の軸２２，２３は、フロントカバ
ー７とケース本体６に穿設された軸受穴２４，２
５にブツシユ１４を介して支承されている。駆動
歯車２および従動歯車３の側面とケース５の内面
との間には側板２７，２８が介装されている。側
板２７，２８には歯車の軸を挿通するための通孔
３１，３２，３３，３４が穿設されている。フロ
ントカバー７側の側板２７は中間部がくびれた形
状に形成され、この部分に高圧側の吐出口３７と
低圧側の吸込口３９とが設けられている。[Embodiment] Figures 1 to 4 show embodiments of the present invention, and the illustrated gear pump 1 includes a driving gear 2 and a driven gear 3, and these gears 2 and 3 are connected to a case 5. It is housed in the gear room. The case 5 is composed of a case body 6 and a front cover 7, both of which are fixed with bolts 8, . . . . One shaft 11 of the drive gear 2 is supported in a shaft hole 13 of the front cover 7 via a bush 14, and the other shaft 15 is supported in a bearing hole 17 of the case body 6 via a bush 14. The shaft 11 projects outward from the front cover 7 and is sealed by an oil seal 20 fitted into the opening 19. The shafts 22 and 23 on both sides of the driven gear 3 are connected to bearing holes 24 and 2 formed in the front cover 7 and the case body 6.
5 via a bushing 14. Side plates 27 and 28 are interposed between the side surfaces of the driving gear 2 and the driven gear 3 and the inner surface of the case 5. The side plates 27 and 28 are provided with through holes 31, 32, 33, and 34 through which the gear shafts are inserted. The side plate 27 on the side of the front cover 7 has a constricted middle portion, and a high pressure side discharge port 37 and a low pressure side suction port 39 are provided in this portion.

側板２７，２８のケース５内面に臨む側面には
シール材嵌着溝４０が形成されており、この溝４
０にシール材であるガスツト４１が嵌装されてい
る。また、ケース５の本体６とフロントカバー７
との接合部には他のシール材４７が設けられてい
る。 A sealing material fitting groove 40 is formed on the side surface of the side plates 27 and 28 facing the inner surface of the case 5.
0 is fitted with a gast 41 which is a sealing material. In addition, the main body 6 of the case 5 and the front cover 7
Another sealing material 47 is provided at the joint portion.

ガスケツト４１は、第３図に示すように３字形
に形成され、その両端部４２，４２は中間部４３
よりも広幅に形成されている。中間部４３の断面
形状は、第４図ａに示すように切欠部４４が形成
され、高圧領域側の高さh₁が低圧領域側の高さh₀
よりも低いＬ字状となつている。また、ガスケツ
トの端部４２の断面形状は、第４図ｂに示すよう
に中央部に凹部４５を有するＵ字状となつてい
る。この凹部４５は高圧領域に連通している。 The gasket 41 is formed in a three-shape as shown in FIG.
It is formed wider than the The cross-sectional shape of the intermediate portion ₄₃ is such that a notch 44 is formed as shown in FIG _.
It has a lower L-shape. The cross-sectional shape of the end portion 42 of the gasket is U-shaped with a recess 45 in the center, as shown in FIG. 4b. This recess 45 communicates with the high pressure region.

この歯車ポンプ１の運転時において、駆動歯車
２がフロントカバー７側から見て左回転（反時計
方向）すると、両歯車２，３の噛合部で発生した
高圧は吐出口３７を通つてガスケツト４１と側板
で形成される溝（前記切欠部４４）および凹部４
５に導入され、ガスケツト４１をケース５側およ
び側板の溝４０の側面４０′に押し付けるととも
に、側板２７，２８を歯車２，３側に押し付け
る。このときの押し付け力Ｆは、Ｆ＝（l₂−l₁）×端部長さ2l₆を除くガスケツト
長さ×圧力＋（l₄−2l₁）×2l₆×圧力で与えられる。 When the gear pump 1 is in operation, when the drive gear 2 rotates to the left (counterclockwise) when viewed from the front cover 7 side, the high pressure generated at the meshing portion of the gears 2 and 3 passes through the discharge port 37 and into the gasket 41. and the groove (the notch 44) formed by the side plate and the recess 4.
5, the gasket 41 is pressed against the case 5 side and the side surface 40' of the groove 40 of the side plate, and the side plates 27 and 28 are pressed against the gears 2 and 3 side. The pressing force F at this time is given by F=(l ₂ −l ₁ )×gasket length excluding end length 2l ₆ ×pressure+(l ₄ −2l ₁ )×2l ₆ ×pressure.

一方、歯車の歯底とケース５とで囲まれた領域
が高圧になつているので、歯車２，３の側面にも
側板２７，２８を押し返す力F′が働いている。Ｆ
＝F′のとき側板はフロートし、Ｆ＞F′のとき歯車
側面に押し付けられる。Ｆ−F′の値が小さいほど
ロストルクが小さくなる。図示例のガスケツト４
１は、l₁の寸法が小さく、中間圧エリヤ（Ｍ）が
狭いので高圧低圧の区分精度が高くなつている。
また、l₁が小さいのでプリロードも小さくなり、
ロストルクを更に小さくすることができる。しか
も（l₂−l₁）×圧力の大きさの力でガスケツト４１
を側板とケース５のスキマと直角な方向に押し付
けているので、上記スキマ方向の力が作用しても
ガスケツト４１がスキマ側へはみ出しにくい。 On the other hand, since the area surrounded by the tooth bottom of the gear and the case 5 is under high pressure, a force F' that pushes back the side plates 27 and 28 also acts on the side surfaces of the gears 2 and 3. F
When =F', the side plate floats, and when F>F', it is pressed against the side of the gear. The smaller the value of F-F', the smaller the loss torque. Gasket 4 in the illustrated example
1 has a small dimension l ₁ and a narrow intermediate pressure area (M), so the high pressure and low pressure classification accuracy is high.
Also, since l ₁ is small, the preload is also small,
Loss torque can be further reduced. _Moreover , the gasket ₄₁ is
Since the gasket 41 is pressed in a direction perpendicular to the gap between the side plate and the case 5, even if a force in the direction of the gap is applied, the gasket 41 is unlikely to protrude toward the gap.

一方、ガスケツト４１の端部４２では、Ｕ字状
の中央部の凹部４５に高圧が作用し、前記と同様
にガスケツト４１をケース５側に押し付ける。端
部にこの凹部４５があるため、ガスケツトのl₂か
らl₄に広くなる部分（Ｑ）におけるガスケツトが
長手方向に受ける力がこの凹部４５がない場合に
比べて小さくなり、かつ、（l₄−2l₁）×l₆×圧力、
の力でケース５の方向に押付けられるので、この
部分における繰返し負荷に対する耐久性が向上す
るのである。 On the other hand, at the end 42 of the gasket 41, high pressure acts on the U-shaped central recess 45, pressing the gasket 41 against the case 5 in the same manner as described above. Because this recess 45 is provided at the end, the force that the gasket receives in the longitudinal direction at the part (Q) where the gasket widens from l ₂ to l ₄ is smaller than in the case where there is no recess 45, and (l ₄ −2l ₁ ) × l ₆ × pressure,
Since it is pressed in the direction of the case 5 with a force of , the durability of this part against repeated loads is improved.

［考案の効果］以上の説明から明らかなように、本考案にかか
る歯車ポンプのシール材は、すぐれたシール性が
得られるとともに、シール長さに対する歯車側面
への押付け力（プリロード）を小さくすることが
できるので歯車ポンプのトルク効率を向上させる
ことができるようになつた。また、このガスケツ
ト４１は、耐久性にすぐれたものであり、バツク
アツプ等の補助部品を用いなくてもすむようにな
つた。[Effects of the invention] As is clear from the above explanation, the gear pump sealing material according to the invention provides excellent sealing performance and reduces the pressing force (preload) on the side surface of the gear relative to the seal length. This makes it possible to improve the torque efficiency of gear pumps. Further, this gasket 41 has excellent durability, and it is no longer necessary to use auxiliary parts such as a backup.

[Brief explanation of drawings]

第１図は歯車ポンプのＡ−Ａ断面図、第２図は
そのＢ−Ｂ矢視図、第３図はガスケツトの全体
図、第４図ａ，ｂはそのＸ−Ｘ断面図およびＹ−
Ｙ断面図、第５図は従来品の説明図、第６図は異
なる従来品の説明図であつてａは全体図、ｂは断
面図、第７図はさらに異なる従来品の説明図であ
る。１……歯車ポンプ、２……駆動歯車、３……従
動歯車、５……ケース、２７，２８……側板、４
１……ガスケツト（シール材）、４５……凹部。 Fig. 1 is a sectional view taken along line A-A of the gear pump, Fig. 2 is a view taken along line B-B, Fig. 3 is an overall view of the gasket, and Figs. 4a and b are cross-sectional views taken along line X-X and Y-
Y sectional view, FIG. 5 is an explanatory diagram of a conventional product, FIG. 6 is an explanatory diagram of a different conventional product, where a is an overall view, b is a sectional view, and FIG. 7 is an explanatory diagram of a further different conventional product. . 1... Gear pump, 2... Drive gear, 3... Driven gear, 5... Case, 27, 28... Side plate, 4
1... Gasket (sealing material), 45... Recessed portion.

Claims

[Scope of utility model registration request]

A sealing material that is located between the gear and the case of a gear pump and is interposed between the case-side side of the side plate that contacts the side of the gear and the inner surface of the case to separate the high-pressure area and the low-pressure area by separating an oil film. 3, which combines two arcs whose ends follow the outer shape of the gear.
The middle part has a roughly L-shaped cross-sectional shape, with the high pressure region side being lower and the lower pressure region side being higher. A sealing material for a gear pump, characterized in that it has a generally U-shaped cross-sectional shape with a recess formed in the center that communicates with a high pressure region.