JPS6346276B2 - - Google Patents
Info
- Publication number
- JPS6346276B2 JPS6346276B2 JP58127288A JP12728883A JPS6346276B2 JP S6346276 B2 JPS6346276 B2 JP S6346276B2 JP 58127288 A JP58127288 A JP 58127288A JP 12728883 A JP12728883 A JP 12728883A JP S6346276 B2 JPS6346276 B2 JP S6346276B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- sliding valve
- casing
- gears
- gear pump
- 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
Links
- 230000037452 priming Effects 0.000 claims description 9
- 229920000049 Carbon (fiber) Polymers 0.000 claims description 5
- 239000004917 carbon fiber Substances 0.000 claims description 5
- 239000000919 ceramic Substances 0.000 claims description 5
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims description 5
- 239000012530 fluid Substances 0.000 claims description 4
- 229920003002 synthetic resin Polymers 0.000 claims description 4
- 239000000057 synthetic resin Substances 0.000 claims description 4
- VGGSQFUCUMXWEO-UHFFFAOYSA-N Ethene Chemical compound C=C VGGSQFUCUMXWEO-UHFFFAOYSA-N 0.000 claims description 3
- 239000005977 Ethylene Substances 0.000 claims description 3
- 239000000463 material Substances 0.000 claims description 3
- PNEYBMLMFCGWSK-UHFFFAOYSA-N aluminium oxide Inorganic materials [O-2].[O-2].[O-2].[Al+3].[Al+3] PNEYBMLMFCGWSK-UHFFFAOYSA-N 0.000 claims description 2
- 229920001577 copolymer Polymers 0.000 claims description 2
- BFKJFAAPBSQJPD-UHFFFAOYSA-N tetrafluoroethene Chemical group FC(F)=C(F)F BFKJFAAPBSQJPD-UHFFFAOYSA-N 0.000 claims description 2
- 239000007788 liquid Substances 0.000 description 28
- 239000000126 substance Substances 0.000 description 5
- 239000002184 metal Substances 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000002378 acidificating effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Landscapes
- Rotary Pumps (AREA)
Description
【発明の詳細な説明】
本発明は、ケーシングの内部室内で一対の歯車
が外接して噛合回転する形式のギヤポンプの改良
に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a gear pump in which a pair of gears mesh and rotate in a circumscribed manner within an internal chamber of a casing.
この種の外接式ギヤポンプは、一般に、歯車の
両側面がケーシング壁ないし固定された側板等で
押さえられていて、歯車の回転に伴つて歯の谷と
ケーシングの内壁との隙間に閉じ込められた液体
がポンプの吐出し側に送り出されて加圧される構
造になつている。しかして、この種のギヤポンプ
にあつては、工作上の点から普通インボリユート
歯形の平歯車が用いられ、歯車の噛合率は１より
大きいから、必らず２組の歯が噛合している期間
があり、従つて、吐出し側の液体の一部が両歯の
隙間に閉じ込められ、再び吸込側に戻される。こ
の閉じ込められた液体は歯車の回転に伴う閉じ込
み容積の変化により圧縮・膨張を行うため大きな
圧力変化が起こる。すなわち、歯と歯の噛合の始
めに閉じ込められた液体の圧力は上昇し、軸荷
重、軸受荷重、軸動力の増大や吐出し量の減少等
の原因となり、噛合の終段では圧力が低下し、キ
ヤビテーシヨンの発生の原因ともなる。加えて、
歯と歯の間にはさまれた液体の圧力は吸込側から
吐出し側でほぼ直線的に上昇するので、歯車の周
辺に働らく横方向の推力により、歯車軸は吐出し
側から吸込側に向つて押圧され、軸荷重ないし軸
受荷重を増大させることになり、この力は吐出し
力が高くなればなるほど大きくなる。 In this type of external gear pump, both sides of the gear are generally held down by a casing wall or a fixed side plate, and as the gear rotates, liquid is trapped in the gap between the tooth valley and the inner wall of the casing. is delivered to the discharge side of the pump and pressurized. However, in this type of gear pump, a spur gear with an involute tooth profile is usually used from a manufacturing standpoint, and since the meshing ratio of the gears is greater than 1, there is always a period when two sets of teeth are meshing. Therefore, part of the liquid on the discharge side is trapped in the gap between both teeth and returned to the suction side. This confined liquid compresses and expands due to changes in the confined volume as the gear rotates, resulting in large pressure changes. In other words, the pressure of the liquid trapped at the beginning of tooth-to-tooth meshing increases, causing an increase in shaft load, bearing load, shaft power, and decrease in discharge amount, and at the end of meshing, the pressure decreases. , which can also cause cavitation. In addition,
The pressure of the liquid sandwiched between the teeth increases almost linearly from the suction side to the discharge side, so the lateral thrust acting around the gear causes the gear shaft to move from the discharge side to the suction side. This force increases the axial load or bearing load, and this force increases as the discharge force increases.
叙上の如き有害な要因の発生ないし不都合を避
けるため、従来は、歯車側面のケーシング壁や側
板等に逃げ溝を吐出し側と吸込側へ向けて設ける
とか、はすば歯車や特殊な歯車を用いるとか、軸
や軸受等の耐荷重部品を大きくかつ堅固に構成す
るとかによつて対策を講じてきた。しかし乍ら、
これらの対策は、いずれも、工作上手数がかかる
と共に、構造が複雑となつたり大型化したりする
といつた欠点があるばかりでなく、軸動力の減少
やポンプ性能それ自体の向上等の点で必ずしも満
足し得なかつたものである。 In order to avoid the occurrence of harmful factors or inconveniences as mentioned above, conventional methods have been to provide relief grooves on the casing wall or side plate of the gear side facing the discharge side and suction side, or to prevent helical gears or special gears Countermeasures have been taken by using large and solid load-bearing parts such as shafts and bearings. However,
All of these countermeasures not only require a lot of workmanship and have the drawbacks of becoming complicated and large in structure, but also have the drawbacks of reducing shaft power and improving the pump performance itself. It was something I couldn't be satisfied with.
のみならず、この種のギヤポンプにあつては、
歯車軸その他の主要構成部品が金属製であるた
め、製造コストが嵩むばかりでなく、酸性の強い
液体その他金属に対し腐蝕性を有する液体の吸い
上げや圧送に適しないという欠点を有していた。 Not only that, but for this type of gear pump,
Since the gear shaft and other main components are made of metal, it not only increases manufacturing costs, but also has the disadvantage that it is not suitable for sucking up or pumping highly acidic liquids or other liquids that are corrosive to metals.
本発明は、叙上の如き欠点ないし不都合な点を
解消すると共に、性能の優秀な外接式ギヤポンプ
を廉価に提供し得るようにしたものである。 The present invention eliminates the above-mentioned drawbacks and inconveniences, and also makes it possible to provide an external gear pump with excellent performance at a low cost.
以下、本発明につきその実施の一例を示した添
付図面を参照して詳細に説明する。 DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail with reference to the accompanying drawings showing an example of its implementation.
第１図及び第２図において、１は外接式スパー
ギヤポンプのケーシングであり、端壁１Ａと周壁
１Ｂとが一体に形成され、その解放側１Ｃには軸
受体２がボルトで連結されており、断面大略８の
字状なる該ケーシングの内部室３内には、駆動軸
４側の歯車５と従動軸６側の歯車７とが外接して
噛合した状態に配置され、駆動軸４は軸受体２に
貫通され、シールされた状態でベアリング８に支
承されている。しかして、この駆動軸４は、軸受
体２から外方に突出する軸端部に連結される電動
機（図示してない）で回転駆動され、駆動軸４に
よつて歯車５，７が回転駆動されると、ケーシン
グ１の吸込口９から内部室３内に導入された液体
は内部室３の壁面、すなわち周壁１Ｂの内壁面と
歯の谷とによつて形成される空間に閉じ込めら
れ、加圧されて吐出し口１０から送出される。 In FIGS. 1 and 2, 1 is a casing of an external spur gear pump, in which an end wall 1A and a peripheral wall 1B are integrally formed, and a bearing body 2 is connected to the open side 1C with bolts. A gear 5 on the drive shaft 4 side and a gear 7 on the driven shaft 6 side are disposed in an internal chamber 3 of the casing, which has a roughly figure-8 cross section, in a state of external contact and meshing. 2 and is supported by a bearing 8 in a sealed state. The drive shaft 4 is rotationally driven by an electric motor (not shown) connected to the shaft end projecting outward from the bearing body 2, and the gears 5 and 7 are rotationally driven by the drive shaft 4. Then, the liquid introduced into the internal chamber 3 from the suction port 9 of the casing 1 is confined in the wall surface of the internal chamber 3, that is, the space formed by the inner wall surface of the peripheral wall 1B and the valleys of the teeth, and is not compressed. It is pressed and sent out from the discharge port 10.
図示の例にあつては、前記した一対の歯車５，
７の両側面とこれら側面とそれぞれ対向する内部
室３の端壁面１１Ａ，１１Ｂとの間の室部分３
Ａ，３Ｂに、それら室部分の断面形状・寸法に適
合した形状・寸法を有する軸受板を兼ねる摺動弁
板１２が各４枚づつ若干のすきまを残した態様で
それぞれ装填されており、それら摺動弁板は、貫
通孔１２′，１２′をそれぞれ有し、それらの貫通
孔に歯車５の駆動軸４及び歯車７の従動軸６の両
軸を挿通することによつてその軸方向に若干摺動
し得るようにそれぞれ支承されている。 In the illustrated example, the pair of gears 5,
7 and the end wall surfaces 11A and 11B of the internal chamber 3 facing each other.
A and 3B are each loaded with four sliding valve plates 12, which also serve as bearing plates, and have a shape and dimensions that match the cross-sectional shape and dimensions of these chambers, leaving a slight gap between them. The sliding valve plate has through holes 12' and 12', respectively, and by inserting both the drive shaft 4 of the gear 5 and the driven shaft 6 of the gear 7 into these through holes, the sliding valve plate can be rotated in the axial direction. Each is supported so that it can slide slightly.
前記摺動弁板１２及び歯車軸４，６ないし歯車
５，７は後述するように、内部室３内の液圧、殊
に吐出し側の吐出し圧力を不断に受けるものであ
り、またケーシングは一種の圧力容器であるか
ら、流体荷重及びこれに伴う機械的荷重に十分耐
え得る機械的強度を有することが必要であり、ま
た、各種の化学的性質をもつ液体の取扱いを可能
ならしめるためには、耐薬品性にも富むものであ
ることが要求される。 As will be described later, the sliding valve plate 12 and the gear shafts 4, 6 or gears 5, 7 are constantly subjected to the hydraulic pressure in the internal chamber 3, especially the discharge pressure on the discharge side, and the casing Since it is a type of pressure vessel, it must have sufficient mechanical strength to withstand the fluid load and the accompanying mechanical load, and it must also be able to handle liquids with various chemical properties. It is also required that the material has high chemical resistance.
これらの要請を考慮に入れて種々実験を試みた
ところ、ケーシング１、軸受体２、歯車５，７及
び摺動弁板１２は、軽くて、強じん性、耐摩耗
性、耐薬品性に富むほか、摺動特性、圧縮特性及
び耐熱性等をも具備している合成樹脂、殊に弗素
樹脂、例えばテトラフルオロエチレン（C2F4）
とエチレン（C2H4）の共重合体に炭素繊維を適
量（例えば、15〜25％）混合したもので製出する
と極めて良好な結果が得られることが判明した。
また、歯車軸４，６については、硬くて、耐摩耗
性、摺動特性、耐薬品性、耐熱性等の点で優れて
いるセラミツクス、例えば99％前後のアルミナを
含有する緻密質のセラミツクスで製出すると極め
て優秀な結果が得られることが判明した。 Taking these requests into consideration, we conducted various experiments and found that the casing 1, bearing body 2, gears 5 and 7, and sliding valve plate 12 are light, strong, and have high wear resistance and chemical resistance. In addition, synthetic resins, especially fluororesins, such as tetrafluoroethylene (C 2 F 4 ), which have sliding properties, compression properties, heat resistance, etc.
It has been found that very good results can be obtained by producing a copolymer of ethylene (C 2 H 4 ) and ethylene (C 2 H 4 ) mixed with an appropriate amount (for example, 15 to 25%) of carbon fiber.
The gear shafts 4 and 6 are made of ceramics that are hard and have excellent wear resistance, sliding properties, chemical resistance, heat resistance, etc., such as dense ceramics containing about 99% alumina. It has been found that excellent results can be obtained when produced.
上述の如く構成された本発明において、駆動軸
４によつて歯車５，７が回転駆動され、液体が吸
込口９から内部室３内に吸い込まれ、吸込側から
吐出し側に送り出される段階になると、加圧され
た液体は両歯車５，７の側面とこれに隣接する摺
動弁板１２との間の僅かなすきまを通つて室部分
３Ａ，３Ｂ内に流入すると共に、該歯車側面とこ
れに隣接する摺動弁板１２との間、各摺動弁板１
２間、各摺動弁板１２と各軸４，６との間、端壁
面１１Ａ，１１Ｂとこれに隣接する摺動弁板１２
との間及び各摺動弁板１２と周壁１Ｂの内壁面と
の間等のすきまに浸入し、そこに液膜を形成する
ので、該隣接摺動弁板１２は他の摺動弁板１２及
びそれらの液膜によつて両歯車５，７の側面に弾
性的に当接される。 In the present invention configured as described above, the gears 5 and 7 are rotationally driven by the drive shaft 4, and the liquid is sucked into the internal chamber 3 from the suction port 9 and sent out from the suction side to the discharge side. Then, the pressurized liquid flows into the chamber portions 3A, 3B through the slight gap between the side surfaces of the gears 5, 7 and the sliding valve plate 12 adjacent thereto, and also flows between the side surfaces of the gears 5, 7 and the sliding valve plate 12 adjacent thereto. Between each sliding valve plate 1 and the adjacent sliding valve plate 12,
2, between each sliding valve plate 12 and each shaft 4, 6, between the end wall surfaces 11A, 11B and the sliding valve plate 12 adjacent thereto.
and between each sliding valve plate 12 and the inner wall surface of the peripheral wall 1B, and forms a liquid film there. The liquid film makes elastic contact with the sides of both gears 5 and 7.
次いで歯と歯の間にはさまれた液体が圧縮さ
れ、その圧力が高められてくると、そこで加圧さ
れた液体の一部は歯車側面の摺動弁板１２及び液
膜に抗して吸込側と吐出し側とに連通する室部分
３Ａ，３Ｂ内に強制流入して逃げこむこととなる
ので、大きな圧力変化の発生が防止され、従つ
て、軸荷重、軸受荷重、軸動力等の増大やキヤビ
テーシヨンの発生を防ぐことができる。また、歯
車の連続回転によつて吐出し圧力が高まつてきた
場合には、吐出し側の圧力液体は歯車５，７に隣
接する摺動弁板１２の吐出し側の部分、すなわ
ち、第２図において右半分の部分にまず作用し、
この部分を液膜に抗して内方、すなわち端壁面１
１Ａ，１１Ｂの方向に押圧してこれを押し開いて
室部分３Ａ，３Ｂ内に強制流入し、次いで、その
吸込側の部分に作用し、その全体を内方に摺動変
位させて該室部分からこれに連通する内部室３の
吸込側に流入するので、吸入側の圧力の相対的な
急速低下はこの吐出し圧力の作用によつて防止さ
れ、吐出し側と吸込側との間における有害な圧力
差の発生が防止される。従つて、これにより、歯
車の周辺に働らく吐出し側から吸込側への横方向
推力は大いに軽減されるので、吐出し圧力が高く
なつてもそれに比例して軸荷重ないし軸受荷重が
増大するようなことはなくなる。 Next, the liquid sandwiched between the teeth is compressed, and as the pressure increases, a part of the pressurized liquid moves against the sliding valve plate 12 on the side of the gear and the liquid film. Since the flow is forced into the chamber portions 3A and 3B that communicate with the suction side and the discharge side and escapes, large pressure changes are prevented from occurring, and the shaft load, bearing load, shaft power, etc. It is possible to prevent the occurrence of enlargement and cavitation. Furthermore, when the discharge pressure increases due to the continuous rotation of the gears, the pressure liquid on the discharge side is transferred to the discharge side portion of the sliding valve plate 12 adjacent to the gears 5 and 7. In Figure 2, it first acts on the right half,
Move this part inward against the liquid film, that is, the end wall surface 1
1A and 11B to force it open and forcefully flow into the chamber parts 3A and 3B, and then act on the suction side part and slide the entire part inward to open the chamber part. Flows into the suction side of the internal chamber 3 communicating with this, so a relative rapid drop in the pressure on the suction side is prevented by the action of this discharge pressure, and harmful substances between the discharge side and the suction side are prevented. This prevents pressure differences from occurring. Therefore, as a result, the lateral thrust acting around the gear from the discharge side to the suction side is greatly reduced, so even if the discharge pressure increases, the shaft load or bearing load increases in proportion to it. This will no longer be the case.
摺動弁板１２は、図示の例では室部分３Ａ，３
Ｂ内に各４枚づつ配設されているが、その数はギ
ヤポンプの大小その他の条件によつて適宜決定さ
れるものであり、また一方の室部分３Ａ内にのみ
所要の数の摺動弁板１２を配設し、他方の室部分
３Ｂ内には単一の部厚い側板等を配置固定したも
のでもほぼ上述の如き作用効果を奏し得るもので
ある。しかして、ケーシング１及び摺動弁板１２
が炭素繊維を適量混合した弗素樹脂で製出される
一方、歯車軸４，６がセラミツクスで製出されて
いる場合には、前記した如きこれら素材の有する
特性、殊にその優れた摺動特性により摺動弁板１
２は圧力変化に対して軽快かつ有効に作動し得る
良好な応答性を有する圧力調整弁として機能し得
るから、上述の如き作用効果は一層高められるこ
とになり、また、歯車、５，７も炭素繊維入りの
弗素樹脂で製出されているものにあつては、歯車
５，７が軸推力を受けて軸方向に移動し、一群の
摺動弁板１２が端壁面１１Ａ又は１１Ｂに押圧さ
れた場合、該摺動弁板１２はその弾性により歯車
５，７を軸推力に抗して押し戻すように作用す
る。この場合、歯車５，７と摺動弁板１２とはい
ずれも良好な摺動特性を有していることに加え
て、該歯車側面と隣接摺動弁板との接触面に存在
する液膜が潤滑液として作用するので、両者間の
接触摩擦は極めて小さい。従つて、両者の接触に
よる発熱量は極めて少なく、歯車５，７の高速回
転が妨げられることもない。 In the illustrated example, the sliding valve plate 12 has chamber portions 3A, 3
Four slide valves are arranged in each chamber part B, but the number is determined appropriately depending on the size of the gear pump and other conditions, and the required number of slide valves are installed only in one chamber part 3A. Even if the plate 12 is disposed and a single thick side plate or the like is arranged and fixed in the other chamber portion 3B, substantially the same effects as described above can be achieved. Therefore, the casing 1 and the sliding valve plate 12
is made of fluororesin mixed with an appropriate amount of carbon fiber, while gear shafts 4 and 6 are made of ceramics. Sliding valve plate 1
Since gear 2 can function as a pressure regulating valve with good responsiveness that can operate easily and effectively against pressure changes, the above-mentioned effects are further enhanced. In the case of a valve made of fluororesin containing carbon fiber, the gears 5 and 7 move in the axial direction under the axial thrust, and the group of sliding valve plates 12 is pressed against the end wall surface 11A or 11B. In this case, the sliding valve plate 12 acts to push back the gears 5, 7 against the axial thrust due to its elasticity. In this case, in addition to the fact that both the gears 5 and 7 and the sliding valve plate 12 have good sliding characteristics, a liquid film exists on the contact surface between the side surface of the gear and the adjacent sliding valve plate. acts as a lubricating liquid, so the contact friction between the two is extremely small. Therefore, the amount of heat generated by contact between the two is extremely small, and the high speed rotation of the gears 5 and 7 is not hindered.
加えて、軸受体２をもケーシング１と同様の素
材で製出する一方、シールリング部材１３、パツ
キング板１４等を耐久性、耐薬品性等に富む弗素
樹脂の如き合成樹脂で製出した場合には、液体が
触れる部分に金属が全く使用されていない、プラ
スチツクギヤポンプと称し得べきギヤポンプが作
られることになり、油その他粘性の比較的高い液
体、酸性の強い液体、低温又は高温液体その他各
種の液体の吸い上げ、圧送等に汎用し得るギヤポ
ンプの提供が可能となるものである。 In addition, while the bearing body 2 is made of the same material as the casing 1, the seal ring member 13, packing plate 14, etc. are made of a synthetic resin such as fluororesin that is highly durable and chemically resistant. A gear pump, which can be called a plastic gear pump, was created in which no metal was used in the parts that came in contact with liquid. This makes it possible to provide a gear pump that can be used for general purposes such as sucking up and pumping liquids.
なお、歯車５，６の片側面とこれに対向する室
部分３Ａ又は３Ｂの端壁面１１Ａ又は１１Ｂとこ
の両面間に装填される複数の摺動弁板１２との間
に残されるべきクリアランスの合計数値は、ポン
プの大きさないし室部分３Ａ，３Ｂの容積の大
小、摺動弁板１２の厚みないし数等によつて異な
つてくるが、実験によれば、歯車側面と端壁面間
の距離が８mmの場合、すきまの合計は0.1〜0.5mm
程度が適当なことが判明している。 In addition, the total clearance that should be left between one side of the gears 5 and 6, the end wall surface 11A or 11B of the chamber portion 3A or 3B opposite thereto, and the plurality of sliding valve plates 12 loaded between these two surfaces. The numerical value varies depending on the size of the pump, the volume of the chamber parts 3A and 3B, the thickness or number of sliding valve plates 12, etc., but according to experiments, the distance between the side surface of the gear and the end wall surface is In the case of 8mm, the total clearance is 0.1~0.5mm
It has been found that the level is appropriate.
図中、１５はケーシング１の上部の駆動歯車５
に面する部位に設けた呼び液吸込口であり、該呼
び液吸込口１５には呼び液タンク（図示してな
い）が供給管（図示してない）を介して連結され
るようになつており、該呼び液吸込口１５を通し
て駆動歯車５に呼び液を直接ふりかける態様で内
部室３に呼び液を供給することができるようにな
つている。 In the figure, 15 is a drive gear 5 on the upper part of the casing 1.
The priming liquid suction port 15 is connected to a priming liquid tank (not shown) via a supply pipe (not shown). The priming liquid can be supplied to the internal chamber 3 by directly sprinkling the priming liquid onto the drive gear 5 through the priming liquid suction port 15.
かようにして、本発明によれば、冒頭に述べた
如き欠点ないし不都合が解消されるばかりでな
く、必要に応じて呼び液を供給してやることがで
きると共に、高い吐出し圧力を維持して運転する
ことのできる高効率で汎用性のある外接式ギヤポ
ンプを廉価に提供することができるものであつ
て、その実益は誠に多大である。 In this way, according to the present invention, not only the drawbacks and inconveniences mentioned at the beginning are solved, but also the priming liquid can be supplied as needed, and the operation can be performed while maintaining a high discharge pressure. It is possible to provide a highly efficient and versatile external gear pump at a low cost, and its practical benefits are truly great.
第１図は本発明に係るギヤポンプの縦断側面
図、第２図は第１図のＡ−Ａ線による断面図、第
３図は軸受部材を兼ねる摺動弁板の端面図であ
る。
図面において、１はケーシング、３は内部室、
３Ａ及び３Ｂは室部分、４は駆動軸、５は駆動歯
車、６は従動軸、７は従動歯車、１１Ａ及び１１
Ｂは内部室の端壁面、１２は軸受部材を兼ねる摺
動弁板、１５は呼び液吸込口である。
FIG. 1 is a longitudinal sectional side view of a gear pump according to the present invention, FIG. 2 is a sectional view taken along line A-A in FIG. 1, and FIG. 3 is an end view of a sliding valve plate that also serves as a bearing member. In the drawings, 1 is the casing, 3 is the internal chamber,
3A and 3B are chamber parts, 4 is a drive shaft, 5 is a drive gear, 6 is a driven shaft, 7 is a driven gear, 11A and 11
B is an end wall surface of the internal chamber, 12 is a sliding valve plate that also serves as a bearing member, and 15 is a priming fluid suction port.
Claims (1)
て噛合回転する形式のギヤポンプにおいて、該一
対の歯車の少なくとも片側面とこれに対向する該
内部室の端壁面との間の室部分に、その室部分の
断面形状・寸法に適合した形状・寸法を有する複
数の軸受部材を兼ねる摺動弁板を若干のすきまを
残した態様で装填すると共に、これら摺動弁板の
貫通孔に歯車の駆動軸及び従動軸の両軸をそれぞ
れ挿通したこと、前記ケーシング、前記一対の歯
車及び前記摺動弁板を適量の炭素繊維を混合した
合成樹脂材でそれぞれ製出したこと、歯車の駆動
軸及び従動軸の両軸をそれぞれセラミツクスで製
出したこと、及び前記ケーシングの上部の駆動歯
車に面する部位に呼び液タンクに連結される呼び
液吸込口を設けたことを特徴とするギヤポンプ。 ２ 合成樹脂が弗素樹脂であることを特徴とする
特許請求の範囲第１項に記載のギヤポンプ。 ３ セラミツクスが99％前後のアルミナを含有す
る緻密質のものであることを特徴とする特許請求
の範囲第１項に記載のギヤポンプ。 ４ 弗素樹脂がテトラフルオロエチレンとエチレ
ンの共重合体であり、15〜20％の炭素繊維を含有
するものであることを特徴とする特許請求の範囲
第１項又は第２項に記載のギヤポンプ。[Claims] 1. In a gear pump of the type in which a pair of gears mesh and rotate externally in an internal chamber of a casing, a gap between at least one side surface of the pair of gears and an end wall surface of the internal chamber opposite thereto. A plurality of sliding valve plates, which also serve as bearing members, having shapes and dimensions that match the cross-sectional shape and dimensions of the chamber are loaded into the chamber, leaving a slight gap, and the sliding valve plates are inserted through the chamber. Both the drive shaft and the driven shaft of the gear are inserted into the holes, the casing, the pair of gears, and the sliding valve plate are each made of a synthetic resin material mixed with an appropriate amount of carbon fiber, and the gear Both the driving shaft and the driven shaft of the casing are made of ceramics, and a priming fluid suction port connected to a priming fluid tank is provided in the upper part of the casing facing the driving gear. gear pump. 2. The gear pump according to claim 1, wherein the synthetic resin is a fluororesin. 3. The gear pump according to claim 1, wherein the ceramic is dense and contains about 99% alumina. 4. The gear pump according to claim 1 or 2, wherein the fluororesin is a copolymer of tetrafluoroethylene and ethylene and contains 15 to 20% carbon fiber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12728883A JPS6019977A (en) | 1983-07-13 | 1983-07-13 | Modification of external contact type gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12728883A JPS6019977A (en) | 1983-07-13 | 1983-07-13 | Modification of external contact type gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6019977A JPS6019977A (en) | 1985-02-01 |
| JPS6346276B2 true JPS6346276B2 (en) | 1988-09-14 |
Family
ID=14956257
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12728883A Granted JPS6019977A (en) | 1983-07-13 | 1983-07-13 | Modification of external contact type gear pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6019977A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6997689B2 (en) * | 2003-02-20 | 2006-02-14 | Honeywell International Inc. | Offset bearing for extended fuel pump life |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4918851A (en) * | 1972-06-16 | 1974-02-19 | ||
| JPS5020206B2 (en) * | 1971-09-10 | 1975-07-12 | ||
| JPS5735648U (en) * | 1980-08-07 | 1982-02-25 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5020206U (en) * | 1973-06-18 | 1975-03-07 |
-
1983
- 1983-07-13 JP JP12728883A patent/JPS6019977A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5020206B2 (en) * | 1971-09-10 | 1975-07-12 | ||
| JPS4918851A (en) * | 1972-06-16 | 1974-02-19 | ||
| JPS5735648U (en) * | 1980-08-07 | 1982-02-25 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6019977A (en) | 1985-02-01 |
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