JPH09280181A - Gear pump - Google Patents
Gear pumpInfo
- Publication number
- JPH09280181A JPH09280181A JP8676996A JP8676996A JPH09280181A JP H09280181 A JPH09280181 A JP H09280181A JP 8676996 A JP8676996 A JP 8676996A JP 8676996 A JP8676996 A JP 8676996A JP H09280181 A JPH09280181 A JP H09280181A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- liquid
- casing
- spiral groove
- gears
- 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.)
- Pending
Links
Landscapes
- Rotary Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、機械効率や容積効
率を有効に高めた送液用のギヤポンプに関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear pump for liquid transfer, which effectively improves mechanical efficiency and volumetric efficiency.
【０００２】[0002]
【従来の技術】この種のギヤポンプは、図５に示すよう
に、ケーシング１に形成したポンプ室２に、駆動軸３に
固着された駆動ギヤ４及び従動軸５に固着された従動ギ
ヤ６を互いに噛合状態で収容するとともに、それらの駆
動軸３及び従動軸５を、ポンプ室２に臨む位置に内設し
た軸受部材７、８に回転可能に支承させることにより構
成される。この配設位置において、両ギヤ４、６の左側
面４ａ、６ａ及び右側面４ｂ、６ｂは、それぞれ側面シ
ール部たる前記軸受部材７の内面７ａと前記軸受部材８
の内面８ａとに近接配置されて、摺動シールされてい
る。駆動軸３は、一端３ａがケーシング１内に位置づけ
られているのに対して、他端３ｂがケーシング１を貫通
して外部に延出させてある。そして、この駆動軸３の他
端３ｂに外部駆動力を付与することにより、両ギヤ４、
６が同期逆回転して、それらの歯が漸次離反する側に設
けられた図示しない吸込口から吸い込んだ液体を、歯溝
と軸受部材内面７ａ、８ａとポンプ室２との間に閉じ込
めて、漸次歯同士が噛合する側に設けられた図示しない
吐出口にまで搬送するという周知のポンプ作用を営み得
るようになっている。2. Description of the Related Art In a gear pump of this type, as shown in FIG. 5, a pump chamber 2 formed in a casing 1 is provided with a drive gear 4 fixed to a drive shaft 3 and a driven gear 6 fixed to a driven shaft 5. The drive shaft 3 and the driven shaft 5 are housed in a meshed state with each other, and are rotatably supported by bearing members 7 and 8 provided at positions facing the pump chamber 2. In this arrangement position, the left side surfaces 4a, 6a and the right side surfaces 4b, 6b of both gears 4, 6 are respectively the inner surface 7a of the bearing member 7 and the bearing member 8 which are the side seal portions.
It is disposed close to the inner surface 8a and is slidingly sealed. The drive shaft 3 has one end 3a positioned inside the casing 1, while the other end 3b extends through the casing 1 to the outside. Then, by applying an external drive force to the other end 3b of the drive shaft 3, both gears 4,
6 reversely rotates in synchronization, and the liquid sucked from a suction port (not shown) provided on the side where the teeth gradually separate from each other is trapped between the tooth groove, the bearing member inner surfaces 7a and 8a, and the pump chamber 2, A well-known pump action of gradually conveying to a discharge port (not shown) provided on the side where the teeth mesh with each other can be performed.
【０００３】ところで、前記ギヤ４、６の左側面４ａ、
６ａと軸受部材内面７ａとの間、また右側面４ｂ、６ｂ
と軸受部材内面８ａとの間には、若干の隙間が設けてあ
り、吐出口側に存在する高圧の液体の一部をこの隙間に
導入して、液による潤滑を行わせるようにしている。加
えて、導入した液体を利用して軸受潤滑を行うために、
軸受部材７、８の内面７ａ、８ａ及び内周面７ｂ、８ｂ
に、図６に示すような軸方向に伸びる潤滑溝７ｃ、８ｃ
を設け、この潤滑溝７ｃ、８ｃに液体を通過させること
によって軸受の潤滑を行っている場合もある。By the way, the left side surfaces 4a of the gears 4 and 6,
6a and the inner surface 7a of the bearing member, and right side surfaces 4b, 6b
There is a slight gap between the bearing member and the inner surface 8a of the bearing member, and a part of the high-pressure liquid existing on the discharge port side is introduced into this gap to allow lubrication by the liquid. In addition, in order to perform bearing lubrication using the introduced liquid,
Inner surfaces 7a, 8a and inner peripheral surfaces 7b, 8b of the bearing members 7, 8
The axially extending lubricating grooves 7c, 8c as shown in FIG.
In some cases, the bearing is lubricated by providing a liquid and passing the liquid through the lubricating grooves 7c and 8c.
【０００４】[0004]
【発明が解決しようとする課題】ところで、この種のギ
ヤポンプとしては、容積効率や機械効率の観点からも、
側面隙間はギヤ４、６の左側面４ａ、６ａ側と右側面４
ｂ、６ｂ側とで均等を保って運転されるのが望ましい。
しかし、ポンプ内部において、駆動軸３に着目すると、
一端３ａが内部に収容されているのに対し、他端３ｂは
ケーシング１外に延出させてあり、一端３ａ側の端面の
みに前記潤滑溝７ｃを通過した液体や他の部材隙間を通
って回り込んだ液体による液圧が作用する。そして、そ
の液圧は駆動軸３の横断面積分に比例したものとなる。
このため、駆動軸３に軸力が発生し、この軸力によって
駆動ギヤ４が駆動軸３の他端３ｂ側へ変位し、この結
果、ギヤ右側面４ｂと対応する軸受部材内面８ａとの隙
間が減少し、逆にギヤ左側面４ａと対応する軸受部材内
面７ａとの隙間が増大して、前者においてギヤ側面ロス
動力が増し、また後者において容積効率が低下するとい
う不都合を招来している。By the way, as a gear pump of this type, in terms of volumetric efficiency and mechanical efficiency,
The side clearances are the left side surfaces 4a, 6a of the gears 4, 6 and the right side surface 4
It is desirable to operate with equality on the sides b and 6b.
However, when focusing on the drive shaft 3 inside the pump,
The one end 3a is housed inside, while the other end 3b is extended to the outside of the casing 1. Only the end surface on the one end 3a side passes through the liquid passing through the lubricating groove 7c or another member gap. The hydraulic pressure due to the circulated liquid acts. The hydraulic pressure becomes proportional to the integral of the cross section of the drive shaft 3.
Therefore, an axial force is generated on the drive shaft 3, and the drive gear 4 is displaced toward the other end 3b side of the drive shaft 3 by this axial force, and as a result, a gap between the right side surface 4b of the gear and the corresponding bearing member inner surface 8a. However, the gap between the left side surface 4a of the gear and the inner surface 7a of the corresponding bearing member increases, which causes an increase in gear side loss power in the former case and a decrease in volumetric efficiency in the latter case.
【０００５】[0005]
【課題を解決するための手段】上記の問題点を解決する
ために、本発明は、ギヤの側面に、渦巻き状の溝を設
け、ギヤが回転することにより積極的に液を軸中心方向
に圧縮しながら取り込むようにしたものである。このた
め、その反力としてギヤが受ける液圧付勢力を利用すれ
ば、駆動ギヤの軸方向変位を解消することができる。In order to solve the above-mentioned problems, the present invention provides a spiral groove on the side surface of a gear, and positively moves the liquid in the axial center direction by rotating the gear. It is designed to be captured while being compressed. Therefore, the axial displacement of the drive gear can be eliminated by using the hydraulic biasing force that the gear receives as its reaction force.
【０００６】[0006]
【発明の実施の形態】本発明のギヤポンプは、一対のギ
ヤを回転軸を介して互いに噛合状態でケーシング内に配
設し、両ギヤの側面をケーシング内部に設定した側面シ
ール部に隣接配置するとともに、少なくとも一方の回転
軸の一端をケーシング内に位置づけ他端をケーシングを
貫通して外部に延出させてなるものにおいて、ケーシン
グを貫通している回転軸に固着されたギヤのその貫通端
側の側面若しくはその側面に対向する側面シール部の内
面に、ギヤの回転に伴って積極的に液を軸中心方向に圧
縮して取り込むための渦巻き状の溝を設けたものであ
る。BEST MODE FOR CARRYING OUT THE INVENTION In the gear pump of the present invention, a pair of gears are arranged in a casing in mesh with each other via a rotary shaft, and the side faces of both gears are arranged adjacent to a side seal part set inside the casing. In addition, at least one rotating shaft has one end positioned in the casing and the other end penetrating the casing to extend to the outside, wherein the penetrating end side of the gear fixed to the rotating shaft penetrating the casing. The side surface or the inner surface of the side surface seal portion facing the side surface is provided with a spiral groove for positively compressing and taking in the liquid in the axial center direction as the gear rotates.
【０００７】このような構成において、取り込まれた液
体が螺旋状の溝に引き込まれて圧縮されながら軸中心に
向かうと、その液体の液圧が上昇し、この液圧がギヤと
側面シール部との間においてその隙間を押し広げようと
する反発力として作用するので、この反発力により、回
転軸の軸力を相殺し、左右の側面隙間を均等な若しくは
それに近いクリアランスに保つことができる。In such a structure, when the taken-in liquid is drawn into the spiral groove and compressed toward the shaft center while being compressed, the hydraulic pressure of the liquid rises, and this hydraulic pressure acts on the gear and the side seal portion. Since it acts as a repulsive force that tends to widen the gap between them, the repulsive force cancels the axial force of the rotating shaft, and the left and right side surface gaps can be maintained at a uniform clearance or a clearance close thereto.
【０００８】[0008]
【実施例】以下、本発明の一実施例を、図１〜図４を参
照して説明する。このギヤポンプは、基本的には図５に
示した従来のものと同様のものである。ケーシング１
は、ポンプ室２を形成するボディ１ａと、このボディ１
ａの両端を蓋封する位置に配設されるリヤカバー１ｂ及
びスタフィングボックス１ｃとから構成されるもので、
前記ポンプ室２に、駆動軸３に固着された駆動ギヤ４及
び従動軸５に固着された従動ギヤ６を互いに噛合状態で
収容するとともに、両ギヤ４、６の左側面４ａ、６ａに
隣接する位置と右側面４ｂ、６ｂに隣接する位置とにそ
れぞれ軸受部材７、８を配設して、これらの軸受部材
７、８の内周７ｂ、８ｂに前記駆動軸３及び従動軸５を
回転可能に軸承している。従動軸５は、全体がケーシン
グ１内に収容されているのに対して、駆動軸３は、一端
３ａがケーシング１内のリヤカバー１ｂ近傍に位置づけ
られ、他端３ｂがケーシング１のスタフィングボックス
１ｃを貫通して外部に延出されている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIGS. This gear pump is basically the same as the conventional one shown in FIG. Casing 1
Is a body 1a forming the pump chamber 2 and the body 1a
It is composed of a rear cover 1b and a stuffing box 1c arranged at positions where both ends of a are sealed.
A drive gear 4 fixed to a drive shaft 3 and a driven gear 6 fixed to a driven shaft 5 are housed in the pump chamber 2 in mesh with each other, and are adjacent to left side surfaces 4a, 6a of both gears 4, 6. Bearing members 7 and 8 are arranged at positions and positions adjacent to the right side surfaces 4b and 6b, respectively, and the drive shaft 3 and the driven shaft 5 can be rotated on inner circumferences 7b and 8b of these bearing members 7 and 8, respectively. Is supported by. The driven shaft 5 is wholly housed in the casing 1, whereas the drive shaft 3 has one end 3a positioned near the rear cover 1b in the casing 1 and the other end 3b in the stuffing box 1c of the casing 1. Is extended to the outside.
【０００９】ところで、前記軸受部材７、８は、その内
面７ａ、８ａが両ギヤ４、６の左側面４ａ、６ａ又は右
側面４ｂ、６ｂを摺動シールする側面シール部としての
機能をも担うものである。すなわち、軸受部材７はその
内面７ａが両ギヤ４、６の左側面４ａ、６ａに対して、
また軸受部材８はその内面８ａが両ギヤ４、６の右側面
４ｂ、６ｂに対してそれぞれ一定の側面隙間を介して近
接するような寸法関係に配設され、その側面隙間に吐出
口側に存在する高圧の液体の一部を導入して摺動面を潤
滑しながらギヤ４、６の歯溝を当該軸受部材内面７ａ、
８ａとポンプ室内周面面とによって閉止するように構成
される。また、導入した液体を利用して軸受潤滑を行う
ために、軸受部材７、８の内周７ｂ、８ｂに軸方向に沿
って潤滑溝７ｃ、８ｃが設けられ、これらの潤滑溝７
ｃ、８ｃに液体を通過させることによって軸受部材７、
８の焼付を防止するようにしている。By the way, the bearing members 7 and 8 also have a function as a side surface seal portion whose inner surfaces 7a and 8a slidably seal the left side surfaces 4a and 6a or the right side surfaces 4b and 6b of both gears 4 and 6, respectively. It is a thing. That is, the bearing member 7 has its inner surface 7a with respect to the left side surfaces 4a and 6a of both gears 4 and 6,
Further, the bearing member 8 is arranged in such a dimensional relationship that the inner surface 8a thereof is close to the right side surfaces 4b and 6b of both gears 4 and 6 with a certain side surface clearance therebetween, and the side surface clearance is provided on the discharge port side. While introducing a part of the existing high-pressure liquid to lubricate the sliding surface, the tooth grooves of the gears 4 and 6 are formed on the inner surface 7a of the bearing member.
8a and the inner peripheral surface of the pump chamber are configured to be closed. Further, in order to perform bearing lubrication using the introduced liquid, lubricating grooves 7c and 8c are provided in the inner circumferences 7b and 8b of the bearing members 7 and 8 along the axial direction.
bearing member 7, by passing a liquid through c, 8c,
The seizure of No. 8 is prevented.
【００１０】このような構成において、駆動ギヤ３の延
出端３ｂから外部駆動力が付与れると、両ギヤ４、６が
同期逆回転してポンプ作用を営むものとなるが、既述し
たように駆動軸３の他端３ｂはケーシング１外に延出し
ているのに対し、一端３ａはケーシング１内にあって軸
受潤滑を終えた後の液体や部材隙間を通じた内部もれに
より到達した液体により液圧を受け、その液圧が駆動軸
３の横断面積分に比例して駆動軸３に図中右方向に向か
う軸力を発生させるので、放置すればこの軸力により駆
動ギヤ４が駆動軸３と共に他端３ｂ側へ変位し、機械効
率や容積効率の低下が避け難いものとなる。In such a structure, when an external driving force is applied from the extending end 3b of the drive gear 3, both gears 4 and 6 rotate in a synchronous reverse direction to perform a pumping action, as described above. On the other hand, the other end 3b of the drive shaft 3 extends to the outside of the casing 1, whereas the one end 3a is inside the casing 1 and the liquid after bearing lubrication is completed or the liquid reached by internal leakage through the member gap. Receives a hydraulic pressure, and the hydraulic pressure generates an axial force on the drive shaft 3 in the right direction in the figure in proportion to the integral of the cross-section of the drive shaft 3. Therefore, if left unattended, the drive gear 4 is driven by this axial force. Displacement to the other end 3b side together with the shaft 3 makes it difficult to avoid reduction in mechanical efficiency and volumetric efficiency.
【００１１】そこで、本実施例のギヤポンプは、駆動ギ
ヤ４の右側面４ｂに、図２に網掛けを付して示すよう
に、回転により積極的に液を軸中心方向に圧縮して取り
込むような渦巻き状の溝１０を設けている。この溝１０
は、駆動ギヤ４の外周から中心に向かって回転方向Ｘと
反対方向に渦を巻くように伸びる平面形状をなし、その
溝底は略一定深さを保ち、その溝幅は外周から中心に近
づくほど漸次狭小となるように形成されるもので、外方
端１０ａは図３に示すように駆動ギヤ４の外周面に開口
し、内方端１０ｂは駆動軸３が挿通される孔４ｃの近く
で切り上げられている。つまり、駆動ギヤ４が図中矢印
Ｘ方向に回転するとき、周囲に存在する液体をその慣性
を利用して外方端１０ａから取り込み、軸中心方向へ螺
旋状に移動させる作用を営むものである。その際、この
溝１０は中心に近づくほど横断面積が小さくなる為、液
体は次第に圧縮され、内方端１０ｂにおいて最もその液
圧が上昇する。そして、液体はこの内方端１０ｂから漏
出し、引き続き軸受部材８の内周８ｂに設けた潤滑路８
ｃへと流れ込んでいくのである。Therefore, in the gear pump of this embodiment, the liquid is positively compressed in the axial direction by rotation as shown in FIG. 2 by hatching on the right side surface 4b of the drive gear 4. A spiral groove 10 is provided. This groove 10
Has a planar shape that extends from the outer periphery of the drive gear 4 toward the center so as to spiral in a direction opposite to the rotational direction X, the groove bottom maintains a substantially constant depth, and the groove width approaches the center from the outer periphery. As shown in FIG. 3, the outer end 10a is opened to the outer peripheral surface of the drive gear 4, and the inner end 10b is near the hole 4c through which the drive shaft 3 is inserted. Rounded up. That is, when the drive gear 4 rotates in the direction of the arrow X in the drawing, the liquid existing around the drive gear 4 is taken in from the outer end 10a by utilizing its inertia, and the liquid is spirally moved in the axial center direction. At this time, since the cross-sectional area of the groove 10 becomes smaller as it gets closer to the center, the liquid is gradually compressed and the liquid pressure rises most at the inner end 10b. Then, the liquid leaks out from the inner end 10b, and the lubricating passage 8 provided on the inner circumference 8b of the bearing member 8 continues.
It flows into c.
【００１２】このような構成であると、渦巻き状の溝１
０内において中心に近づくにつれて圧縮された液体の液
圧が駆動ギヤ４と対応する軸受部材８との間でその隙間
を押し広げようとする反発力として作用するので（図４
参照）、この反発力により、駆動軸３の軸変位に起因し
て狭まろうとするギヤ右側面４ｂと軸受部材内面８ａと
の側面隙間を適正な寸法に保ち、この結果、反対側のギ
ヤ側面４ａと軸受部材内面７ａとの側面隙間も適正な寸
法に保って、両クリアランスを略均等なものとすること
ができる。With this structure, the spiral groove 1 is formed.
Since the hydraulic pressure of the compressed liquid approaches the center within 0, it acts as a repulsive force for expanding the gap between the drive gear 4 and the corresponding bearing member 8 (see FIG. 4).
By this repulsive force, the side surface gap between the right side surface 4b of the gear and the inner surface 8a of the bearing member, which tends to become narrow due to the axial displacement of the drive shaft 3, is maintained at an appropriate dimension, and as a result, the side surface on the opposite side The clearance between the side surface of the bearing member 4a and the inner surface 7a of the bearing member can be maintained at an appropriate size, and both clearances can be made substantially equal.
【００１３】このようにして、本実施例のギヤポンプ
は、側面隙間のトータルは従来のものと等しいにもかか
わらず、均等隙間とすることによってポンプの全効率を
有効に向上させ得るものとなる。すなわち、一般理論と
して、ギヤ側面の損失動力は側面隙間に１次反比例する
ことが知られているので、側面隙間が均等な場合の全損
失動力は、一方の側面隙間が他方のそれに比べて著しく
小さい場合の各損失動力の総和よりも遙かに小さくなる
ことが明らかである。このため、ロストルクが著しく低
減され、機械効率の飛躍的な向上が図れるとともに、軸
受部材内面７ａ、８ａの早期磨耗も有効に低減すること
ができるものとなる。加えて、他の一般理論として、側
面からの漏れ量は側面隙間の３乗に比例することが知ら
れているので、側面隙間が均等な場合の全漏れ量は、一
方の側面隙間が他方のそれに比べて著しく大きい場合の
各漏れ量の総和よりも遙かに小さくなることが明らかで
ある。このため、このポンプは同時に高い容積効率を発
揮することができる。これらの効果は、左右の側面隙間
が完全に均等を保ったときに最大となるものである。In this way, the gear pump of this embodiment can effectively improve the overall efficiency of the pump by making the side gaps equal to the conventional ones, even though the total of the side face gaps is equal to the conventional one. That is, as a general theory, it is known that the power loss on the side surface of the gear is linearly inversely proportional to the side surface clearance. Therefore, the total loss power when the side surface clearance is equal is significantly higher than that of the other side surface clearance. It is clear that it is much smaller than the sum of each loss power when it is small. Therefore, the loss torque is remarkably reduced, the mechanical efficiency is dramatically improved, and the early wear of the bearing member inner surfaces 7a, 8a can be effectively reduced. In addition, as another general theory, it is known that the amount of leakage from the side surface is proportional to the cube of the side surface clearance, so the total amount of leakage when the side surface clearance is equal is It is clear that it is much smaller than the sum of the leakage amounts when it is significantly larger. Therefore, this pump can exhibit high volume efficiency at the same time. These effects are maximized when the left and right side surface gaps are completely even.
【００１４】なお、上記実施例では渦巻き状の溝の溝深
さを一定とし、溝幅のみをギヤ外周から軸心に向かって
漸次狭小となるように構成したが、溝深さもギヤ外周か
ら軸心に向かって漸次浅くなるように構成すれば、溝断
面積の変化が大きくなり、より顕著な効果を得ることが
できる。このような構成は、ギヤ外周から軸外周までの
距離が短いポンプにおいて特に有効となるものである。
勿論、溝深さのみの変化によっても溝断面積の変化は実
現できるものである。また、上記実施例では別途の軸受
部材をポンプ内部に備えたギヤポンプを示したが、軸受
が外部にあり、ギヤ側面に対する側面シール部がケーシ
ング内面に設定されているタイプのポンプにおいても、
ギヤとケーシングの間で同様の効果を期待することがで
できる。さらに、上記実施例では渦巻き溝をギヤ側面に
設けた実施例について説明したが、軸受部材やケーシン
グ等の側面シール部側に設けても、相対的に考えれば同
等である。In the above embodiment, the spiral groove has a constant groove depth, and only the groove width is gradually narrowed from the outer circumference of the gear toward the shaft center. If it is configured so that it gradually becomes shallower toward the center, the change in groove cross-sectional area becomes large, and a more remarkable effect can be obtained. Such a configuration is particularly effective for a pump having a short distance from the outer circumference of the gear to the outer circumference of the shaft.
Of course, it is possible to change the groove cross-sectional area by changing only the groove depth. Further, in the above embodiment, the gear pump provided with a separate bearing member inside the pump is shown, but also in the type of pump in which the bearing is outside and the side seal portion for the gear side surface is set on the inner surface of the casing,
A similar effect can be expected between the gear and the casing. Further, in the above-described embodiment, the embodiment in which the spiral groove is provided on the side surface of the gear has been described.
【００１５】[0015]
【発明の効果】本発明は、以上説明したような形態で実
施され、以下に記載されるような効果を奏する。すなわ
ち、本発明のギヤポンプは、渦巻き状の溝をギヤ側面に
設けることにより、液体を圧縮してそのギヤ側面に側面
隙間のアンバランスを防止する液圧付勢力を作用させる
ことができるので、容積効率並びに機械効率すなわち全
効率のよいギヤポンプを提供することができる。The present invention is embodied in the form described above and has the following effects. That is, in the gear pump of the present invention, by providing a spiral groove on the side surface of the gear, it is possible to compress the liquid and apply a hydraulic biasing force to the side surface of the gear to prevent the imbalance of the side surface gap. It is possible to provide a gear pump with high efficiency and mechanical efficiency, that is, total efficiency.
【００１６】また、従来では吐出側の圧力を利用してギ
ヤ側面や軸の潤滑を行ってきたため、吐出圧力が低圧で
ある場合には適正な潤滑が行えない場合があったが、本
発明では、ギヤの回転により液を積極的に取り込んで圧
縮するものであるため、吐出圧力が比較的低圧である場
合にも軸受部分に適切に液体を送り込んで良好な軸受潤
滑を行わせる効果が期待できる。Further, conventionally, since the side surface of the gear and the shaft are lubricated by utilizing the pressure on the discharge side, there is a case where proper lubrication cannot be performed when the discharge pressure is low, but in the present invention. Since the rotation of the gear positively takes in the liquid and compresses it, an effect can be expected that the liquid is appropriately sent to the bearing portion to perform good bearing lubrication even when the discharge pressure is relatively low. .
【図面の簡単な説明】[Brief description of drawings]
【図１】本発明の一実施例を示す全体縦断面図。FIG. 1 is an overall vertical sectional view showing one embodiment of the present invention.
【図２】同実施例の駆動ギヤの側面を示す図。FIG. 2 is a diagram showing a side surface of a drive gear of the embodiment.
【図３】同実施例における渦巻き状の溝の構造及び作用
説明図。FIG. 3 is an explanatory view of the structure and action of a spiral groove in the embodiment.
【図４】同実施例において駆動ギヤに掛かる液圧付勢力
の関係を示す図。FIG. 4 is a diagram showing a relationship between hydraulic pressure urging forces applied to drive gears in the embodiment.
【図５】従来例を示す全体断面図。FIG. 5 is an overall sectional view showing a conventional example.
【図６】同従来例の軸受部材を示す斜視図。FIG. 6 is a perspective view showing a bearing member of the conventional example.
３…駆動軸 ３ａ…一端 ３ｂ…他端 ４…駆動ギヤ ５…従動軸 ６…従動ギヤ ７ａ、８ａ…側面シール部（軸受部材内面） １０…渦巻き状の溝 3 ... Drive shaft 3a ... One end 3b ... The other end 4 ... Drive gear 5 ... Driven shaft 6 ... Driven gears 7a, 8a ... Side seal part (bearing member inner surface) 10 ... Spiral groove
Claims (1)
態でケーシング内に配設し、両ギヤの側面をケーシング
内部に設定した側面シール部に隣接配置するとともに、
少なくとも一方の回転軸の一端をケーシング内に位置づ
け他端をケーシングを貫通して外部に延出させてなるも
のにおいて、 ケーシングを貫通している回転軸に固着されたギヤのそ
の貫通端側の側面若しくはその対向位置にある側面シー
ル部の内面に、ギヤの回転に伴って積極的に液を軸中心
方向に圧縮して取り込むための渦巻き状の溝を設けたこ
とを特徴とするギヤポンプ。1. A pair of gears are arranged in a casing in mesh with each other via a rotary shaft, and side surfaces of both gears are arranged adjacent to a side seal portion set inside the casing.
In one in which one end of at least one rotating shaft is located inside the casing and the other end extends through the casing to the outside, a side surface of the gear fixed to the rotating shaft passing through the casing on the penetrating end side Alternatively, a gear pump characterized in that a spiral groove for positively compressing and taking in the liquid in the axial direction along with the rotation of the gear is provided on the inner surface of the side surface seal portion at the opposite position.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8676996A JPH09280181A (en) | 1996-04-09 | 1996-04-09 | Gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8676996A JPH09280181A (en) | 1996-04-09 | 1996-04-09 | Gear pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09280181A true JPH09280181A (en) | 1997-10-28 |
Family
ID=13895967
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8676996A Pending JPH09280181A (en) | 1996-04-09 | 1996-04-09 | Gear pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09280181A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002242851A (en) * | 2001-02-16 | 2002-08-28 | Bridgestone Corp | Gear pump for rubber extrusion |
| CN102348897A (en) * | 2009-03-12 | 2012-02-08 | 罗伯特·博世有限公司 | Hydraulic toothed wheel machine |
| WO2015129256A1 (en) * | 2014-02-25 | 2015-09-03 | Seiko Epson Corporation | Gear pump and image recording apparatus |
| EP3120027A4 (en) * | 2014-03-21 | 2017-12-06 | Imo Industries Inc. | Gear pump with end plates or bearings having spiral grooves |
-
1996
- 1996-04-09 JP JP8676996A patent/JPH09280181A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002242851A (en) * | 2001-02-16 | 2002-08-28 | Bridgestone Corp | Gear pump for rubber extrusion |
| CN102348897A (en) * | 2009-03-12 | 2012-02-08 | 罗伯特·博世有限公司 | Hydraulic toothed wheel machine |
| JP2012519798A (en) * | 2009-03-12 | 2012-08-30 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Hydraulic gear machine |
| WO2015129256A1 (en) * | 2014-02-25 | 2015-09-03 | Seiko Epson Corporation | Gear pump and image recording apparatus |
| EP3120027A4 (en) * | 2014-03-21 | 2017-12-06 | Imo Industries Inc. | Gear pump with end plates or bearings having spiral grooves |
| US10323636B2 (en) | 2014-03-21 | 2019-06-18 | Circor Pumps North America, Llc | Gear pump with end plates or bearings having spiral grooves |
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