JP3213356U - Internal gear pump - Google Patents

Internal gear pump Download PDF

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JP3213356U
JP3213356U JP2017003891U JP2017003891U JP3213356U JP 3213356 U JP3213356 U JP 3213356U JP 2017003891 U JP2017003891 U JP 2017003891U JP 2017003891 U JP2017003891 U JP 2017003891U JP 3213356 U JP3213356 U JP 3213356U
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bearing
internal gear
gear
end surface
external gear
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遼 西山
遼 西山
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Sumitomo Precision Products Co Ltd
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Abstract

【課題】外歯歯車の端面とハウジングとの間の焼き付きを防止した内接歯車ポンプを提供する。【解決手段】外周面に歯部が形成されるとともに、両端面の中心部に、該両端面から中心軸に沿ってそれぞれ外方に延設された回転軸22を備える外歯歯車20と、内周面に歯部が形成された環状の内歯歯車30と、外歯歯車20及び内歯歯車30を、その歯部の一部が相互に噛み合った状態で収容するハウジング2と、ハウジング2内で外歯歯車20の回転軸22を回転自在に支持する軸受とを備える。外歯歯車20はその両端面に開口し、該開口部が回転軸22の軸線に沿った方向から見て軸受と少なくとも一部重なり合うように穿設された軸受潤滑用貫通孔24を備え、更に、両端面に開口し、同心円である歯部の歯底円、及び軸受の外径と同径の円によって挟まれる領域内に穿設された端面潤滑用貫通孔25を備える。【選択図】図2An internal gear pump that prevents seizure between an end face of an external gear and a housing is provided. An external gear having a tooth portion formed on the outer peripheral surface and having a rotation shaft extending outwardly from the both end surfaces along the central axis at the center of both end surfaces; A housing 2 that accommodates an annular internal gear 30 having teeth on the inner peripheral surface, an external gear 20 and an internal gear 30 in a state in which the teeth are partially engaged with each other, and a housing 2. And a bearing that rotatably supports the rotating shaft 22 of the external gear 20. The external gear 20 is provided with through-holes 24 for bearing lubrication that are opened at both end faces thereof, and the openings are formed so as to at least partially overlap the bearing when viewed from the direction along the axis of the rotary shaft 22. The end face lubrication through-hole 25 is provided in the region sandwiched between the bottom circle of the tooth portion that is concentric and open to both end faces and the same diameter as the outer diameter of the bearing. [Selection] Figure 2

Description

本考案は、歯部の一部が相互に噛み合う外歯歯車及び内歯歯車を備えた内接歯車ポンプに関する。   The present invention relates to an internal gear pump provided with an external gear and an internal gear in which a part of tooth portions mesh with each other.

前記内接歯車ポンプとして、従来、例えば、下記特許文献1に開示されたものが知られている。この内接歯車ポンプは、一体成形されたピニオンギヤ(外歯歯車)及び駆動軸と、ピニオンギヤに外嵌されたリングギヤ(内歯歯車)と、ピニオンギヤ及びリングギヤを収容するフロント側取付体及びエンド側取付体(ハウジング)と、このフロント側取付体及びエンド側取付体のそれぞれに設けられて前記駆動軸を回転自在に支持する前部ベアリング及び後部ベアリングとから構成される。   Conventionally, for example, the internal gear pump disclosed in Patent Document 1 below is known. The internal gear pump includes an integrally formed pinion gear (external gear) and a drive shaft, a ring gear (internal gear) externally fitted to the pinion gear, a front side mounting body and an end side mounting that accommodate the pinion gear and the ring gear. A body (housing), and a front bearing and a rear bearing which are provided on each of the front side mounting body and the end side mounting body and rotatably support the drive shaft.

ピニオンギヤは外周に歯部を備え、一方、リングギヤはピニオンギヤの外径よりも大きい内径を有するとともに、その内周に歯部を備えており、これらピニオンギヤ及びリングギヤは、その一部が噛合した状態で前記エンド側取付体の収容室内に収容され、当該収容室の開口部が前記フロント側取付体によって閉塞されている。また、ピニオンギヤには、駆動軸との境界部分に、一側面から他側面に貫通する小孔が穿設されている。   The pinion gear has teeth on the outer periphery, while the ring gear has an inner diameter that is larger than the outer diameter of the pinion gear and has teeth on the inner periphery. The pinion gear and the ring gear are partially engaged. The end-side attachment body is accommodated in the accommodation chamber, and the opening of the accommodation chamber is closed by the front-side attachment body. The pinion gear is provided with a small hole penetrating from one side surface to the other side surface at a boundary portion with the drive shaft.

斯くして、この内接歯車ポンプによれば、前記収容室内に収容されたピニオンギヤが、外力により、例えば、前部ベアリング側に移動して、当該ピニオンギヤの端面がフロント側取付体に押し付けられても、前記小孔を介して後部ベアリング側から前部ベアリング側に作動油が供給されるので、この作動油によって当該前部ベアリングの焼き付きが防止される。逆に、ピニオンギヤが後部ベアリング側に移動して、ピニオンギヤの端面がエンド側取付体に押し付けられても、前記小孔を介して前部ベアリング側から後部ベアリング側に作動油が供給され、この作動油によって当該後部ベアリングの焼き付きが防止される。   Thus, according to this internal gear pump, the pinion gear housed in the housing chamber is moved, for example, to the front bearing side by an external force, and the end surface of the pinion gear is pressed against the front mounting body. In addition, since hydraulic oil is supplied from the rear bearing side to the front bearing side through the small hole, seizure of the front bearing is prevented by this hydraulic oil. Conversely, even if the pinion gear moves to the rear bearing side and the end surface of the pinion gear is pressed against the end mounting body, hydraulic oil is supplied from the front bearing side to the rear bearing side through the small hole, and this operation The oil prevents seizure of the rear bearing.

このように、この従来の内接歯車ポンプによれば、前記小孔の作用によって、前部ベアリング及び後部ベアリングの焼き付きが防止されるようになっている。   As described above, according to this conventional internal gear pump, the front bearing and the rear bearing are prevented from being seized by the action of the small hole.

実願昭62−167076号(実開平1−71185号)のマイクロフィルムMicrofilm of Japanese Utility Model Application No. Sho 62-167076 (Japanese Utility Model Application Laid-Open No. 1-71185)

ところで、近年では、当該分野における要請から、より高圧の作動油を出力することができるポンプ、即ち、高圧ポンプの開発が進められている。   By the way, in recent years, a pump capable of outputting higher-pressure hydraulic oil, that is, a high-pressure pump has been developed in response to a request in the field.

ところが、作動油がより高圧になると、ピニオンギヤがその軸線方向に移動してフロント側取付体やエンド側取付体と摺接した際の接触面圧が大きくなるため、当該ピニオンギヤの端面とフロント側取付体やエンド側取付体との間で、油切れによって焼き付きを起こすという問題を生じていた。   However, when the hydraulic oil becomes higher in pressure, the contact surface pressure when the pinion gear moves in the axial direction thereof and comes into sliding contact with the front side mounting body or the end side mounting body increases, so the end surface of the pinion gear and the front side mounting There has been a problem that seizure occurs due to running out of oil between the body and the attachment body on the end side.

本考案は以上の実情に鑑みなされたものであって、外歯歯車の端面とハウジングとの間の焼き付きを防止した内接歯車ポンプの提供を、その目的とする。   The present invention has been made in view of the above circumstances, and an object thereof is to provide an internal gear pump that prevents seizure between the end face of the external gear and the housing.

上記課題を解決するための本考案は、
外周面に歯部が形成されるとともに、両端面の中心部に、該両端面から中心軸に沿ってそれぞれ外方に延設された回転軸を備える外歯歯車と、
内周面に歯部が形成された環状の内歯歯車と、
前記外歯歯車及び内歯歯車を、その前記歯部の一部が相互に噛み合った状態で収容するハウジングと、
前記ハウジング内で、前記外歯歯車の両回転軸をそれぞれ回転自在に支持する軸受とを備えて構成され、
前記外歯歯車は、その両端面に開口し、該開口部が前記回転軸の軸線に沿った方向から見て前記軸受と少なくとも一部重なり合うように穿設された軸受潤滑用の貫通孔を備えた内接歯車ポンプにおいて、
前記外歯歯車は、更に、その両端面に開口し、同心円である前記歯部の歯底円、及び前記軸受の外径と同径の円によって挟まれる領域内に穿設された端面潤滑用の貫通孔を備えた内接歯車ポンプに係る。
The present invention for solving the above problems
Toothed portions are formed on the outer peripheral surface, and external gears each having a rotation shaft extending outwardly from the both end surfaces along the central axis at the center portions of the both end surfaces;
An annular internal gear having teeth formed on the inner peripheral surface;
A housing that accommodates the external gear and the internal gear in a state in which a part of the tooth portion meshes with each other;
A bearing that rotatably supports both rotation shafts of the external gear within the housing;
The external gear includes a through-hole for bearing lubrication that is opened at both end faces thereof, and the opening is formed so as to at least partially overlap the bearing when viewed from the direction along the axis of the rotating shaft. In the internal gear pump,
Further, the external gear is open at both end faces thereof, and is used for end face lubrication drilled in a region sandwiched by a bottom circle of the tooth portion that is a concentric circle and a circle having the same diameter as the outer diameter of the bearing. The present invention relates to an internal gear pump having a through hole.

この内接歯車ポンプでは、ハウジングに収容された外歯歯車が、例えば、外力により、その軸線方向の一方側に移動して、当該外歯歯車の一方側の端面がハウジングの同一方側の内端面に摺接すると、他方側の高圧の作動液体が、前記軸受潤滑用の貫通孔を介して、当該一方側に配設された軸受に供給され、これにより当該一方側の軸受に焼き付きが生じるのが防止される。   In this internal gear pump, the external gear accommodated in the housing is moved to one side in the axial direction by an external force, for example, and the end surface on one side of the external gear is the internal gear on the same side of the housing. When slidably contacted with the end face, the high-pressure working liquid on the other side is supplied to the bearing disposed on the one side via the bearing lubrication through-hole, whereby seizure occurs on the bearing on the one side. Is prevented.

また、前記他方側の高圧の作動液体は、前記端面潤滑用の貫通孔を介して、前記外歯歯車の一方側の端面とハウジングの同一方側の内端面との間にも供給され、これによりこれらの間が潤滑され、同部に焼き付きが生じるのが防止される。   Further, the high-pressure working liquid on the other side is also supplied between the end surface on one side of the external gear and the inner end surface on the same side of the housing via the through hole for end surface lubrication. Therefore, the gap between them is lubricated, and seizure is prevented from occurring in the same part.

逆に、前記外歯歯車が、その軸線方向の他方側に移動して、当該外歯歯車の他方側の端面がハウジングの同他方側の内端面に摺接すると、前記一方側の高圧の作動液体が、前記軸受潤滑用の貫通孔を介して、当該他方側に配設された軸受に供給され、これにより当該他方側の軸受に焼き付きが生じるのが防止される。   Conversely, when the external gear moves to the other side in the axial direction and the end surface on the other side of the external gear slides on the inner end surface on the other side of the housing, the high-pressure operation on the one side is performed. The liquid is supplied to the bearing disposed on the other side through the bearing lubrication through-hole, thereby preventing seizure from occurring on the other side bearing.

また、前記一方側の高圧の作動液体は、前記端面潤滑用の貫通孔を介して、前記外歯歯車の他方側の端面とハウジングの同他方側の内端面との間にも供給され、これによりこれらの間が潤滑され、同部に焼き付きが生じるのが防止される。   Further, the high-pressure working liquid on the one side is also supplied between the end surface on the other side of the external gear and the inner end surface on the other side of the housing via the through hole for end face lubrication. Therefore, the gap between them is lubricated, and seizure is prevented from occurring in the same part.

以上のように、本考案に係る内接歯車ポンプによれば、外歯歯車がその軸線方向に移動しても、前記端面潤滑用の貫通孔を介して、外歯歯車の端面とハウジングの内端面との間に作動液体が供給されて潤滑され、更に、外歯歯車の各端面に作用する圧力差、即ち面圧の差が低減され、これらによって同部に焼き付きが生じるのが防止される。また、軸受には、軸受潤滑用の貫通孔を介して作動液体が供給され、これにより軸受に焼き付きが生じるのが防止される。   As described above, according to the internal gear pump according to the present invention, even if the external gear moves in the axial direction, the end surface of the external gear and the inner surface of the housing are connected via the through hole for end surface lubrication. The working liquid is supplied between the end faces and lubricated, and the pressure difference acting on each end face of the external gear, that is, the difference in the face pressure is reduced, thereby preventing seizure from occurring in the same part. . In addition, the working liquid is supplied to the bearing through a through hole for lubricating the bearing, thereby preventing the bearing from being seized.

また、本考案に係る内接歯車ポンプでは、等角度となる間隔で穿設された複数個の前記軸受潤滑用貫通孔及び端面潤滑用貫通孔を備えているのが好ましい。   Further, the internal gear pump according to the present invention preferably includes a plurality of the bearing lubrication through holes and end face lubrication through holes formed at equal intervals.

このようにすれば、外歯歯車の回転を安定したものとすることができ、振動などの不安定な挙動が生じるのを防止することができる。また、外歯歯車の端面とハウジングの内端面との間、並びに軸受にバランス良く作動液体を供給することができ、これら各部における焼き付きを効果的に防止することができる。   If it does in this way, rotation of an external gear can be stabilized and it can prevent that unstable behaviors, such as vibration, arise. Further, the working liquid can be supplied in a well-balanced manner between the end face of the external gear and the inner end face of the housing and to the bearing, and seizure in these parts can be effectively prevented.

本考案において、前記端面潤滑用貫通孔は、前記歯底円の直径をD、前記軸受の外径をDとしたとき、直径Dが下式の範囲内に在る円上に穿設されているのが好ましい。
0.9(D+D)/2≦D≦1.1×(D+D)/2
In the present invention, the end face lubricating through-hole, the tooth root D 1 the diameter of the circle, when the outer diameter of the bearing and D 2, puncture on a circle diameter D P is in the range of the following formula It is preferable to be provided.
0.9 (D 1 + D 2 ) / 2 ≦ D P ≦ 1.1 × (D 1 + D 2 ) / 2

端面潤滑用貫通孔の配設位置がこの範囲内にあれば、外歯歯車の端面とハウジングの内端面との間の潤滑を良好に行うことができる。   If the arrangement position of the through hole for end face lubrication is within this range, lubrication between the end face of the external gear and the inner end face of the housing can be performed satisfactorily.

また、本考案において、端面潤滑用貫通孔は、その直径dが下式の範囲内に設定されているが好ましい。
0.3(D−D)/2≦d
Further, in the present invention, it is preferable that the diameter d 1 of the end surface through hole for lubrication is set within the range of the following formula.
0.3 (D 1 -D 2 ) / 2 ≦ d 1

端面潤滑用貫通孔の直径dをこの範囲に設定することで、外歯歯車の端面とハウジングの内端面との間の潤滑を良好に行うのに十分な量の作動液体を供給することができる。 The diameter d 1 of the end face lubrication holes By setting this range, is possible to supply a sufficient amount of hydraulic fluid lubrication between the end face and the inner end surface of the housing of the external gear to satisfactorily perform it can.

本考案に係る内接歯車ポンプによれば、外歯歯車がその軸線方向に移動しても、前記端面潤滑用の貫通孔を介して、外歯歯車の端面とハウジングの内端面との間に作動液体が供給されて潤滑され、更に、外歯歯車の各端面に作用する圧力差、即ち面圧の差が低減され、これらによって同部に焼き付きが生じるのが防止される。また、軸受には、軸受潤滑用の貫通孔を介して作動液体が供給され、これにより軸受に焼き付きが生じるのが防止される。   According to the internal gear pump according to the present invention, even if the external gear moves in the axial direction, it is provided between the end face of the external gear and the inner end face of the housing via the through hole for end face lubrication. The working liquid is supplied and lubricated, and further, the pressure difference acting on each end face of the external gear, that is, the difference in surface pressure, is reduced, thereby preventing seizure from occurring in the same part. In addition, the working liquid is supplied to the bearing through a through hole for lubricating the bearing, thereby preventing the bearing from being seized.

本考案の一実施形態に係る内接歯車ポンプの正断面図であり、図2における矢視B−B方向の断面図である。It is a front sectional view of the internal gear pump according to one embodiment of the present invention, and is a sectional view in the direction of arrow BB in FIG. 本実施形態に係る内接歯車ポンプの側断面図であり、図1における矢視A−A方向の断面図である。It is a sectional side view of the internal gear pump which concerns on this embodiment, and is sectional drawing of the arrow AA direction in FIG. 本実施形態に係る外歯歯車を示した側面図であり、図4における矢視E方向の側面図である。It is the side view which showed the external gear which concerns on this embodiment, and is a side view of the arrow E direction in FIG. 本実施形態に係る外歯歯車を示した正断面図であり、図3における矢視C−C方向の断面図である。It is a front sectional view showing an external gear according to the present embodiment, and is a sectional view in the direction of arrow CC in FIG. 本実施形態に係る内接歯車ポンプの効果を説明するための説明図である。It is explanatory drawing for demonstrating the effect of the internal gear pump which concerns on this embodiment. 本実施形態に係る内接歯車ポンプの効果を説明するための説明図である。It is explanatory drawing for demonstrating the effect of the internal gear pump which concerns on this embodiment.

以下、本考案の具体的な実施の形態について、図面を参照しながら説明する。図1及び図2に示すように、本例の内接歯車ポンプ1は、内部に収納室4が形成されたハウジング2と、収納室4内に収納された外歯歯車20及び内歯歯車30とを備える。尚、説明のために便宜上設定した前後方向を図1において図示している。   Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. As shown in FIGS. 1 and 2, the internal gear pump 1 of this example includes a housing 2 in which a storage chamber 4 is formed, and an external gear 20 and an internal gear 30 stored in the storage chamber 4. With. For the sake of explanation, the front-rear direction set for convenience is shown in FIG.

前記ハウジング2は、前方側の端面(前端面)に開口し、断面形状が円形状をした空間を有する前記収納室4が形成された本体3と、この本体3の前端面に液密状に固定されたカバー体10と、前記本体3の後方側の端面(後端面)に固定された後部蓋体9と、前記カバー体10の前側に設けられる前部蓋体14とから構成される。   The housing 2 opens to the front end surface (front end surface), and has a main body 3 in which the storage chamber 4 having a space with a circular cross-section is formed, and a liquid-tight shape on the front end surface of the main body 3. The cover body 10 is fixed, the rear cover body 9 is fixed to the rear end face (rear end face) of the main body 3, and the front cover body 14 is provided on the front side of the cover body 10.

前記外歯歯車20は、外周面に歯部が形成された歯車部21と、この歯車部21の中心部に、その両端面21a,21bから中心軸に沿って後方に延設された回転軸22及び前方に延設された回転軸23とを備える。また、前記内歯歯車30は、内周面に歯部が形成された環状の歯車であり、環内部に外歯歯車20の歯車部21が配設される。   The external gear 20 includes a gear portion 21 having a tooth portion formed on the outer peripheral surface thereof, and a rotation shaft extending rearward from the both end surfaces 21a and 21b along the central axis at the center portion of the gear portion 21. 22 and a rotating shaft 23 extending forward. The internal gear 30 is an annular gear having a tooth portion formed on the inner peripheral surface, and the gear portion 21 of the external gear 20 is disposed inside the ring.

前記本体3は、その中心部に、前記収納室4の内端面4a及び当該本体3の後端面に開口する貫通孔5を備えており、前記収容室4の中心軸は、この貫通孔5の中心軸から偏心した状態となっている。そして、この収納室4内には、前記内歯歯車30が回転自在に嵌め込まれ、更に、歯部の一部が相互に噛み合った状態で、当該内歯歯車30の環内部に前記外歯歯車20の歯車部21が配設されており、この結果、内歯歯車30と外歯歯車20の歯車部21とは相互に偏心した状態で収納室4内に収納されている。また、前記貫通孔5には軸受17が嵌挿され、前記外歯歯車20の回転軸22がこの軸受17に挿通された状態で回転自在に支持されている。   The main body 3 is provided with a through hole 5 opened at the inner end surface 4 a of the storage chamber 4 and a rear end surface of the main body 3 at the center thereof, and the central axis of the storage chamber 4 is the center of the through hole 5. It is in an eccentric state from the central axis. Then, the internal gear 30 is rotatably fitted in the storage chamber 4, and the external gear is placed inside the ring of the internal gear 30 in a state where a part of the tooth portions are meshed with each other. As a result, the internal gear 30 and the gear portion 21 of the external gear 20 are stored in the storage chamber 4 in an eccentric state. A bearing 17 is fitted into the through-hole 5, and a rotating shaft 22 of the external gear 20 is rotatably supported in a state of being inserted into the bearing 17.

前記収納室4の内端面4aには、前記外歯歯車20の歯車部21と内歯歯車30とが噛み合っていない部分に、クレセントと称される三日月状の仕切片6が突設されており、内歯歯車30の歯部内周面が仕切片6の突部に摺接し、前記歯車部21の歯部外周面が仕切片6の凹部に摺接した状態となっている。   On the inner end surface 4a of the storage chamber 4, a crescent-shaped partition piece 6 called a crescent protrudes from a portion where the gear portion 21 of the external gear 20 and the internal gear 30 are not meshed with each other. The inner peripheral surface of the tooth portion of the internal gear 30 is in sliding contact with the protrusion of the partition piece 6, and the outer peripheral surface of the tooth portion of the gear portion 21 is in sliding contact with the concave portion of the partition piece 6.

一方、前記カバー体10は、その中心部に、その前端面及び後端面10aに開口する貫通孔11を備えている。この貫通孔11は、その前方側が後方側よりも大径に形成され、後方の小径部に軸受18が嵌挿され、前記回転軸23がこの軸受18に挿通された状態で回転自在に支持されている。また、回転軸23の軸受18より前方部分は、貫通孔11の大径部に嵌挿されたベアリング15によって回転自在に支持され、更に、このベアリング15よりも前方部分がオイルシール16によってシールされている。尚、前記貫通孔11の大径部は前部蓋体14によって閉塞され、前記オイルシール16はこの前部蓋体14に保持されている。   On the other hand, the cover body 10 is provided with a through-hole 11 that opens at the front end face and the rear end face 10a at the center thereof. The front side of the through hole 11 is formed to have a larger diameter than the rear side, and a bearing 18 is inserted into a rear small diameter portion, and the rotary shaft 23 is inserted in the bearing 18 and is supported rotatably. ing. Further, the front portion of the rotary shaft 23 from the bearing 18 is rotatably supported by a bearing 15 inserted into the large diameter portion of the through hole 11, and the front portion of the bearing 15 is sealed by an oil seal 16. ing. The large-diameter portion of the through hole 11 is closed by the front lid 14, and the oil seal 16 is held by the front lid 14.

また、前記回転軸23は、その前端部にキー23aが設けられており、このキー23aを介して回転軸23と適宜駆動モータの出力軸とが連結され、この駆動モータによって当該回転軸23を回転させることで、外歯歯車20が図2に示した矢示方向に回転する。   The rotary shaft 23 is provided with a key 23a at the front end thereof, and the rotary shaft 23 and an output shaft of a drive motor are appropriately connected via the key 23a, and the rotary shaft 23 is connected by the drive motor. By rotating, the external gear 20 rotates in the direction of the arrow shown in FIG.

前記本体3には、前記仕切片6よりも外歯歯車20の回転方向上流側(以下、単に「上流側」という。)に、前記内壁面4aに開口した弧状の吸込側凹部7が形成されており、また、前記仕切片6よりも前記回転方向下流側(以下、単に「下流側」という。)には、同様に内壁面4aに開口した弧状の吐出側凹部8が形成されている。   The main body 3 is formed with an arcuate suction side recess 7 opened in the inner wall surface 4a on the upstream side in the rotation direction of the external gear 20 (hereinafter simply referred to as “upstream side”) with respect to the partition piece 6. In addition, an arc-shaped discharge-side recess 8 that is similarly open to the inner wall surface 4a is formed on the downstream side in the rotational direction (hereinafter simply referred to as “downstream side”) with respect to the partition piece 6.

これら吸込側凹部7及び吐出側凹部8は、それぞれ外歯歯車20の歯車部21における歯底の経路及び内歯歯車30における歯底の経路に沿って開口しており、吸込側凹部7の開口部は、上流側から下流側に向けて徐々に幅広になった形状を有し、吐出側凹部8の開口部は、下流側から上流側に向けて徐々に幅広になった形状を有する。   The suction-side recess 7 and the discharge-side recess 8 open along the root path in the gear portion 21 of the external gear 20 and the root path in the internal gear 30, respectively. The portion has a shape that gradually widens from the upstream side toward the downstream side, and the opening of the discharge-side concave portion 8 has a shape that gradually widens from the downstream side toward the upstream side.

また、前記カバー体10には、吸込流路12及び吐出流路13が形成されている。吸込流路12は、その一方がカバー体10の一方側面(図1における下面)に開口し、他方がカバー体10の後端面10aに開口している。また、吐出流路13は、その一方がカバー体10の他方側面(図1における上面)に開口し、他方が前記後端面10aに開口している。これら吸込流路12及び吐出流路13の前記後端面10aへの開口部は、外歯歯車20の歯車部21及び内歯歯車30を挟んで、吸込側凹部7及び吐出側凹部8とそれぞれ対向しており、吸込流路12の前記後端面10aへの開口部は、上流側から下流側に向けて徐々に幅広になっており、吐出流路13の前記後端面10aへの開口部は、下流側から上流側に向けて徐々に幅広になっている。   The cover body 10 is formed with a suction channel 12 and a discharge channel 13. One of the suction flow paths 12 opens on one side surface (the lower surface in FIG. 1) of the cover body 10, and the other opens on the rear end surface 10 a of the cover body 10. Further, one of the discharge flow paths 13 is opened on the other side surface (upper surface in FIG. 1) of the cover body 10, and the other is opened on the rear end face 10a. The openings to the rear end face 10a of the suction flow channel 12 and the discharge flow channel 13 are opposed to the suction side concave portion 7 and the discharge side concave portion 8 with the gear portion 21 and the internal gear 30 of the external gear 20 interposed therebetween. The opening to the rear end surface 10a of the suction flow channel 12 is gradually widened from the upstream side toward the downstream side, and the opening to the rear end surface 10a of the discharge flow channel 13 is It gradually becomes wider from the downstream side toward the upstream side.

また、外歯歯車20は、図3及び図4にも示すように、その歯車部21に、両端面21a,21bに開口する2つの軸受潤滑用貫通孔24,24、及び同じく2つの端面潤滑用貫通孔25,25を備えている。そして、軸受潤滑用貫通孔24は、その開口部が前記回転軸22,23の軸線に沿った方向から見て前記軸受17,18と少なくとも一部重なり合うように穿設されている。また、前記端面潤滑用貫通孔25は、同心円である歯車部21の歯底円、及び軸受17,18の外径と同径の円によって挟まれる領域内に穿設されている。また、これら軸受潤滑用貫通孔24,24及び端面潤滑用貫通孔25,25は交互に等角度間隔となるように穿設され、端面潤滑用貫通孔25,25は歯車部21の歯頂部と同じ角度位置に設けられている。   Further, as shown in FIGS. 3 and 4, the external gear 20 has two bearing lubrication through holes 24, 24 opened on both end faces 21 a, 21 b and two end face lubrications. Through-holes 25, 25 are provided. The through hole 24 for bearing lubrication is bored so that the opening thereof overlaps at least partly with the bearings 17 and 18 when viewed from the direction along the axis of the rotary shafts 22 and 23. Further, the end face lubricating through hole 25 is formed in a region sandwiched by a concentric circle at the bottom of the gear portion 21 and a circle having the same diameter as the outer diameter of the bearings 17 and 18. The bearing lubrication through holes 24 and 24 and the end surface lubrication through holes 25 and 25 are alternately drilled at equal angular intervals, and the end surface lubrication through holes 25 and 25 are connected to the tooth crest portion of the gear portion 21. They are provided at the same angular position.

以上の構成を備えた本例の内接歯車ポンプ1によれば、まず、作動油を貯留する適宜タンク内に接続された適宜配管(図示せず)をカバー体10の下面に形成された吸込流路12の開口部に接続するとともに、適宜油圧機器が接続された適宜配管をカバー体10の上面に形成された吐出流路13の開口部に接続し、また、前記回転軸23の前端部に適宜駆動モータを接続した後、当該駆動モータを作動させて外歯歯車20を回転させる。   According to the internal gear pump 1 of the present example having the above-described configuration, first, an appropriate pipe (not shown) connected to an appropriate tank that stores hydraulic oil is formed on the lower surface of the cover body 10. Connected to the opening of the flow channel 12 and connected to an appropriate pipe connected to an appropriate hydraulic device to the opening of the discharge flow channel 13 formed on the upper surface of the cover body 10. After appropriately connecting a drive motor to the motor, the drive motor is operated to rotate the external gear 20.

これにより、外歯歯車20と歯部の一部が噛み合った内歯歯車30に回転力が伝達され、両歯車20,30が偏心した状態で回転し、吸込流路12が形成されている側、即ち、仕切片6よりも上流側では、外歯歯車20の歯部と内歯歯車30の歯部とが漸次離反し、この歯部間の空間が広がることによって吸引作用が生じる。そして、この吸引作用が前記吸込流路12に作用し、前記タンクに接続された配管(図示せず)及びこれに接続した吸込流路12を介して、前記各歯車20,30の歯部間に作動油が吸入される。   As a result, the rotational force is transmitted to the internal gear 30 in which the external gear 20 and a part of the tooth portion mesh with each other, and the gears 20 and 30 rotate in an eccentric state, and the suction flow path 12 is formed. That is, on the upstream side of the partition piece 6, the tooth portion of the external gear 20 and the tooth portion of the internal gear 30 are gradually separated from each other, and the space between the tooth portions is widened to produce a suction action. Then, this suction action acts on the suction flow path 12, and between the tooth portions of the gears 20, 30 through a pipe (not shown) connected to the tank and the suction flow path 12 connected thereto. Hydraulic fluid is inhaled.

そして、このようにして吸い込まれた作動油は、仕切片6の内周側と外周側とに分かれて、吐出流路13が形成されている側、即ち、仕切片6よりも下流側へと移送され、仕切片6よりも下流側においては、各歯車20,30の歯部が漸次接近して歯部間が狭まるため、上流側から移送された作動油が加圧されて、吐出流路13及びこれに接続される配管(図示せず)を介して油圧機器に送られる。   Then, the hydraulic oil sucked in this way is divided into an inner peripheral side and an outer peripheral side of the partition piece 6, and to the side where the discharge flow path 13 is formed, that is, downstream from the partition piece 6. Since the tooth portions of the gears 20 and 30 gradually approach and narrow between the tooth portions on the downstream side of the partition piece 6, the hydraulic oil transferred from the upstream side is pressurized and discharged. 13 and a pipe (not shown) connected to this and sent to the hydraulic equipment.

そして、通常の場合には、外歯歯車20の歯車部21は、その軸方向において、前記収納室4内の中間位置にあり、歯車部21の前端面21bとカバー体10の後端面10aとの間、並びに歯車部21の後端面21aと収容室4の内端面4aとの間にはそれぞれ隙間が形成されている。そして、歯車部21の前端面21bとカバー体10の後端面10aとの間の隙間には、吐出流路13から高圧の作動油が流入して同部を潤滑するとともに、この作動油が更に軸受18に供給されて当該軸受18を潤滑する。また、歯車部21の後端面21aと収容室4の内端面4aとの間の隙間には、吐出側凹部8から高圧の作動油が流入して同部を潤滑するとともに、この作動油が更に軸受17に供給されて当該軸受17を潤滑する。   In a normal case, the gear portion 21 of the external gear 20 is in an intermediate position in the storage chamber 4 in the axial direction, and the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10 A gap is formed between the rear end surface 21a of the gear portion 21 and the inner end surface 4a of the storage chamber 4. Then, high pressure hydraulic oil flows into the gap between the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10 from the discharge flow path 13 to lubricate the same portion. The bearing 18 is supplied to lubricate the bearing 18. In addition, high pressure hydraulic oil flows into the gap between the rear end surface 21a of the gear portion 21 and the inner end surface 4a of the storage chamber 4 from the discharge-side concave portion 8 to lubricate the same portion. The bearing 17 is supplied to lubricate the bearing 17.

斯くして、通常の場合、以上の作用によって、歯車部21の前端面21bとカバー体10の後端面10aとの間、歯車部21の後端面21aと収容室4の内端面4aとの間、軸受17及び軸受18がそれぞれ作動油によって潤滑され、各部における焼き付きが防止される。   Thus, in the normal case, the above action causes the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10 to be between the rear end surface 21a of the gear portion 21 and the inner end surface 4a of the storage chamber 4. The bearing 17 and the bearing 18 are each lubricated by the hydraulic oil, and seizure in each part is prevented.

ところで、本例の内接歯車ポンプ1では、その外歯歯車20の回転軸23に駆動モータ(図示せず)が接続されており、この駆動モータ(図示せず)を介して外力が入力されることによって外歯歯車20がその軸線方向に移動する、或いは、その歯車部21の両端面21a,21bに作用する作動油の圧力差が局所的に大きくなることにより、圧力の大きい側から圧力の小さい側に押付力が働いて、当該外歯歯車20がその軸線方向に移動するといったことが起こり得る。   By the way, in the internal gear pump 1 of this example, a drive motor (not shown) is connected to the rotating shaft 23 of the external gear 20, and external force is input via this drive motor (not shown). As a result, the external gear 20 moves in the axial direction thereof, or the pressure difference of the hydraulic oil acting on the both end faces 21a and 21b of the gear portion 21 is locally increased, so that the pressure is increased from the higher pressure side. It is possible that a pressing force acts on the smaller side of the external gear 20 and the external gear 20 moves in the axial direction.

この場合に、本例の内接歯車ポンプ1では、外歯歯車20がその軸線方向の一方側、例えば、カバー体10側に移動して、その歯車部21の前端面21bがカバー体10の後端面10aに摺接すると、吐出側凹部8から歯車部21の後端面21aと収納室4の内端面4aとの間に供給される高圧の作動油が、端面潤滑用貫通孔25,25を介して歯車部21の前端面21bとカバー体10の後端面10aとの間に供給され、また、軸受潤滑用貫通孔24,24を介して軸受18に供給される。これにより、歯車部21の前端面21bとカバー体10の後端面10aとの間、及び軸受18が作動油によって潤滑され、同部における焼き付きが防止される。   In this case, in the internal gear pump 1 of this example, the external gear 20 moves to one side in the axial direction, for example, the cover body 10 side, and the front end surface 21b of the gear portion 21 is the cover body 10 side. When slidably contacting the rear end surface 10a, high-pressure hydraulic oil supplied from the discharge-side concave portion 8 between the rear end surface 21a of the gear portion 21 and the inner end surface 4a of the storage chamber 4 passes through the end surface lubricating through holes 25, 25. And is supplied between the front end surface 21 b of the gear portion 21 and the rear end surface 10 a of the cover body 10, and is supplied to the bearing 18 through the bearing lubrication through holes 24 and 24. Thereby, between the front-end surface 21b of the gear part 21, and the rear-end surface 10a of the cover body 10, and the bearing 18 are lubricated with hydraulic fluid, and the seizing in the part is prevented.

これとは逆に、外歯歯車20が収納室4の内端面4a側に移動して、歯車部21の後端面21aが収納室4の内端面4aに摺接すると、吐出流路13から歯車部21の前端面21bとカバー体10の後端面10aとの間に供給される高圧の作動油が、端面潤滑用貫通孔25,25を介して歯車部21の後端面21aと収納室4の内端面4aとの間に供給され、また、軸受潤滑用貫通孔24,24を介して軸受17に供給される。これにより、歯車部21の後端面21aと収納室4の内端面4aとの間、及び軸受17が作動油によって潤滑され、同部における焼き付きが防止される。   On the contrary, when the external gear 20 moves to the inner end surface 4 a side of the storage chamber 4 and the rear end surface 21 a of the gear portion 21 slides on the inner end surface 4 a of the storage chamber 4, the gear from the discharge flow path 13 High-pressure hydraulic oil supplied between the front end surface 21 b of the portion 21 and the rear end surface 10 a of the cover body 10 passes through the end surface lubricating through holes 25, 25, so that the rear end surface 21 a of the gear portion 21 and the storage chamber 4 It is supplied between the inner end surface 4 a and the bearing 17 through the bearing lubrication through holes 24 and 24. Thereby, between the rear-end surface 21a of the gear part 21 and the inner end surface 4a of the storage chamber 4, and the bearing 17 are lubricated with hydraulic fluid, and the seizing in the part is prevented.

斯くして、本例の内接歯車ポンプ1によれば、外歯歯車20がその軸線方向に移動しても、前記端面潤滑用貫通孔25,25を介して、歯車部21の後端面21aと収納室4の内端面4aとの間、或いは歯車部21の前端面21bとカバー体10の後端面10aとの間に作動油が供給されてそれぞれ潤滑され、更に、前端面21b及び後端面21aに作用する圧力差、即ち面圧の差が低減され、これらによって同部に焼き付きが生じるのが防止される。また、軸受17,18には、軸受潤滑用貫通孔24,24を介して作動油が供給され、これにより軸受17,18に焼き付きが生じるのが防止される。   Thus, according to the internal gear pump 1 of this example, even if the external gear 20 moves in the axial direction thereof, the rear end surface 21a of the gear portion 21 through the end surface lubricating through holes 25, 25. And the inner end surface 4a of the storage chamber 4 or between the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10 are supplied with hydraulic oil and lubricated, respectively, and further, the front end surface 21b and the rear end surface The pressure difference acting on 21a, that is, the difference in surface pressure, is reduced, thereby preventing seizure from occurring in the same part. The bearings 17 and 18 are supplied with hydraulic fluid through the bearing lubrication through holes 24 and 24, thereby preventing the bearings 17 and 18 from being seized.

また、本例の内接歯車ポンプ1では、軸受潤滑用貫通孔24,24及び端面潤滑用貫通孔25,25を交互に等角度間隔となるように穿設しているので、外歯歯車20の回転を安定したものとすることができ、振動などの不安定な挙動が生じるのを防止することができる。また、歯車部21の後端面21aと収納室4の内端面4aとの間、歯車部21の前端面21bとカバー体10の後端面10aとの間、並びに軸受17,18にバランス良く作動油を供給することができ、これら各部における焼き付きを効果的に防止することができる。   Further, in the internal gear pump 1 of this example, the bearing lubrication through holes 24 and 24 and the end surface lubrication through holes 25 and 25 are alternately drilled at equal angular intervals. Can be made stable, and unstable behavior such as vibration can be prevented. Further, the hydraulic oil is balanced between the rear end surface 21a of the gear portion 21 and the inner end surface 4a of the storage chamber 4, between the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10, and in the bearings 17 and 18. Can be supplied, and seizure in these parts can be effectively prevented.

因みに、本例の内接歯車ポンプ1と、本例の内接歯車ポンプ1から端面潤滑用貫通孔25,25を省略した従来構造の内接歯車ポンプにおいて、外歯歯車20をカバー体10側に移動させた状態で、歯車部21の前端面21bとカバー体10の後端面10aと間の作動油の圧力(歯車部の前側圧力)、歯車部21の後端面21aと収納室4の内端面4aとの間の作動油の圧力(歯車部の後側圧力)及び吐出流路13内の作動油の圧力を測定した結果を図5及び図6に示す。尚、図5は従来構造の内接歯車ポンプの場合であり、図6は本例の内接歯車ポンプ1の場合である。   Incidentally, in the internal gear pump 1 of this example and the internal gear pump of the conventional structure in which the end face lubricating through holes 25 and 25 are omitted from the internal gear pump 1 of this example, the external gear 20 is connected to the cover body 10 side. The hydraulic oil pressure between the front end face 21b of the gear part 21 and the rear end face 10a of the cover body 10 (the front side pressure of the gear part), the rear end face 21a of the gear part 21 and the inside of the storage chamber 4 FIG. 5 and FIG. 6 show the results of measuring the pressure of the hydraulic oil between the end surface 4a (the rear pressure of the gear portion) and the pressure of the hydraulic oil in the discharge passage 13. 5 shows a case of an internal gear pump having a conventional structure, and FIG. 6 shows a case of the internal gear pump 1 of this example.

図5に示すように、従来構造の内接歯車ポンプの場合、外歯歯車20がカバー体10側に移動すると、歯車部21の前側の圧力が低くなり、一方、歯車部21の後側の圧力は高くなって、両者間に差を生じる。これは歯車部21の前端面21bとカバー体10の後端面10aと間に作動油が入流し難くなっていることを示すものであり、この間で焼き付きが生じ易くなっていることが分かる。   As shown in FIG. 5, in the case of the internal gear pump having the conventional structure, when the external gear 20 moves to the cover body 10 side, the pressure on the front side of the gear portion 21 is reduced, while the rear side of the gear portion 21 is The pressure rises, creating a difference between the two. This indicates that it is difficult for hydraulic oil to flow between the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10, and it can be seen that seizure is likely to occur between them.

一方、本例の内接歯車ポンプ1の場合、図6に示すように、外歯歯車20がカバー体10側に移動しても、歯車部21の前側の圧力と、歯車部21の後側の圧力とは略同じ圧力になっており、歯車部21の前端面21bとカバー体10の後端面10aと間にも十分な量の作動油が入流していることが分かる。これにより、歯車部21の前端面21bとカバー体10の後端面10aと間における焼き付きが防止される。   On the other hand, in the case of the internal gear pump 1 of this example, as shown in FIG. 6, even if the external gear 20 moves to the cover body 10 side, the pressure on the front side of the gear portion 21 and the rear side of the gear portion 21 It can be seen that a sufficient amount of hydraulic fluid flows between the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10. Thereby, the seizing between the front end surface 21b of the gear part 21 and the rear end surface 10a of the cover body 10 is prevented.

また、本例の内接歯車ポンプ1では、端面潤滑用貫通孔25,25を歯車部21の歯頂部と同じ角度位置に設けているので、歯車部21の外面と端面潤滑用貫通孔25,25との間の厚さを十分な厚さにすることができ、当該端面潤滑用貫通孔25,25を穿設することによって、歯車部21の強度が低下するのを最小限に押さえることができる。   Further, in the internal gear pump 1 of the present example, the end surface lubrication through holes 25 and 25 are provided at the same angular position as the tooth crest portion of the gear portion 21, so that the outer surface of the gear portion 21 and the end surface lubrication through hole 25, The end face lubrication through holes 25 and 25 can be provided to minimize the reduction in the strength of the gear portion 21. it can.

尚、前記端面潤滑用貫通孔25,25は、前記歯底円の直径をD、軸受17,18の外径をDとして、直径Dが下式の範囲内に在る円上に穿設されているのが好ましい(D,D,Dについては、図3を参照)。
0.9(D+D)/2≦D≦1.1×(D+D)/2
端面潤滑用貫通孔25,25の配設位置がこの範囲内にあれば、歯車部21の前端面21bとカバー体10の後端面10aとの間、及び歯車部21の後端面21aと収容室4の内端面4aとの間の潤滑を良好に行うことができる。
Incidentally, the end face lubrication holes 25 and 25, the tooth root D 1 the diameter of a circle, as D 2 the outer diameter of the bearing 17, on a circle diameter D P is in the range of the following formula preferably it is drilled (for D 1, D 2, D P , see Figure 3).
0.9 (D 1 + D 2 ) / 2 ≦ D P ≦ 1.1 × (D 1 + D 2 ) / 2
If the arrangement positions of the end surface lubricating through holes 25 and 25 are within this range, the front end surface 21b of the gear portion 21 and the rear end surface 10a of the cover body 10, and the rear end surface 21a of the gear portion 21 and the accommodating chamber are provided. The lubrication between the inner end surface 4a and the inner end surface 4a can be performed well.

また、端面潤滑用貫通孔25,25の直径dは下式で表わされる範囲内に設定されているのが好ましい(dについては、図4を参照)。
0.3(D−D)/2≦d
端面潤滑用貫通孔25,25の直径dをこの範囲に設定することで、歯車部21の前端面21bとカバー体10の後端面10aとの間、及び歯車部21の後端面21aと収容室4の内端面4aとの間の潤滑を良好に行うのに十分な量の作動油を供給することができる。
Also, preferably the diameter d 1 of the end face lubrication holes 25, 25 is set in a range represented by the following formula (for d 1, see FIG. 4).
0.3 (D 1 -D 2 ) / 2 ≦ d 1
The diameter d 1 of the end face lubrication holes 25, 25 by setting in this range, between the rear end surface 10a of the front end face 21b and the cover member 10 of the gear portion 21, and a rear end surface 21a of the gear portion 21 accommodated It is possible to supply a sufficient amount of hydraulic fluid to satisfactorily lubricate between the inner end surface 4a of the chamber 4.

また、軸受潤滑用貫通孔24,24の直径dは、下式で表わされる範囲内に設定されているのが好ましい(dについては、図4を参照)。
0.3(D−D)/2≦d
軸受潤滑用貫通孔24,24の直径dをこの範囲に設定することで、軸受17,18の潤滑を良好に行うのに十分な量の作動油を供給することができる。
The diameter d 2 of the bearing lubrication through holes 24, 24 is preferably is set within the range represented by the following formula (for d 2, see FIG. 4).
0.3 (D 1 -D 2 ) / 2 ≦ d 2
The diameter d 2 of the bearing lubrication through holes 24, 24 by setting this range, it is possible to supply a sufficient amount of hydraulic oil to satisfactorily perform the lubrication of the bearings 17, 18.

以上、本考案の一実施形態について説明したが、本考案の採り得る具体的な態様は何らこれに限定されるものではない。   As mentioned above, although one Embodiment of this invention was described, the specific aspect which this invention can take is not limited to this at all.

例えば、上例では、軸受潤滑用貫通孔24,24及び端面潤滑用貫通孔25,25を丸孔としたが、これに限られるものではなく、長孔や角孔など、各種形状の孔を採用することができる。また、それぞれ設ける個数を2個としたが、当然この個数に限られるものではなく、これ以上の個数でも、これ以下の個数であっても良い。   For example, in the above example, the bearing lubrication through holes 24 and 24 and the end surface lubrication through holes 25 and 25 are round holes. However, the present invention is not limited to this, and various shapes of holes such as long holes and square holes may be used. Can be adopted. In addition, although the number of each provided is two, it is naturally not limited to this number, and may be more or less.

1 内接歯車ポンプ
2 ハウジング
3 本体
4 収納室
6 仕切片
7 吸込側凹部
8 吐出側凹部
9 後部蓋体
10 カバー体
12 吸込流路
13 吐出流路
14 前部蓋体
15 ベアリング
16 オイルシール
17 軸受
18 軸受
20 外歯歯車
21 歯車部
22,23 回転軸
24 軸受潤滑用貫通孔
25 端面潤滑用貫通孔
30 内歯歯車
DESCRIPTION OF SYMBOLS 1 Internal gear pump 2 Housing 3 Main body 4 Storage chamber 6 Partition piece 7 Suction side recessed part 8 Discharge side recessed part 9 Rear cover body 10 Cover body 12 Suction flow path 13 Discharge flow path 14 Front cover body 15 Bearing 16 Oil seal 17 Bearing DESCRIPTION OF SYMBOLS 18 Bearing 20 External gear 21 Gear part 22, 23 Rotating shaft 24 Through hole for bearing lubrication 25 Through hole for end face lubrication 30 Internal gear

Claims (4)

外周面に歯部が形成されるとともに、両端面の中心部に、該両端面から中心軸に沿ってそれぞれ外方に延設された回転軸を備える外歯歯車と、
内周面に歯部が形成された環状の内歯歯車と、
前記外歯歯車及び内歯歯車を、その前記歯部の一部が相互に噛み合った状態で収容するハウジングと、
前記ハウジング内で、前記外歯歯車の両回転軸をそれぞれ回転自在に支持する軸受とを備えて構成され、
前記外歯歯車は、その両端面に開口し、該開口部が前記回転軸の軸線に沿った方向から見て前記軸受と少なくとも一部重なり合うように穿設された軸受潤滑用の貫通孔を備えた内接歯車ポンプにおいて、
前記外歯歯車は、更に、その両端面に開口し、同心円である前記歯部の歯底円、及び前記軸受の外径と同径の円によって挟まれる領域内に穿設された端面潤滑用の貫通孔を備えていることを特徴とする内接歯車ポンプ。
Toothed portions are formed on the outer peripheral surface, and external gears each having a rotation shaft extending outwardly from the both end surfaces along the central axis at the center portions of the both end surfaces;
An annular internal gear having teeth formed on the inner peripheral surface;
A housing that accommodates the external gear and the internal gear in a state in which a part of the tooth portion meshes with each other;
A bearing that rotatably supports both rotation shafts of the external gear within the housing;
The external gear includes a through-hole for bearing lubrication that is opened at both end faces thereof, and the opening is formed so as to at least partially overlap the bearing when viewed from the direction along the axis of the rotating shaft. In the internal gear pump,
Further, the external gear is open at both end faces thereof, and is used for end face lubrication drilled in a region sandwiched by a bottom circle of the tooth portion that is a concentric circle and a circle having the same diameter as the outer diameter of the bearing. An internal gear pump comprising a through hole.
等角度となる間隔で穿設された複数個の前記軸受潤滑用貫通孔及び端面潤滑用貫通孔を備えたことを特徴とする請求項1記載の内接歯車ポンプ。   2. The internal gear pump according to claim 1, further comprising a plurality of through holes for bearing lubrication and through holes for end face lubrication that are formed at equiangular intervals. 前記端面潤滑用貫通孔は、前記歯底円の直径をD、前記軸受の外径をDとしたとき、直径Dが下式の範囲内に在る円上に穿設されていることを特徴とする請求項1又は2記載の内接歯車ポンプ。
0.9(D+D)/2≦D≦1.1×(D+D)/2
It said end face lubricating through-hole, D 1 the diameter of the root circle, when the outer diameter of the bearing and D 2, are bored on a circle diameter D P is in the range of the following formula The internal gear pump according to claim 1, wherein the internal gear pump is provided.
0.9 (D 1 + D 2 ) / 2 ≦ D P ≦ 1.1 × (D 1 + D 2 ) / 2
端面潤滑用貫通孔は、前記歯底円の直径をD、前記軸受の外径をDとして、その直径dが下式の範囲内に設定されていることを特徴とする請求項1乃至3記載のいずれかの内接歯車ポンプ。
0.3(D−D)/2≦d
The end surface lubricating through-hole has a diameter d 1 set within a range of the following formula, where D 1 is the diameter of the root circle and D 2 is the outer diameter of the bearing. The internal gear pump of any one of thru | or 3.
0.3 (D 1 -D 2 ) / 2 ≦ d 1
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111520322A (en) * 2019-02-04 2020-08-11 施瓦本冶金工程汽车有限公司 Internal gear pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111520322A (en) * 2019-02-04 2020-08-11 施瓦本冶金工程汽车有限公司 Internal gear pump
CN111520322B (en) * 2019-02-04 2022-04-19 施瓦本冶金工程汽车有限公司 Internal gear pump

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