WO2013186839A1 - Gear pump or motor - Google Patents

Gear pump or motor Download PDF

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Publication number
WO2013186839A1
WO2013186839A1 PCT/JP2012/064937 JP2012064937W WO2013186839A1 WO 2013186839 A1 WO2013186839 A1 WO 2013186839A1 JP 2012064937 W JP2012064937 W JP 2012064937W WO 2013186839 A1 WO2013186839 A1 WO 2013186839A1
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Prior art keywords
gear
hydraulic
driven
helical gear
pressure
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PCT/JP2012/064937
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French (fr)
Japanese (ja)
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信雄 向井
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株式会社 島津製作所
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Priority to PCT/JP2012/064937 priority Critical patent/WO2013186839A1/en
Publication of WO2013186839A1 publication Critical patent/WO2013186839A1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042Systems for the equilibration of forces acting on the machines or pump
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/50Bearings
    • F04C2240/56Bearing bushings or details thereof

Abstract

A gear pump or a motor comprises: an externally meshing gear pair (1) which is composed of a driving helical gear (6) and a driven helical gear (7) which mesh with each other; a casing (2) which has therein a gear housing chamber (2a) for housing the externally meshing gear pair (1) and which has bearings (25, 26) for receiving a driving shaft (8) which supports the driving helical gear (6) in a rotatable manner and also receiving a driven shaft (9) which supports the driven helical gear (7) in a rotatable manner; a pair of side plates (31, 32) which are housed within the casing (2) and which are each provided in contact with side surfaces (6a, 7a, 6b, 7b) of each of the helical gears (6, 7) of the externally meshing gear pair (1); a hydraulic mechanism (4) which has hydraulic chambers (41a, 41b) and which, by means of hydraulic pressure introduced into the hydraulic chambers (41a, 41b), presses the driving shaft (8) and the driven shaft (9) in the direction opposite the direction in which a thrust load acts; and a high-pressure hydraulic fluid introduction passage (5) which introduces hydraulic fluid from the high-pressure side into the hydraulic chambers (41a, 41b) of the hydraulic mechanism (4). Pressing pressure generated by the hydraulic mechanism (4) is set so that the driving shaft (8) and the driven shaft (9) are pressed at a value exceeding the maximum value of a changing thrust load, the driving shaft (8) and the driven shaft (9) being pressed in the direction opposite the direction in which the thrust load acts.

Description

歯車ポンプ又はモータGear pump or motor
 本発明は、互いに噛み合うはすば歯車をそれぞれ利用した駆動歯車及び従動歯車からなる外接歯車対と、内部にこの外接歯車対を収納する歯車収納室を有するケーシングとを備えた歯車ポンプ又はモータに関する。 The present invention relates to a gear pump or a motor provided with an external gear pair composed of a drive gear and a driven gear each utilizing helical gears that mesh with each other, and a casing having a gear storage chamber for storing the external gear pair therein. .
 従来より、互いに噛み合う駆動歯車と従動歯車とからなる外接歯車対と、この外接歯車対を収納する歯車収納室を内部に有するケーシングとを備える歯車ポンプ又はモータが広く用いられている。このような歯車ポンプ又はモータの駆動歯車及び従動歯車は、軸芯に平行な歯が周囲に形成されている平歯車が主流である。しかし、駆動歯車及び従動歯車に平歯車を使用する場合、以下のような問題が存在する。具体的には、駆動歯車の歯と従動歯車の歯とが噛み合う際には歯幅全域にわたって同時に噛み合う。また、駆動歯車の歯と従動歯車の歯との噛み合いを終了する際には歯幅全域にわたって同時に噛み合いを終了する。このことにより、騒音や振動が発生することがある。この問題を解決するために、駆動歯車と従動歯車としてはすば歯車を採用する工夫が提案されている(例えば、特許文献1参照)。 2. Description of the Related Art Conventionally, a gear pump or a motor including an external gear pair that includes a drive gear and a driven gear that mesh with each other and a casing that internally includes a gear storage chamber that stores the external gear pair has been widely used. The spur gear in which teeth parallel to the axis are formed around the drive gear and driven gear of such a gear pump or motor is the mainstream. However, when a spur gear is used for the drive gear and the driven gear, there are the following problems. Specifically, when the teeth of the drive gear and the teeth of the driven gear mesh with each other, they mesh simultaneously over the entire tooth width. Further, when the meshing between the teeth of the drive gear and the teeth of the driven gear is terminated, the meshing is simultaneously terminated over the entire tooth width. This can cause noise and vibration. In order to solve this problem, a contrivance has been proposed in which helical gears are used as the drive gear and the driven gear (see, for example, Patent Document 1).
 このような歯車ポンプ又はモータは、例えば、以下に示すような構成を有する。すなわち、図2に示すように、互いに噛み合う駆動側はすば歯車X6及び従動側はすば歯車X7からなる外接歯車対X1と、この外接歯車対X1を収納する歯車収納室X2aを内部に有するとともに前記駆動側はすば歯車X6を軸支する駆動軸X8及び前記従動側はすば歯車X7を軸支する従動軸X9を収納するための軸受を有するケーシングX2と、このケーシングX2内に収納され前記外接歯車対X1の各はすば歯車X6、X7の両側面X6a、X6b、X7a、X7bにそれぞれ添接しそれぞれ対をなす側板を兼ねるリア側のベアリングケースX3a及びフロント側のベアリングケースX3bと、液圧室X41a、X41bを有しこの液圧室X41a、X41bに導入される液圧により前記駆動軸X8及び従動軸X9を反スラスト方向に押圧する液圧機構X4と、この液圧機構X4の液圧室X41a、X41bに高圧側から作動液を導く高圧作動液導入路X5とを具備してなる。前記ケーシングX2は、前記歯車収納室X2aを有する筒状のボディX23と、このボディX23の前面側に装着されたフロントカバーX22と、前記ボディX23の背面側に装着されたリアカバーX24とを有する。前記ボディX23の内部には、一方の側板を兼ね駆動軸X8の後端側及び従動軸X9の後端側を軸支するリア側のベアリングケースX3aと、他方の側板を兼ね駆動軸X8の前端側及び従動軸X9の前端側を軸支するリア側のベアリングケースX3bとを収納している。 Such a gear pump or motor has the following configuration, for example. That is, as shown in FIG. 2, an external gear pair X1 composed of a driving side helical gear X6 and a driven side helical gear X7, and a gear storage chamber X2a for storing the external gear pair X1 are internally provided. A casing X2 having a bearing for housing a drive shaft X8 for supporting the helical gear X6 on the driving side and a driven shaft X9 for supporting the driven helical gear X7 on the driving side is housed in the casing X2. And a rear-side bearing case X3a and a front-side bearing case X3b that serve as a pair of side plates that are in contact with both side surfaces X6a, X6b, X7a, and X7b of the helical gears X6 and X7, respectively. The hydraulic shafts X41a and X41b have hydraulic chambers X41a and X41b, and the drive shaft X8 and the driven shaft X9 are anti-thrusted by the hydraulic pressure introduced into the hydraulic chambers X41a and X41b. A hydraulic mechanism X4 for pressing, hydraulic chambers X41a of the hydraulic mechanism X4, formed by and a high-pressure hydraulic fluid introducing passage X5 for guiding hydraulic fluid from the high pressure side X41b. The casing X2 includes a cylindrical body X23 having the gear housing chamber X2a, a front cover X22 attached to the front side of the body X23, and a rear cover X24 attached to the rear side of the body X23. Inside the body X23, there is a bearing case X3a on the rear side that also serves as one side plate and the rear end side of the drive shaft X8 and the rear end side of the driven shaft X9, and the front end of the drive shaft X8 that also serves as the other side plate. And a rear bearing case X3b that pivotally supports the front end side of the driven shaft X9.
 このような構成の歯車ポンプを運転している状態では、駆動側はすば歯車X6及び従動側はすば歯車X7に、回転トルクの分力によるスラスト荷重と液圧によるスラスト荷重とが発生する。これら回転トルクの分力によるスラスト荷重と液圧によるスラスト荷重とが合成された結果、図2に示すように、駆動側はすば歯車X6及び従動側はすば歯車X7に、それぞれ異なる大きさのスラスト荷重が、後方に向けて加えられる(以下、このスラスト荷重の方向を「スラスト方向」と呼び、その反対方向を「反スラスト方向」と呼ぶ)。 In a state where the gear pump having such a configuration is operated, a thrust load due to a component of rotational torque and a thrust load due to hydraulic pressure are generated on the driving side helical gear X6 and the driven side helical gear X7. . As a result of synthesizing the thrust load due to the component force of the rotational torque and the thrust load due to the hydraulic pressure, as shown in FIG. 2, the driving side is different in the helical gear X6 and the driven side is different in the helical gear X7. (Hereinafter, the direction of the thrust load is referred to as “thrust direction” and the opposite direction is referred to as “anti-thrust direction”).
 リア側のベアリングケースX3aは、前記スラスト荷重によって受ける面圧が大きくなるため、負荷を軽減させる目的で、駆動軸X8及び従動軸X9の後端側に前記液圧機構X4のバランスピストンX43a、X43bをそれぞれ接触させ、液圧力によりバランスさせている。この結果、バランスピストンX43a、X43bは液圧力に比例した押し付け力を前記スラスト荷重に対抗して作用させることが可能となる。 The bearing case X3a on the rear side receives a large surface pressure due to the thrust load. For the purpose of reducing the load, the balance pistons X43a and X43b of the hydraulic mechanism X4 are arranged on the rear end side of the drive shaft X8 and the driven shaft X9. Are brought into contact with each other and balanced by liquid pressure. As a result, the balance pistons X43a and X43b can apply a pressing force proportional to the fluid pressure against the thrust load.
 しかし、前記液圧機構X4は、スラストを軽減してバランスさせるだけの目的で設けられたものであるため、運転条件が変動した場合、駆動側はすば歯車X6及び従動側はすば歯車X7が受けるスラスト荷重が不均一で不安定となることがある。その際、リア側のベアリングケースX3a及びフロント側のベアリングケースX3bにスラスト荷重が負荷されるだけでなく、駆動側はすば歯車X6及び従動側はすば歯車X7の側面X6a、X6b、X7a、X7bが位置ズレすることによって、これらのはすば歯車X6、X7の側面X6a、X6b、X7a、X7bからの作動液の漏れが増大し容積性能が低下する不具合が発生し得る。この不具合の発生を防ぐために、各ベアリングケースX3a、X3bにコストが割高の面圧強度の高い材料を使用し、いわゆる3の字形のガスケットX31を利用した圧力バランスによって、すなわち3の字形のガスケットX31の内側に液圧封入領域を形成し前記リア側のベアリングケースX3aを駆動側はすば歯車X6及び従動側はすば歯車X7の後側の側面X6a、X7aに強く押し戻してバランスさせることによって性能を維持させる必要があった。 However, since the hydraulic mechanism X4 is provided only for the purpose of reducing and balancing the thrust, when the operating conditions fluctuate, the driving side is the helical gear X6 and the driven side is the helical gear X7. The thrust load received by the cylinder may be uneven and unstable. At this time, not only a thrust load is applied to the rear side bearing case X3a and the front side bearing case X3b, but the driving side is a helical gear X6 and the driven side is a side X6a, X6b, X7a, When X7b is misaligned, the leakage of the hydraulic fluid from the side surfaces X6a, X6b, X7a, and X7b of the helical gears X6 and X7 may increase, resulting in a problem that the volume performance decreases. In order to prevent the occurrence of this problem, the bearing cases X3a and X3b are made of a material with high surface pressure strength at a high cost, and by pressure balance using a so-called three-shaped gasket X31, that is, a three-shaped gasket X31. Performance is achieved by forming a hydraulically sealed region inside the rear side and pushing the rear side bearing case X3a strongly against the rear side surfaces X6a and X7a of the driving side helical gear X6 and the driven side helical gear X7 for balancing. It was necessary to maintain.
特開平5-330330号公報JP-A-5-330330
 本発明は以上の点に着目したものであり、コストが割高の面圧強度の高い側板を採用しなければならないという制約を無くすことができ、部品コストを低減させるための設計の自由度を高めることができる歯車ポンプ又はモータを提供することを所期の目的とする。 The present invention pays attention to the above points, and can eliminate the restriction that the costly side plate having a high surface pressure strength must be adopted, thereby increasing the degree of design freedom for reducing the component cost. It is an intended object to provide a gear pump or motor that can be used.
 すなわち本発明に係る歯車ポンプ又はモータは、互いに噛み合う駆動側はすば歯車及び従動側はすば歯車からなる外接歯車対と、この外接歯車対を収納する歯車収納室を内部に有するとともに前記駆動側はすば歯車を軸支する駆動軸及び前記従動側はすば歯車を軸支する従動軸を収納するための軸受を有するケーシングと、このケーシング内に収納され前記外接歯車対の各はすば歯車の両側面にそれぞれ添接する対をなす側板と、液圧室を有しこの液圧室に導入される液圧により前記駆動軸及び従動軸を反スラスト方向に押圧する液圧機構と、この液圧機構の液圧室に高圧側から作動液を導く高圧作動液導入路とを具備してなり、変動するスラストの最大値を上回る値で前記駆動軸及び前記従動軸を反スラスト方向に押圧するように前記液圧機構による押圧力を設定していることを特徴とする。 That is, the gear pump or motor according to the present invention has an external gear pair composed of a driving side helical gear and a driven side helical gear meshing with each other, and a gear storage chamber for storing the external gear pair, and the drive. A casing having a drive shaft for supporting a helical gear on the side and a bearing for housing a driven shaft for supporting the driven helical gear, and a helical gear housed in the casing. A pair of side plates that make contact with both side surfaces of the gear, a hydraulic mechanism that has a hydraulic chamber and presses the drive shaft and the driven shaft in the anti-thrust direction by the hydraulic pressure introduced into the hydraulic chamber; The hydraulic pressure mechanism includes a high-pressure hydraulic fluid introduction path that guides hydraulic fluid from the high-pressure side to the hydraulic pressure chamber. The drive shaft and the driven shaft are set in the anti-thrust direction at a value exceeding the maximum value of the varying thrust. Said liquid to press Characterized in that it sets the pressing force of the mechanism.
 このような構成によれば、前記液圧機構により、変動するスラストの最大値を上回る値で前記駆動軸及び前記従動軸が反スラスト方向に押圧されるので、スラスト方向側に配された側板は駆動側はすば歯車及び従動側はすば歯車からのスラスト荷重の影響を受けないことになる。従って、スラスト方向側に配された側板は面圧強度の低い材料で構成することができる。そして、駆動側はすば歯車及び従動側はすば歯車の双方が常時反スラスト方向に押圧されることとなるので、圧力変動による駆動側はすば歯車及び従動側はすば歯車の側面の位置ズレに伴う問題を解消することもできる。 According to such a configuration, the drive shaft and the driven shaft are pressed in the anti-thrust direction at a value exceeding the maximum value of the varying thrust by the hydraulic mechanism, so the side plate disposed on the thrust direction side is The driving side is not affected by the thrust load from the helical gear and the driven side is not affected by the thrust load from the helical gear. Therefore, the side plate arranged on the thrust direction side can be made of a material having low surface pressure strength. Since both the helical gear on the driving side and the helical gear on the driven side are always pressed in the anti-thrust direction, the driving side on the side of the helical gear and the driven side on the side of the helical gear due to pressure fluctuations. Problems associated with misalignment can also be solved.
 本発明によれば、コストが割高の面圧強度の高い側板を採用しなければならないという制約を無くすことができ、部品コストを低減させるための設計の自由度を高めることができる歯車ポンプ又はモータを提供することができる。 According to the present invention, a gear pump or a motor that can eliminate the restriction that a costly side plate having a high surface pressure strength must be adopted and can increase the degree of freedom in designing to reduce the component cost. Can be provided.
本発明の一実施形態に係る歯車ポンプ又はモータを示す概略図。Schematic which shows the gear pump or motor which concerns on one Embodiment of this invention. 従来の歯車ポンプ又はモータを示す概略図。Schematic which shows the conventional gear pump or motor.
 以下、本発明の一実施形態を、図面を参照して説明する。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
 本実施形態に係る歯車ポンプP1は、図1に示すように、互いに噛み合う駆動側はすば歯車6及び従動側はすば歯車7からなる外接歯車対1と、この外接歯車対1を収納する歯車収納室2aを内部に有するとともに前記駆動側はすば歯車6を軸支する駆動軸8及び前記従動側はすば歯車7を軸支する従動軸9を収納するための軸受を有するケーシング2と、このケーシング2内に収納され前記外接歯車1対の各はすば歯車6、7の両側面6a、6b、7a、7bにそれぞれ添接する対をなす後側板3a及び前側板3bと、液圧室41a、41bを有しこの液圧室41a、41bに導入される液圧により前記駆動軸8及び従動軸9を反スラスト方向に押圧する液圧機構4と、この液圧機構4の液圧室41a、41bに高圧側から作動液を導く高圧作動液導入路5とを具備する。 As shown in FIG. 1, the gear pump P <b> 1 according to the present embodiment accommodates an external gear pair 1 including a driving-side helical gear 6 and a driven-side helical gear 7 that mesh with each other, and the external gear pair 1. A casing 2 having a gear housing chamber 2a therein and a bearing for housing the drive shaft 8 that supports the helical gear 6 on the driving side and the driven shaft 9 that supports the helical gear 7 on the driven side. A rear plate 3a and a front plate 3b, which are housed in the casing 2 and make a pair respectively contacting the both side surfaces 6a, 6b, 7a, 7b of the helical gears 6, 7; A hydraulic mechanism 4 having pressure chambers 41a and 41b and pressing the drive shaft 8 and the driven shaft 9 in the anti-thrust direction by the hydraulic pressure introduced into the hydraulic chambers 41a and 41b; The hydraulic fluid is guided to the pressure chambers 41a and 41b from the high pressure side. Comprising a pressure hydraulic fluid introducing passage 5.
 前記外接歯車対1を構成する駆動側はすば歯車6及び従動側はすば歯車7は、この種の歯車ポンプに用いられるものとして周知のはすば歯車である。ここで、前記駆動側はすば歯車6の歯及び従動側はすば歯車7の歯は、これらを噛み合わせた状態で歯車ポンプとして作動させる際に、回転トルクの分力により、駆動側はすば歯車6は後方に向かうスラスト荷重、従動側はすば歯車7は前方に向かうスラスト荷重をそれぞれ受ける。また、これら駆動側はすば歯車6及び従動側はすば歯車7は、歯車ポンプとして作動している状態で、液圧により、後方に向かうスラスト荷重をそれぞれ受ける。これら回転トルクの分力によるスラスト荷重と液圧によるスラスト荷重とが合成された結果、図2に示すように、駆動側はすば歯車6及び従動側はすば歯車7に、それぞれ異なる大きさのスラスト荷重が、後方に向けて加えられる。本実施形態では、前記駆動側はすば歯車6と駆動軸8とを一体に設けている。前記駆動軸8は、前記駆動側はすば歯車6の中心から回転軸心方向に延伸している。この駆動軸8は、一端がケーシング2の外部に延出している。また、従動側はすば歯車7と従動軸9とも一体に設けている。前記従動軸9は、前記従動側はすば歯車7の中心から回転軸心方向に延伸している。 The driving-side helical gear 6 and the driven-side helical gear 7 constituting the external gear pair 1 are helical gears that are well known as those used in this type of gear pump. Here, the teeth on the driving side of the helical gear 6 and the teeth on the driven side of the helical gear 7 are operated as a gear pump in a state where they are engaged with each other. The helical gear 6 receives a thrust load going backward, and the driven gear 7 receives a thrust load going forward. The helical gear 6 on the driving side and the helical gear 7 on the driven side receive thrust loads directed rearward by the hydraulic pressure while operating as a gear pump. As a result of the combination of the thrust load due to the component force of the rotational torque and the thrust load due to the hydraulic pressure, as shown in FIG. 2, the driving side is different in the helical gear 6 and the driven side is different in the helical gear 7. The thrust load is applied toward the rear. In the present embodiment, the drive side is provided with the helical gear 6 and the drive shaft 8 integrally. The drive shaft 8 extends from the center of the helical gear 6 on the drive side in the rotational axis direction. One end of the drive shaft 8 extends to the outside of the casing 2. Further, the driven side is provided integrally with the helical gear 7 and the driven shaft 9. The driven shaft 9 extends from the center of the driven helical gear 7 in the direction of the rotational axis.
 ケーシング2は、前方に開口する歯車収納室2aを有するケーシング本体21と、このケーシング本体21の前面側に装着されたフロントカバー22とを備えている。 The casing 2 includes a casing body 21 having a gear housing chamber 2a that opens forward, and a front cover 22 that is mounted on the front side of the casing body 21.
 ケーシング本体21は、その内部に前記外接歯車対1すなわち駆動側はすば歯車6及び従動側はすば歯車7を噛合状態で収容する略眼鏡状の前記歯車収納室2aとこの歯車収納室2aを外部に連通させる図示しない作動液吸入口及び作動液吐出口2bとを備えた筒状のボディ23と、このボディ23の後端を閉塞するリアカバー24とを一体に形成したものである。また、前記ボディ23は、前記歯車収納室2aの後方に、前記駆動軸8及び従動軸9の後端側を軸支する軸受25を備えている。各軸受25は、前記駆動軸8及び従動軸9の後端側がそれぞれ嵌入可能な軸受穴25xと、この軸受穴25xの内周に設けられ前記前記駆動軸8及び従動軸9をそれぞれ摺動可能に軸支するブッシュ25yとを備えたものである。 The casing main body 21 has a substantially eyeglass-shaped gear housing chamber 2a in which the external gear pair 1, that is, the driving-side helical gear 6 and the driven-side helical gear 7 are housed in an engaged state, and the gear housing chamber 2a. Is formed integrally with a cylindrical body 23 having a hydraulic fluid inlet and a hydraulic fluid outlet 2b (not shown) that communicate with the outside, and a rear cover 24 that closes the rear end of the body 23. The body 23 includes a bearing 25 that supports the rear end sides of the drive shaft 8 and the driven shaft 9 behind the gear housing chamber 2a. Each bearing 25 is provided with a bearing hole 25x into which the rear end side of the drive shaft 8 and the driven shaft 9 can be respectively fitted, and is slidable on the drive shaft 8 and the driven shaft 9 provided on the inner periphery of the bearing hole 25x. And a bush 25y that pivotally supports the shaft.
 前記フロントカバー22は、ケーシング本体21にボルト等によって着脱可能に装着され、前記歯車収納室2aの開口面を閉塞する。また、このフロントカバー22は、前記駆動軸8及び従動軸9の前端側を軸支する軸受26を備えている。各軸受26は、前記駆動軸8及び従動軸9の前端側がそれぞれ嵌入可能な軸受穴26xと、この軸受穴26xの内周に設けられ前記駆動軸8及び従動軸9をそれぞれ摺動可能に軸支するブッシュ26yとを備えたものである。駆動軸8の前端は、前記軸受穴26xを貫通してケーシング2の外部に突出させてある。 The front cover 22 is detachably attached to the casing body 21 with bolts or the like, and closes the opening surface of the gear housing chamber 2a. The front cover 22 includes a bearing 26 that pivotally supports the front end sides of the drive shaft 8 and the driven shaft 9. Each bearing 26 is provided with a bearing hole 26x in which the front end sides of the drive shaft 8 and the driven shaft 9 can be respectively fitted, and an inner periphery of the bearing hole 26x so that the drive shaft 8 and the driven shaft 9 can slide. A supporting bush 26y is provided. The front end of the drive shaft 8 passes through the bearing hole 26x and protrudes to the outside of the casing 2.
 また、本実施形態では、駆動側はすば歯車6の後側の側面6a及び従動側はすば歯車7の後側の側面7aに、後側板3aを添接させて設けている。この後側板3aは、平歯車式歯車ポンプに用いられているものと略同等の薄板状のものである。この後側板3aの背面は、3の字形のガスケット31を介してケーシング本体21の段部端面21aに当接させてある。なお、3の字形のガスケット31の内側に形成される液圧封入領域は、従来のものに比べて狭く設定してある。また、駆動側はすば歯車6の前側の側面6b及び従動側はすば歯車7の前側の側面7bに、前側板3bを添接させて設けている。この前側板3bは、面圧強度の比較的高い材料により作られたもので、薄板状のものである。この前側板3bの前面は、ガスケット32を介してフロントカバー22の内面22aに当接させてある。なお、本実施形態では、前側板3bの材料は、後側板3aの材料と異なる。 Further, in the present embodiment, the driving side is provided with the rear side plate 3 a attached to the rear side surface 6 a of the helical gear 6 and the driven side helical gear 7. This rear side plate 3a has a thin plate shape substantially the same as that used in a spur gear type gear pump. The rear surface of the rear side plate 3 a is brought into contact with the stepped end surface 21 a of the casing body 21 through a three-shaped gasket 31. Note that the hydraulic pressure sealing region formed inside the three-shaped gasket 31 is set narrower than that of the conventional one. Further, the driving side is provided with a front side plate 3b attached to the front side surface 6b of the helical gear 6 and the driven side helical surface 7b. The front side plate 3b is made of a material having a relatively high surface pressure strength, and has a thin plate shape. The front surface of the front plate 3 b is in contact with the inner surface 22 a of the front cover 22 via the gasket 32. In the present embodiment, the material of the front side plate 3b is different from the material of the rear side plate 3a.
 前記液圧機構4は、前記駆動軸8及び前記従動軸9にそれぞれ対応させてリアカバー24の内部に形成した対をなす液圧室41a、41bと、これら液圧室41a、41bをケーシング本体21内に連通させる対をなすシリンダボア42a、42bと、これらシリンダボア42a、42b内にそれぞれスライド可能に嵌装された対をなすバランスピストン43a、43bとを具備してなるもので、前記各バランスピストン43a、43bを対応する前記駆動軸8及び従動軸9の端面に当接させている。前記バランスピストン43a、43bの直径、換言すればこのバランスピストン43a、43bを嵌装するシリンダボア42a、42bの直径は、変動するスラストの最大値を上回る値で前記駆動軸8及び前記従動軸9を反スラスト方向に押圧することができる値に設定されている。具体的には、例えば作動液の圧力をPとし、駆動軸8側のシリンダボア42aの断面積をA1とした場合、前記駆動軸はP×A1の力F1で反スラスト方向に駆動軸8側のバランスピストン43aにより押圧される。この実施形態においては、駆動軸8が受けるスラストが7~9の範囲で変動することが事前の計測により判明した場合、前記押圧力F1が10となるように駆動軸8側のシリンダボア42aの断面積A1を設定する。また、作動液の圧力をPとし、従動軸9側のシリンダボア43bの断面積をA2とした場合、前記従動軸9はP×A2の力F2で反スラスト方向にバランスピストンにより押圧される。この実施形態においては、従動軸9が受けるスラストが2~4の範囲で変動することが事前の計測により判明した場合、前記押圧力F2が5となるように従動軸9側のシリンダボア42bの断面積A2を設定する。 The hydraulic mechanism 4 includes a pair of hydraulic chambers 41a and 41b formed inside the rear cover 24 so as to correspond to the drive shaft 8 and the driven shaft 9, respectively, and these hydraulic chambers 41a and 41b are connected to the casing body 21. A pair of cylinder bores 42a and 42b communicating with each other, and a pair of balance pistons 43a and 43b slidably fitted in the cylinder bores 42a and 42b, respectively. 43b are brought into contact with the corresponding end surfaces of the drive shaft 8 and the driven shaft 9. The diameters of the balance pistons 43a and 43b, in other words, the diameters of the cylinder bores 42a and 42b in which the balance pistons 43a and 43b are fitted exceed the maximum value of the fluctuating thrust. It is set to a value that can be pressed in the anti-thrust direction. Specifically, for example, when the pressure of the hydraulic fluid is P and the cross-sectional area of the cylinder bore 42a on the drive shaft 8 side is A1, the drive shaft is on the drive shaft 8 side in the anti-thrust direction with a force F1 of P × A1. It is pressed by the balance piston 43a. In this embodiment, when it is found by prior measurement that the thrust received by the drive shaft 8 varies in the range of 7 to 9, the cylinder bore 42a on the drive shaft 8 side is disconnected so that the pressing force F1 becomes 10. The area A1 is set. When the pressure of the hydraulic fluid is P and the cross-sectional area of the cylinder bore 43b on the driven shaft 9 side is A2, the driven shaft 9 is pressed by the balance piston in the anti-thrust direction with a force F2 of P × A2. In this embodiment, when it is found by prior measurement that the thrust received by the driven shaft 9 varies in the range of 2 to 4, the cylinder bore 42b on the driven shaft 9 side is disconnected so that the pressing force F2 becomes 5. The area A2 is set.
 前記高圧作動液導入路5は、液圧機構4の液圧室41a、41bに高圧側から作動液を導くためのもので、ケーシング本体21内に形成されている。 The high-pressure hydraulic fluid introduction path 5 is for guiding the hydraulic fluid from the high-pressure side to the hydraulic chambers 41 a and 41 b of the hydraulic mechanism 4 and is formed in the casing body 21.
 ここで、この歯車ポンプP1の前記駆動軸8を介して前記駆動側はすば歯車6及び従動側はすば歯車7を同期逆回転駆動した場合に、前記作動液吸入口と前記作動液吐出口2bとの間で高低圧差が生じる。このとき、前記駆動側はすば歯車6及び従動側はすば歯車7の歯同士が漸次離反する側のボディ23内空間、つまり前記作動液吸込口側の空間が低圧領域になるとともに、歯同士が漸次噛合する側のボディ23内空間、つまり作動液吐出口2b側の空間が高圧領域になる。そして、作動液吸込口より導入した作動液を、前記駆動側はすば歯車6及び従動側はすば歯車7の歯先と歯車収納室2aとの間に閉成される容積空間に閉じ込めて作動液吐出口2bにまで導き吐出するポンプ作用を営むようにしている。なお、この歯車ポンプP1は、作動液吐出口2bより高圧の作動液を導入し、これにより前記駆動軸8から回転トルクを取り出して外部負荷を駆動するとともに、低圧となった作動液を前記作動液吸込口から吐出するというモータ作用を営む歯車モータとして機能させることもできるものであることはいうまでもない。 Here, when the driving-side helical gear 6 and the driven-side helical gear 7 are driven synchronously and reversely through the driving shaft 8 of the gear pump P1, the hydraulic fluid suction port and the hydraulic fluid discharge are driven. A high and low pressure difference is generated between the outlet 2b. At this time, the internal space of the body 23 on the side where the teeth of the helical gear 6 on the driving side and the helical gear 7 on the driven side are gradually separated from each other, that is, the space on the side of the hydraulic fluid suction port is in a low pressure region. The space in the body 23 on the side where the meshes with each other gradually, that is, the space on the hydraulic fluid discharge port 2b side becomes a high pressure region. Then, the hydraulic fluid introduced from the hydraulic fluid suction port is confined in a volume space that is closed between the tooth tip of the helical gear 6 on the driving side and the helical gear 7 on the driven side and the gear housing chamber 2a. A pumping action is performed so as to lead to the hydraulic fluid discharge port 2b and discharge. The gear pump P1 introduces high-pressure hydraulic fluid from the hydraulic fluid discharge port 2b, thereby taking out rotational torque from the drive shaft 8 and driving an external load, and at the same time, operating the hydraulic fluid at low pressure in the operation. It goes without saying that it can also function as a gear motor that performs the motor action of discharging from the liquid suction port.
 以上に述べたように、本実施形態に係る歯車ポンプP1の構成によれば、前記バランスピストン43a、43bを収納するシリンダボア42a、42bの直径は、変動するスラストの最大値を上回る値で前記駆動軸8及び前記従動軸9を反スラスト方向に押圧することができる値に設定しているので、後側板3aは前記スラストによる影響を受けない。従って、後側板3aは平歯車式歯車ポンプに用いられているものと略同等の面圧強度の低い材料を用いて構成することができる。また、前側板3bは、前記バランスピストン43a、43bから押圧力を受けるので、十分な面圧強度を有する材料により構成する必要はあるが、この前側板3bは薄い板状のものにより構成することができる。すなわち、両側板3a、3bにコストが割高の面圧強度の高い材料を採用しなければならないという制約を無くすことができ、部品コストを低減させるための設計の自由度を高めることができる。換言すれば、駆動軸及び従動軸を観入させるための軸受を有するベアリングケースを省略し、薄板状の後側板31及び前側板32によりスラストを受けるようにできるので、部品点数を削減し製造コストを低下させることができる。そして、前記駆動側はすば歯車6及び従動側はすば歯車7の双方が常時前方すなわち反ラスト力方向に押圧されることとなるので、圧力変動による前記駆動側はすば歯車6及び従動側はすば歯車7の側面6a、6b、7a、7bの位置ズレに伴い歯車6、7の側面6a、6b、7a、7bから作動液が漏れ容積性能が低下する問題を解消することもできる。 As described above, according to the configuration of the gear pump P1 according to the present embodiment, the diameters of the cylinder bores 42a and 42b that house the balance pistons 43a and 43b exceed the maximum value of the fluctuating thrust. Since the shaft 8 and the driven shaft 9 are set to values capable of pressing in the anti-thrust direction, the rear side plate 3a is not affected by the thrust. Therefore, the rear side plate 3a can be configured by using a material having a low surface pressure strength which is substantially the same as that used in the spur gear type gear pump. Further, since the front side plate 3b receives a pressing force from the balance pistons 43a and 43b, the front side plate 3b needs to be made of a material having a sufficient surface pressure strength. However, the front side plate 3b is made of a thin plate. Can do. That is, it is possible to eliminate the restriction that a material having a high cost and high surface pressure strength must be used for the side plates 3a and 3b, and it is possible to increase the degree of design freedom for reducing the component cost. In other words, a bearing case having a bearing for viewing the drive shaft and the driven shaft can be omitted, and the thrust can be received by the thin plate-like rear side plate 31 and front side plate 32, thereby reducing the number of parts and manufacturing cost. Can be reduced. Then, both the helical gear 6 on the driving side and the helical gear 7 on the driven side are always pressed forward, that is, in the direction opposite to the last force, so that the driving side helical gear 6 and the driven gear due to pressure fluctuations. As for the side, the problem that the hydraulic fluid leaks from the side surfaces 6a, 6b, 7a and 7b of the gears 6 and 7 due to the displacement of the side surfaces 6a, 6b, 7a and 7b of the helical gear 7 can be solved. .
 また、本実施形態では、その内部に前記外接歯車対1を噛合状態で収容する略眼鏡状の前記歯車収納室2aとこの歯車収納室2aを外部に連通させる作動液吸入口及び作動液吐出口2bとを備えた筒状のボディ23と、このボディ23の後端を閉塞するリアカバー24とをボディ本体21として一体に形成しているので、これらを別体に形成したものと異なり、ボディ23とリアカバー24との接合箇所からの作動液漏れが発生し得ず、この点からも容積性能が低下する問題を解消することもできる。 In the present embodiment, the substantially eyeglass-shaped gear housing chamber 2a that accommodates the external gear pair 1 in an engaged state therein, and the hydraulic fluid inlet and the hydraulic fluid outlet that communicate the gear housing chamber 2a with the outside. Since the cylindrical body 23 provided with 2b and the rear cover 24 for closing the rear end of the body 23 are integrally formed as the body main body 21, the body 23 is different from the one formed separately. From this point, it is possible to eliminate the problem that the hydraulic fluid leaks from the joint portion between the rear cover 24 and the rear cover 24, and the volume performance is lowered.
 なお、本発明は以上に述べた実施形態に限らず、種々に変形してよい。 Note that the present invention is not limited to the above-described embodiment, and may be variously modified.
 例えば、上述した実施形態においては、ボディに、外接歯車対を収納する歯車収納室を備えたボディと、このボディの後端を閉塞するリアカバーとを一体に形成しているが、前記ボディと前記リアカバーとを別体に構成したものに本発明を適用してもよい。また、前記ボディと前記リアカバーとを別体に構成する場合、前記ボディと、このボディの前端を閉塞するフロントカバーとを一体に構成するようにしてもよい。 For example, in the above-described embodiment, the body is integrally formed with a body including a gear storage chamber that stores the external gear pair and a rear cover that closes the rear end of the body. You may apply this invention to what comprised the rear cover separately. When the body and the rear cover are configured separately, the body and a front cover that closes the front end of the body may be configured integrally.
 加えて、上述した実施形態において、フロントカバーが前側板を兼ねる構成を採用してもよい。 In addition, in the above-described embodiment, a configuration in which the front cover also serves as the front side plate may be employed.
 さらに、上述した実施形態では、後側板と前側板とを異なる材料によって作っているが、これら後側板と前側板とを同一の材料により作るようにしてももちろんよい。 Furthermore, in the above-described embodiment, the rear side plate and the front side plate are made of different materials. However, the rear side plate and the front side plate may be made of the same material.
 その他、本発明の趣旨を損ねない範囲で種々に変形してよい。 Other various modifications may be made without departing from the spirit of the present invention.
 本発明の歯車ポンプ又はモータの構成を採用すれば、コストが割高の面圧強度の高い側板を採用しなければならないという制約を無くすことができ、部品コストを低減させるための設計の自由度を高めることができる。 By adopting the configuration of the gear pump or motor of the present invention, it is possible to eliminate the restriction that the costly side plate having a high surface pressure strength must be adopted, and the degree of design freedom for reducing the component cost can be eliminated. Can be increased.
 P1…歯車ポンプ
 1…外接歯車対
 2…ケーシング
 2a…歯車収納室
 3…側板
 4…液圧機構
 41…液圧室
 5…高圧作動液導入路
 6…駆動側はすば歯車
 7…従動側はすば歯車
 8…駆動軸
 9…従動軸
P1 ... gear pump 1 ... external gear pair 2 ... casing 2a ... gear housing chamber 3 ... side plate 4 ... hydraulic mechanism 41 ... hydraulic chamber 5 ... high pressure hydraulic fluid introduction path 6 ... drive side helical gear 7 ... driven side Helical gear 8 ... Drive shaft 9 ... Drive shaft

Claims (1)

  1. 互いに噛み合う駆動側はすば歯車及び従動側はすば歯車からなる外接歯車対と、この外接歯車対を収納する歯車収納室を内部に有するとともに前記駆動側はすば歯車を軸支する駆動軸及び前記従動側はすば歯車を軸支する従動軸を収納するための軸受を有するケーシングと、このケーシング内に収納され前記外接歯車対の各はすば歯車の両側面にそれぞれ添接する対をなす側板と、液圧室を有しこの液圧室に導入される液圧により前記駆動軸及び従動軸を反スラスト方向に押圧する液圧機構と、この液圧機構の液圧室に高圧側から作動液を導く高圧作動液導入路とを具備してなり、変動するスラストの最大値を上回る値で前記駆動軸及び前記従動軸を反スラスト方向に押圧するように前記液圧機構による押圧力を設定していることを特徴とする歯車ポンプ又はモータ。 A drive shaft that has an external gear pair composed of a helical gear and a driven helical gear that mesh with each other, and a gear housing chamber that houses the external gear pair, and that supports the helical gear on the drive side. And a casing having a bearing for housing a driven shaft for supporting the helical gear, and a pair accommodated in both sides of the helical gear accommodated in the casing and housed in the casing. And a hydraulic mechanism that has a hydraulic chamber and presses the drive shaft and the driven shaft in the anti-thrust direction by the hydraulic pressure introduced into the hydraulic chamber, and the hydraulic chamber of the hydraulic mechanism has a high pressure side. And a high-pressure hydraulic fluid introduction passage that guides the hydraulic fluid from the hydraulic pressure mechanism, and the hydraulic pressure mechanism presses the drive shaft and the driven shaft in the anti-thrust direction at a value that exceeds the maximum value of the fluctuating thrust. It is characterized by setting Gear pump or motor.
PCT/JP2012/064937 2012-06-11 2012-06-11 Gear pump or motor WO2013186839A1 (en)

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PCT/JP2012/064937 WO2013186839A1 (en) 2012-06-11 2012-06-11 Gear pump or motor
JP2014520825A JP6119748B2 (en) 2012-06-11 2012-06-11 Gear pump or motor
TW102120463A TW201350681A (en) 2012-06-11 2013-06-10 Gear pump and motor

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JP5654717B1 (en) * 2014-03-20 2015-01-14 住友精密工業株式会社 Hydraulic device
WO2016052570A1 (en) * 2014-09-30 2016-04-07 ダイキン工業株式会社 Gear pump or gear motor

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CN106471253B (en) * 2014-05-28 2018-05-22 株式会社岛津制作所 gear pump or motor
KR102009908B1 (en) * 2018-05-15 2019-08-14 김범열 Helical gear pump

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JPH0213185U (en) * 1988-06-30 1990-01-26
JPH04228892A (en) * 1990-06-30 1992-08-18 Kobe Steel Ltd Oil injection type screw compressor

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JPH0213185U (en) * 1988-06-30 1990-01-26
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JP5654717B1 (en) * 2014-03-20 2015-01-14 住友精密工業株式会社 Hydraulic device
WO2015140986A1 (en) * 2014-03-20 2015-09-24 住友精密工業株式会社 Hydraulic device
WO2016052570A1 (en) * 2014-09-30 2016-04-07 ダイキン工業株式会社 Gear pump or gear motor
JP2016070210A (en) * 2014-09-30 2016-05-09 ダイキン工業株式会社 Gear pump or gear motor
US20170298934A1 (en) * 2014-09-30 2017-10-19 Daikin Industries, Ltd. Gear pump and gear motor
EP3203083A4 (en) * 2014-09-30 2018-03-28 Daikin Industries, Ltd. Gear pump or gear motor
US10267309B2 (en) 2014-09-30 2019-04-23 Daikin Industries, Ltd. Gear pump and gear motor

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TW201350681A (en) 2013-12-16
JP6119748B2 (en) 2017-04-26
JPWO2013186839A1 (en) 2016-02-01

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