WO2016181520A1 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
WO2016181520A1
WO2016181520A1 PCT/JP2015/063741 JP2015063741W WO2016181520A1 WO 2016181520 A1 WO2016181520 A1 WO 2016181520A1 JP 2015063741 W JP2015063741 W JP 2015063741W WO 2016181520 A1 WO2016181520 A1 WO 2016181520A1
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Prior art keywords
gear
pressure
sliding surface
pressure side
side plate
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PCT/JP2015/063741
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French (fr)
Japanese (ja)
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次則 石中
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株式会社 島津製作所
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Priority to JP2017517536A priority Critical patent/JP6350744B2/en
Priority to PCT/JP2015/063741 priority patent/WO2016181520A1/en
Publication of WO2016181520A1 publication Critical patent/WO2016181520A1/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
    • F04C2/18Rotary-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 similar tooth forms

Abstract

A gear pump provided with: a casing having in the interior a gear storage chamber for storing a pair of gears; a movable side plate having a high-pressure entry groove in a high-pressure-side region of a sliding surface, which is the surface of a side that lies between the casing and the gears and that faces the gears; and a gasket that is provided to a non-sliding surface, which is the surface of the side opposite from the side facing the gears of the movable side plate, and that sections the space between the non-sliding surface and the casing into a high-pressure side and a low-pressure side; wherein a liquid-membrane-forming concavity is provided to the region where the low-pressure side changes to the high-pressure side in the sliding surface of the movable side plate, in order to suppress liquid membrane rupturing between the gears and the movable side plate and abnormal wear that occurs with such rupturing.

Description

歯車ポンプGear pump
 本発明は、互いに噛み合い歯車対を形成する駆動歯車及び従動歯車の歯溝を利用して作動液を送り出す歯車ポンプに関する。 The present invention relates to a gear pump that feeds hydraulic fluid using a tooth space of a drive gear and a driven gear that form a pair of meshing gears.
 従来より、噛合する少なくとも一対の歯車の歯溝を利用して作動液を送り出す歯車ポンプにおいて、これら歯車の側面近傍に可動側板を配設し、作動液の側方への漏れ量を低減せしめることが知られている。この種の歯車ポンプにおける可動側板は、歯車の歯及び側板の摺動面により区成される空間に閉じ込められた作動液の液圧により歯車から離反する方向の力を受けるが、側板の摺動面と反対側の面に高圧の作動液を導き入れることで、この力と相反する力、即ち歯車に接近する方向の力を側板に付与して圧力バランスを保つようにしている。 Conventionally, in a gear pump that sends hydraulic fluid using the tooth grooves of at least a pair of gears that mesh with each other, a movable side plate is provided near the side surface of these gears to reduce the amount of hydraulic fluid leaked to the side. It has been known. The movable side plate in this type of gear pump receives a force in the direction away from the gear due to the hydraulic pressure of the working fluid confined in the space defined by the gear teeth and the sliding surface of the side plate. By introducing high-pressure hydraulic fluid into the surface opposite to the surface, a force opposite to this force, that is, a force in the direction approaching the gears, is applied to the side plate to maintain the pressure balance.
 具体的には、前記可動側板の非摺動面側に、該非摺動面及びケーシングの内周面に密着して可動側板の非摺動面とケーシングとの間の空間を低圧側と高圧側とに区画するガスケットを予め配設し、このガスケットよりも高圧側に高圧の作動液を導入する。一方、前記可動側板の摺動面の外周縁には、軸受荷重を軽減させるために高圧導入溝を設けている。ここで、歯溝が前記高圧導入溝と連通している部位では、歯溝内の作動液も高圧である。 Specifically, on the non-sliding surface side of the movable side plate, the space between the non-sliding surface of the movable side plate and the casing is in close contact with the non-sliding surface and the inner peripheral surface of the casing. A gasket is provided in advance, and high-pressure hydraulic fluid is introduced to the high-pressure side of the gasket. On the other hand, a high-pressure introduction groove is provided on the outer peripheral edge of the sliding surface of the movable side plate to reduce the bearing load. Here, at the site where the tooth gap communicates with the high pressure introduction groove, the hydraulic fluid in the tooth gap is also at a high pressure.
 ところで、高低圧の切り替わり部位、より具体的にはガスケットの低圧側端縁と高圧導入溝の低圧側端縁との間に対応する部位では、液圧は以下の通りである。すなわち、非摺動面側では、ガスケット及びケーシングにより区成される高圧側の空間内には高圧の作動液が導入されており、可動側板が受ける圧力は低圧側に向かうにつれ吸入ポート側の圧力に向かい漸次低下している。一方、摺動面側において歯溝が前記高圧導入溝に連通していない部位の液圧は吸入ポート側の圧力に等しい。従って、高低圧の切り替わり部位においては非摺動面側の方が高圧となる。可動側板が摺動面側と非摺動面側との間の圧力差により受ける力は、歯車が回転していることから時間の経過に伴い変動する。そこで、非摺動面側の高圧側及び低圧側の領域の大きさは、通常は前記力の大きさの平均が適正となるように決定される(例えば、特許文献1を参照)。 By the way, the hydraulic pressure is as follows at the portion corresponding to the high-low pressure switching portion, more specifically, the portion corresponding to between the low-pressure side edge of the gasket and the low-pressure side edge of the high-pressure introduction groove. That is, on the non-sliding surface side, high-pressure hydraulic fluid is introduced into the high-pressure side space defined by the gasket and casing, and the pressure received by the movable side plate is the pressure on the suction port side as it goes to the low-pressure side. It is gradually decreasing toward. On the other hand, the fluid pressure at the portion where the tooth groove does not communicate with the high pressure introduction groove on the sliding surface side is equal to the pressure on the suction port side. Therefore, the non-sliding surface side has a higher pressure at the high / low pressure switching portion. The force that the movable side plate receives due to the pressure difference between the sliding surface side and the non-sliding surface side varies with the passage of time because the gear rotates. Therefore, the sizes of the high-pressure side and the low-pressure side region on the non-sliding surface side are usually determined so that the average of the magnitudes of the forces is appropriate (see, for example, Patent Document 1).
 しかし、歯車が回転しているときには可動側板が摺動面側に向けて受ける作用の大きさが前記平均より大きくなることがある。しかも、高低圧の切り替わり部位において、摺動面側には高圧の作動液が導入されていない。これらのことから、歯車の側面と可動側板の摺動面との間に液膜切れが生じ、さらに異常摩耗が生じることがある。 However, when the gear is rotating, the magnitude of the action that the movable side plate receives toward the sliding surface side may be larger than the average. In addition, no high pressure hydraulic fluid is introduced into the sliding surface at the high / low pressure switching site. For these reasons, a liquid film breakage may occur between the side surface of the gear and the sliding surface of the movable side plate, and abnormal wear may occur.
特開2005-330858号公報JP 2005-330858 A
 本発明は以上の点に着目し、歯車と可動側板との間の液膜切れやそれに伴う異常摩耗の発生を抑制することにより、歯数や歯の形状に関わらず、液圧を利用して可動側板を歯車に向けて適切な力で押圧させるべく設計できるようにすることを目的とする。 The present invention pays attention to the above points, and by utilizing the hydraulic pressure regardless of the number of teeth and the shape of the teeth by suppressing the occurrence of liquid film breakage between the gear and the movable side plate and the accompanying abnormal wear. An object is to enable the movable side plate to be designed to be pressed against the gear with an appropriate force.
 以上の課題を解決すべく、本発明に係る歯車ポンプは、以下に述べるような構成を有する。すなわち本発明に係る歯車ポンプは、対をなす歯車を収納する歯車収納室を内部に備えたケーシングと、ケーシングと歯車との間に介在し歯車に向かう側の面である摺動面における高圧側の部位に高圧導入溝を有する可動側板と、この可動側板の歯車に向かう側と反対側の面である非摺動面に設けられ該非摺動面とケーシングとの間の空間を高圧側と低圧側とに区画するガスケットとを備えた歯車ポンプであって、前記可動側板の摺動面における低圧側から高圧側の切り替わり部位に、液膜形成用凹部を設けている。 In order to solve the above problems, the gear pump according to the present invention has a configuration as described below. That is, the gear pump according to the present invention includes a casing having a gear housing chamber for housing a pair of gears, and a high-pressure side on a sliding surface that is a surface that is interposed between the casing and the gear and faces the gear. The movable side plate having a high-pressure introduction groove at the portion and a non-sliding surface which is a surface opposite to the gear side of the movable side plate are provided with a space between the non-sliding surface and the casing in the high-pressure side and the low-pressure side. A gear pump having a gasket divided into a side and a liquid film forming recess is provided at a switching portion from the low pressure side to the high pressure side on the sliding surface of the movable side plate.
 このようなものであれば、歯溝内を低圧側から高圧側に移動する作動液の一部が液膜形成用凹部内に導かれるので、当該部位における摺動面側と非摺動面側との圧力差に関わらず摺動面側に作動液膜を発生させることができる。すなわち、当該部位における液膜切れの発生を抑制することができる。従って、歯数や歯の形状に関わらず、液圧を利用して可動側板を歯車に向けて適切な力で押圧させるべく設計できる。そしてこのことにより、安定して高い性能を発揮するポンプを設計することができる。その上、ケーシングや可動側板における加工の誤差に関わらず歯車と可動側板との間の液膜切れの発生を抑制できるので、このような歯車ポンプの生産性を高めることもできる。 In such a case, a part of the working fluid that moves from the low pressure side to the high pressure side in the tooth gap is guided into the recess for forming the liquid film. A hydraulic fluid film can be generated on the sliding surface side regardless of the pressure difference. That is, the occurrence of the liquid film breakage at the site can be suppressed. Therefore, regardless of the number of teeth and the shape of the teeth, the movable side plate can be designed to be pressed toward the gear with an appropriate force using the hydraulic pressure. This makes it possible to design a pump that stably exhibits high performance. In addition, since the occurrence of a liquid film breakage between the gear and the movable side plate can be suppressed regardless of processing errors in the casing and the movable side plate, the productivity of such a gear pump can be increased.
 なお、本発明において、「低圧側から高圧側の切り替わり部位」とは、前記ガスケットの低圧側端縁と前記高圧導入溝の低圧側端縁との間に対応する回転位相の歯に対向する部位を示す概念である。 In the present invention, the “switching portion from the low pressure side to the high pressure side” means a portion facing the tooth of the corresponding rotation phase between the low pressure side edge of the gasket and the low pressure side edge of the high pressure introduction groove. It is the concept which shows.
 前記液膜形成用凹部の具体的な態様の例として、有底で低圧側と高圧側を連通しない液だめ穴や、有底で低圧側と高圧側を連通する液導入溝が挙げられる。 Examples of specific embodiments of the recess for forming a liquid film include a liquid reservoir hole that is bottomed and does not communicate between the low pressure side and the high pressure side, and a liquid introduction groove that is bottomed and communicates between the low pressure side and the high pressure side.
 本発明によれば、歯車と可動側板との間の液膜切れやそれに伴う異常摩耗の発生を抑制することにより、歯数や歯の形状に関わらず、液圧を利用して可動側板を歯車に向けて適切な力で押圧させるべく設計できる。 According to the present invention, by suppressing the occurrence of liquid film breakage between the gear and the movable side plate and the accompanying abnormal wear, the movable side plate is geared using the hydraulic pressure regardless of the number of teeth and the shape of the teeth. Can be designed to be pressed with an appropriate force toward
本発明の第一実施形態に係る歯車ポンプの構成を示す概略図。Schematic which shows the structure of the gear pump which concerns on 1st embodiment of this invention. 同実施形態に係る可動側板を示す正面図。The front view which shows the movable side plate which concerns on the same embodiment. 同実施形態に係る可動側板を示す背面図。The rear view which shows the movable side plate which concerns on the same embodiment. 同実施形態に係る可動側板の要部を示す図。The figure which shows the principal part of the movable side plate which concerns on the same embodiment. 本発明の第二実施形態に係る可動側板の要部を示す図。The figure which shows the principal part of the movable side plate which concerns on 2nd embodiment of this invention.
 本発明の第一実施形態を図1~図4を参照しつつ以下に説明する。 A first embodiment of the present invention will be described below with reference to FIGS.
 本実施形態に係る歯車ポンプPは、図1に示すように、主として、歯車収納室11aを内部に有するケーシング1と、このケーシング1の歯車収納室11a内に収納保持され互いに噛み合わせてなる外接歯車対、すなわち駆動歯車2及び従動歯車3と、各歯車2、3の両側面2a、3aに添接する可動側板6、6とを具備する。 As shown in FIG. 1, the gear pump P according to the present embodiment mainly includes a casing 1 having a gear housing chamber 11 a therein, and a circumscribed portion that is housed and held in the gear housing chamber 11 a of the casing 1 and meshes with each other. A gear pair, that is, a drive gear 2 and a driven gear 3, and movable side plates 6 and 6 that are in contact with both side surfaces 2 a and 3 a of the gears 2 and 3 are provided.
 駆動歯車2及び従動歯車3は、複数の歯体を外周面に沿って所定間隔で設けた周知のものである。なお、本実施形態では、前記駆動歯車2の中心から駆動軸4を回転軸方向に一体に延伸させて設けているとともに、従動歯車3から従動軸5を回転軸方向に一体に延伸させて設けているが、駆動歯車2と駆動軸4とを別体に構成してもよく、また、従動歯車3と従動軸5とを別体に構成してもよい。 The driving gear 2 and the driven gear 3 are well-known gears in which a plurality of tooth bodies are provided at predetermined intervals along the outer peripheral surface. In the present embodiment, the drive shaft 4 is integrally extended from the center of the drive gear 2 in the rotational axis direction, and the driven shaft 5 is integrally extended from the driven gear 3 in the rotational axis direction. However, the drive gear 2 and the drive shaft 4 may be configured separately, and the driven gear 3 and the driven shaft 5 may be configured separately.
 ケーシング1は、図1に示すように、前記歯車収納室11aを有するボディ11と、この歯車収納室11aの開口面を閉塞するカバーたるフロントカバー12と、前記歯車収納室11aの開口面を閉塞するカバーたるリアカバー13とから構成したものである。ボディ11には、前記歯車対すなわち駆動歯車2及び従動歯車3を噛合状態で収容する略眼鏡状の歯車収納室11aが形成されている。また、ボディ11には、図示は省略しているが、前記駆動歯車2と従動歯車3との噛合部位に臨む位置に図1には示していない吸込口X及び吐出口Yをそれぞれ開口させてある。前記フロントカバー12は、例えばボディ11にボルト等によって着脱可能に装着されて前記歯車収納室11aの前側開口面を閉塞するものであり、前記駆動軸4及び従動軸5がそれぞれ嵌入可能な軸受孔12a、12bが形成さている。駆動歯車2を挿入すべき位置寄りの軸受孔12aにはブッシュ7を嵌装し、このブッシュ7に前記駆動軸4の一端部を挿入し回転可能に軸承している。一方、従動歯車3を挿入すべき位置寄りの軸受孔12bにもブッシュ7を嵌装していて、このブッシュ7に前記従動軸5の一端部を挿入し回転可能に軸承している。同様に、前記リアカバー13も、前記ボディ11にボルト等によって着脱可能に装着されて前記歯車収納室11aの後側開口面を閉塞するものであり、前記駆動軸4及び従動軸5がそれぞれ嵌入可能な軸受孔13a、13bが形成さている。駆動歯車2を挿入すべき位置寄りの軸受孔13aにはブッシュ7を嵌装し、このブッシュ7に前記駆動軸4の他端部を挿入し回転可能に軸承している。一方、従動歯車3を挿入すべき位置寄りの軸受孔13bにもブッシュ7を嵌装していて、このブッシュ7に前記従動軸5の他端部を挿入し回転可能に軸承している。なお、ボディ11とフロントカバー12とを一体に構成しリアカバー13により歯車収納室11aを後方から閉塞する構成や、ボディ11とリアカバー13とを一体に構成しフロントカバー12により歯車収納室11aを前方から閉塞する構成を採用してももちろんよい。 As shown in FIG. 1, the casing 1 includes a body 11 having the gear housing chamber 11a, a front cover 12 serving as a cover for closing the opening surface of the gear housing chamber 11a, and an opening surface of the gear housing chamber 11a. It is comprised from the rear cover 13 which is a cover. The body 11 is formed with a substantially glasses-like gear housing chamber 11a for housing the gear pair, that is, the driving gear 2 and the driven gear 3 in a meshed state. Although not shown, the body 11 has a suction port X and a discharge port Y which are not shown in FIG. 1 opened at positions facing the meshing portion of the drive gear 2 and the driven gear 3. is there. The front cover 12 is detachably attached to the body 11 with a bolt or the like, for example, and closes the front opening surface of the gear housing chamber 11a, and a bearing hole into which the drive shaft 4 and the driven shaft 5 can be respectively fitted. 12a and 12b are formed. A bush 7 is fitted into the bearing hole 12a near the position where the drive gear 2 is to be inserted, and one end of the drive shaft 4 is inserted into the bush 7 so as to be rotatably supported. On the other hand, a bush 7 is fitted into the bearing hole 12b near the position where the driven gear 3 is to be inserted, and one end of the driven shaft 5 is inserted into the bush 7 so as to be rotatably supported. Similarly, the rear cover 13 is also detachably attached to the body 11 with a bolt or the like and closes the rear opening surface of the gear housing chamber 11a, and the drive shaft 4 and the driven shaft 5 can be respectively inserted thereinto. Bearing holes 13a and 13b are formed. A bush 7 is fitted in the bearing hole 13a near the position where the drive gear 2 is to be inserted, and the other end of the drive shaft 4 is inserted into the bush 7 so as to be rotatably supported. On the other hand, a bush 7 is also fitted in the bearing hole 13b near the position where the driven gear 3 is to be inserted, and the other end of the driven shaft 5 is inserted into the bush 7 so as to be rotatably supported. The body 11 and the front cover 12 are integrally formed, and the gear storage chamber 11a is closed from the rear by the rear cover 13, or the body 11 and the rear cover 13 are integrally formed and the gear cover chamber 11a is forwarded by the front cover 12. Of course, it is also possible to adopt a structure that closes from the outside.
 可動側板6は、図1に示すように、前記駆動歯車2及び従動歯車3の両側面2a、3aに添接させるべく2箇所に配され、駆動歯車2及び従動歯車3の各側面2a、3aをそれぞれシールするためのものである。この可動側板6の摺動面6aの外周縁には、図2に示すように、軸受荷重を軽減させるために高圧導入溝6xを設けている。ここで、可動側板6の摺動面6a側のうち、図2の斜線で示す領域に吐出口Yから高圧の作動液が導入される。一方、図3に示すように、前記可動側板6の非摺動面6bにはガスケット溝6yを設けていて、このガスケット溝6yにガスケット8を嵌め入れるようにしている。このガスケット溝6yは、可動側板6の外周に向けて開口する高圧導入部6y2と、外周縁が可動側板6の外周より内側に位置し低圧側端縁が前記高圧導入溝6aの低圧側端縁より低圧側に達している周回部6y1とを有する。そして、ケーシング1に前記駆動歯車2、従動歯車3及びこの可動側板6、6を収容した状態で、この可動側板6の非摺動面6bとケーシング1との間に高圧流体を導き入れることが可能な圧力バランス領域が形成される。 As shown in FIG. 1, the movable side plate 6 is disposed at two locations so as to be brought into contact with both side surfaces 2 a and 3 a of the drive gear 2 and the driven gear 3, and the side surfaces 2 a and 3 a of the drive gear 2 and the driven gear 3. It is for sealing each. As shown in FIG. 2, a high-pressure introduction groove 6x is provided on the outer peripheral edge of the sliding surface 6a of the movable side plate 6 in order to reduce the bearing load. Here, high-pressure hydraulic fluid is introduced from the discharge port Y into the region indicated by the oblique lines in FIG. 2 on the sliding surface 6 a side of the movable side plate 6. On the other hand, as shown in FIG. 3, a gasket groove 6y is provided in the non-sliding surface 6b of the movable side plate 6, and the gasket 8 is fitted into the gasket groove 6y. The gasket groove 6y includes a high-pressure introduction portion 6y2 that opens toward the outer periphery of the movable side plate 6, and an outer peripheral edge located on the inner side of the outer periphery of the movable side plate 6 and a low-pressure side edge that is a low-pressure side edge of the high-pressure introduction groove 6a. And the surrounding portion 6y1 reaching the lower pressure side. Then, in a state where the drive gear 2, the driven gear 3 and the movable side plates 6 and 6 are accommodated in the casing 1, high-pressure fluid can be introduced between the non-sliding surface 6 b of the movable side plate 6 and the casing 1. A possible pressure balance region is formed.
 前記ガスケット8は、上述したように、前記ガスケット溝6y内に装着され、前記圧力バランス領域を低圧側すなわち吸込口X側と高圧側すなわち吐出口Y側とに区画する。ここで、図3の斜線で示す領域が高圧側領域である。また、このガスケット8は、図3に示すように、前記ガスケット溝6yの周回部6y1に装着されるガスケット本体81と、前記ガスケット溝6yの高圧導入部6y2を閉塞する閉塞部82とを備えている。このガスケット8の低圧側の端縁は、前記高圧導入溝6xの低圧側の端縁6x1よりもさらに低圧側に達している。 As described above, the gasket 8 is mounted in the gasket groove 6y, and divides the pressure balance region into a low pressure side, that is, a suction port X side and a high pressure side, that is, a discharge port Y side. Here, a region indicated by diagonal lines in FIG. 3 is a high-pressure side region. Further, as shown in FIG. 3, the gasket 8 includes a gasket body 81 attached to the circumferential portion 6y1 of the gasket groove 6y, and a closing portion 82 for closing the high pressure introduction portion 6y2 of the gasket groove 6y. Yes. The low-pressure end edge of the gasket 8 reaches the low-pressure side further than the low-pressure end edge 6x1 of the high-pressure introduction groove 6x.
 この歯車ポンプPは、一端を外部に延出させてなる前記駆動軸4を介して前記駆動歯車2及び従動歯車3を同期逆回転駆動した場合に、吸込口Xと吐出口Yとの間で高低圧差が生じ、前記駆動歯車2及び従動歯車3の歯体(図示略)同士が漸次離反する側のボディ11内空間、つまり前記吸込口X側が低圧領域になるとともに、歯体同士が漸次噛合する側のボディ11内空間、つまり吐出口Y側が高圧領域になる。 When the drive gear 2 and the driven gear 3 are driven synchronously and reversely via the drive shaft 4 having one end extended to the outside, the gear pump P is connected between the suction port X and the discharge port Y. A difference between high and low pressure occurs, and the toothed body (not shown) of the drive gear 2 and the driven gear 3 gradually separates from each other, the inner space of the body 11, that is, the suction port X side becomes a low pressure region, and the toothed bodies gradually mesh with each other. The space inside the body 11 on the side to be operated, that is, the discharge port Y side becomes a high pressure region.
 そして、吸込口Xより導入した作動液を、前記駆動歯車2及び従動歯車3の歯先とケーシング1の内周との間に閉成される容積空間に閉じ込めて吐出口Yにまで導き吐出するポンプ作用を営むようにしている。 Then, the hydraulic fluid introduced from the suction port X is confined in a volume space closed between the tooth tips of the drive gear 2 and the driven gear 3 and the inner periphery of the casing 1 and guided to the discharge port Y to be discharged. The pump is operated.
 しかして本実施形態では、図4に示すように、前記可動側板6の摺動面6aにおける低圧側から高圧側の切り替わり部位に、液膜形成用凹部たる液だめ穴6zを設けている。より具体的には、歯車2の歯の1つの歯先2bが前記ガスケット8の低圧側の端縁8xに達した時点でその歯に対向する部位から、歯車の歯の1つの歯先2bが前記高圧導入溝6xの低圧側の端縁6x1に達した時点でその歯に対向する部位にかけての部位、すなわち図4において薄墨を付した部位に、液膜形成用凹部たる液だめ穴6zを複数設けている。液だめ穴6zは、有底で低圧側と高圧側を連通しない凹部である。また、本実施形態では、前記部位にこの液だめ穴6zを多数ランダムに配置している。なお、図4においては、歯車2を想像線で示している。また、同図においては駆動歯車2側のみを示しているが、従動歯車3側にも同様に前記液だめ穴6zを設けている。 In the present embodiment, however, as shown in FIG. 4, a liquid reservoir hole 6z which is a recess for forming a liquid film is provided at a switching portion from the low pressure side to the high pressure side on the sliding surface 6a of the movable side plate 6. More specifically, when one tooth tip 2b of the tooth of the gear 2 reaches the low-pressure side edge 8x of the gasket 8, one tooth tip 2b of the gear tooth is formed from a portion facing the tooth 8b. When reaching the low pressure side edge 6x1 of the high pressure introduction groove 6x, a plurality of reservoir holes 6z, which are the recesses for forming a liquid film, are formed on the part facing the tooth, that is, the part marked with light ink in FIG. Provided. The liquid reservoir hole 6z is a recess having a bottom and does not communicate with the low pressure side and the high pressure side. In the present embodiment, a large number of the reservoir holes 6z are randomly arranged in the portion. In FIG. 4, the gear 2 is indicated by an imaginary line. Although only the drive gear 2 side is shown in the figure, the liquid reservoir hole 6z is similarly provided on the driven gear 3 side.
 ここで、低圧側から高圧側の切り替わり部位においては、摺動面6a側の歯溝内の作動液が低圧であるのに対して、非摺動面6b側の作動液はより高圧である。しかし、摺動面6aの該当箇所には前記液だめ穴6zが形成されており、低圧側から導かれた作動液の一部はこの液だめ穴6z内に導かれる。そして、この液だめ穴6z内の作動液により液膜が形成される。 Here, in the switching portion from the low pressure side to the high pressure side, the hydraulic fluid in the tooth gap on the sliding surface 6a side is low pressure, whereas the hydraulic fluid on the non-sliding surface 6b side is higher pressure. However, the liquid reservoir hole 6z is formed at a corresponding portion of the sliding surface 6a, and a part of the hydraulic fluid guided from the low pressure side is guided into the liquid reservoir hole 6z. A liquid film is formed by the working liquid in the liquid reservoir hole 6z.
 すなわち本実施形態によれば、低圧側から高圧側の切り替わり部位において、当該部位における摺動面6a側と非摺動面6b側との圧力差に関わらず摺動面6a側に作動液膜を発生させることができる。従って、当該部位における液膜切れの発生を抑制することができる。そして、液膜切れに伴う異常摩耗の発生を抑制することにより、歯数や歯の形状に関わらず、液圧を利用して可動側板6を歯車2、3に向けて適切な力で押圧させるべく設計できる。その上、ケーシング1や可動側板6における加工の誤差に関わらず歯車2、3と可動側板6との間の液膜切れの発生を抑制できるので、このような歯車ポンプの生産性を高めることもできる。 That is, according to the present embodiment, the hydraulic fluid film is provided on the sliding surface 6a side in the switching portion from the low pressure side to the high pressure side regardless of the pressure difference between the sliding surface 6a side and the non-sliding surface 6b side in the portion. Can be generated. Therefore, it is possible to suppress the occurrence of the liquid film breakage at the site. Then, by suppressing the occurrence of abnormal wear due to the liquid film breakage, the movable side plate 6 is pressed toward the gears 2 and 3 with an appropriate force using the hydraulic pressure regardless of the number of teeth and the shape of the teeth. Can be designed as needed. In addition, the occurrence of a liquid film breakage between the gears 2 and 3 and the movable side plate 6 can be suppressed regardless of processing errors in the casing 1 and the movable side plate 6, so that the productivity of such a gear pump can be improved. it can.
 次いで、本発明の第二実施形態を図5を参照しつつ以下に示す。第二実施形態に係る歯車ポンプは、以下に述べる相違点の他は上述した第一実施形態に係るものと同様の構成を有する。そこで、上述した第一実施形態におけるものに対応する各部位には、同一の名称及び符号を付し、詳細な説明は省略する。 Next, a second embodiment of the present invention will be described below with reference to FIG. The gear pump according to the second embodiment has the same configuration as that according to the first embodiment described above except for the differences described below. Therefore, the parts corresponding to those in the first embodiment described above are denoted by the same names and symbols, and detailed description thereof is omitted.
 本実施形態では、図5に示すように、前記可動側板6の摺動面6aにおける低圧側から高圧側の切り替わり部位に、液膜形成用凹部たる液導入溝6mを設けている。より具体的には、歯車2の歯の1つの歯先2bが前記ガスケット8の低圧側の端縁8xに達した時点でその歯に対向する部位から、歯車の歯の1つの歯先2bが前記高圧導入溝6xの低圧側の端縁に達した時点でその歯に対向する部位にかけての部位に、すなわち図5において薄墨を付した部位に、前記液導入溝6mを複数設けている。液導入溝6mは、有底で低圧側と高圧側を連通する溝である。また、この液導入溝6mは、駆動軸4又は従動軸5の軸心を中心とする円周方向に伸びている。前記液導入溝6mの幅及び深さは、ともに数μmである。なお、図5においては、歯車2を想像線で示している。また、同図においては駆動歯車2側のみを示しているが、従動歯車3側にも同様に前記液導入溝6mを設けている。さらに、同図においては、液導入溝6mをわかりやすくするために実際より液導入溝6mの幅を大きく描いており、液導入溝6mを3本のみ描いているが、実際には、前記領域内に液導入溝6mを数μm~数十μmの間隔で多数設けている。 In the present embodiment, as shown in FIG. 5, a liquid introduction groove 6 m serving as a liquid film forming recess is provided at a switching portion from the low pressure side to the high pressure side on the sliding surface 6 a of the movable side plate 6. More specifically, when one tooth tip 2b of the tooth of the gear 2 reaches the low-pressure side edge 8x of the gasket 8, one tooth tip 2b of the gear tooth is formed from a portion facing the tooth 8b. A plurality of the liquid introduction grooves 6m are provided in a portion of the high pressure introduction groove 6x that reaches the low pressure side edge of the high pressure introduction groove 6x, that is, a portion that faces the tooth, that is, a portion that is marked with light ink in FIG. The liquid introduction groove 6m is a bottomed groove that communicates the low pressure side and the high pressure side. The liquid introduction groove 6 m extends in the circumferential direction around the axis of the drive shaft 4 or the driven shaft 5. Both the width and the depth of the liquid introduction groove 6m are several μm. In FIG. 5, the gear 2 is indicated by an imaginary line. Although only the drive gear 2 side is shown in the figure, the liquid introduction groove 6m is similarly provided on the driven gear 3 side. Furthermore, in the same figure, in order to make the liquid introduction groove 6m easy to understand, the width of the liquid introduction groove 6m is drawn larger than the actual, and only three liquid introduction grooves 6m are drawn. A large number of liquid introduction grooves 6m are provided at intervals of several μm to several tens of μm.
 ここで、低圧側から高圧側の切り替わり部位においては、摺動面6a側の歯溝内の作動液が低圧であるのに対して、非摺動面6b側の作動液はより高圧である。しかし、該当箇所には前記液導入溝6mが形成されており、この液導入溝6m内を高圧側から低圧側に向けて微量の作動液が流通する。そして、この液導入溝6m内を流通する作動液により液膜が形成される。 Here, in the switching portion from the low pressure side to the high pressure side, the hydraulic fluid in the tooth gap on the sliding surface 6a side is low pressure, whereas the hydraulic fluid on the non-sliding surface 6b side is higher pressure. However, the liquid introduction groove 6m is formed at the corresponding location, and a small amount of hydraulic fluid flows through the liquid introduction groove 6m from the high pressure side to the low pressure side. Then, a liquid film is formed by the working fluid flowing through the liquid introduction groove 6m.
 すなわち本実施形態によっても、上述した第一実施形態と同様に、低圧側から高圧側の切り替わり部位において、当該部位における摺動面6a側と非摺動面6b側との圧力差に関わらず摺動面6a側に作動液膜を発生させることができる。従って、当該部位における液膜切れの発生を抑制することができる。そして、液膜切れに伴う異常摩耗の発生を抑制することにより、歯数や歯の形状に関わらず、液圧を利用して可動側板6を歯車2、3に向けて適切な力で押圧させるべく設計できる。その上、本実施形態によっても、ケーシング1や可動側板6における加工の誤差に関わらず歯車2、3と可動側板6との間の液膜切れの発生を抑制できるので、このような歯車ポンプの生産性を高めることもできる。 That is, also in the present embodiment, as in the first embodiment described above, the sliding portion from the low pressure side to the high pressure side is slid regardless of the pressure difference between the sliding surface 6a side and the non-sliding surface 6b side at that portion. A working fluid film can be generated on the moving surface 6a side. Therefore, it is possible to suppress the occurrence of the liquid film breakage at the site. Then, by suppressing the occurrence of abnormal wear due to the liquid film breakage, the movable side plate 6 is pressed toward the gears 2 and 3 with an appropriate force using the hydraulic pressure regardless of the number of teeth and the shape of the teeth. Can be designed as needed. In addition, according to this embodiment, the occurrence of a liquid film breakage between the gears 2 and 3 and the movable side plate 6 can be suppressed regardless of processing errors in the casing 1 and the movable side plate 6. Productivity can also be increased.
 なお、本発明は以上に述べた第一及び第二実施形態に限らない。 The present invention is not limited to the first and second embodiments described above.
 例えば、上述した第一実施形態においては、液膜形成用凹部たる液だめ穴を円形に形成しているが、液だめ穴の形状は、例えば多角形状等、任意に設定してよい。また、同実施形態においては、液だめ穴をランダムに配置しているが、液だめ穴の配置も任意に設定してよい。加えて、液だめ穴の数、深さ及び該液だめ穴の開口の大きさは任意に設定してよい。 For example, in the first embodiment described above, the liquid reservoir hole that is the recess for forming the liquid film is formed in a circular shape, but the shape of the liquid reservoir hole may be arbitrarily set, for example, a polygonal shape. In the embodiment, the reservoir holes are randomly arranged, but the arrangement of the reservoir holes may be arbitrarily set. In addition, the number and depth of the reservoir holes and the size of the opening of the reservoir holes may be arbitrarily set.
 一方、上述した第二実施形態において、液膜形成用凹部たる液導入溝の幅、深さ、形状及び本数は任意に設定してよい。 On the other hand, in the above-described second embodiment, the width, depth, shape, and number of liquid introduction grooves that are liquid film forming recesses may be arbitrarily set.
 その他、本発明の趣旨を損ねない範囲で種々に変更してよい。 Other various modifications may be made without departing from the spirit of the present invention.
 本発明によれば、歯車ポンプにおいて、歯車と可動側板との間の液膜切れやそれに伴う異常摩耗の発生を抑制することにより、歯数や歯の形状に関わらず、液圧を利用して可動側板を歯車に向けて適切な力で押圧させるべく設計できる。 According to the present invention, in the gear pump, by suppressing the occurrence of liquid film breakage between the gear and the movable side plate and the accompanying abnormal wear, the hydraulic pressure is utilized regardless of the number of teeth and the shape of the teeth. The movable side plate can be designed to be pressed against the gear with an appropriate force.
 1…ケーシング
 11a…歯車収納室
 2、3…歯車
 6…可動側板
 6a…摺動面
 6b…非摺動面
 6x…高圧導入溝
 6z…液膜形成用凹部(液だめ穴)
 6m…液膜形成用凹部(液導入溝)
 8…ガスケット
DESCRIPTION OF SYMBOLS 1 ... Casing 11a ... Gear accommodation chamber 2, 3 ... Gear 6 ... Movable side plate 6a ... Sliding surface 6b ... Non-sliding surface 6x ... High pressure introduction groove 6z ... Recess for liquid film formation (container hole)
6m ... Liquid film formation recess (liquid introduction groove)
8 ... Gasket

Claims (3)

  1. 対をなす歯車を収納する歯車収納室を内部に備えたケーシングと、ケーシングと歯車との間に介在し歯車に向かう側の面である摺動面における高圧側の部位に高圧導入溝を有する可動側板と、この可動側板の歯車に向かう側と反対側の面である非摺動面に設けられ該非摺動面とケーシングとの間の空間を高圧側と低圧側とに区画するガスケットとを備えた歯車ポンプであって、
    前記可動側板の摺動面における低圧側から高圧側の切り替わり部位に、液膜形成用凹部を設けている歯車ポンプ。
    A casing having a gear housing chamber for housing a pair of gears, and a movable having a high-pressure introduction groove in a high-pressure side portion of a sliding surface that is interposed between the casing and the gear and faces the gear A side plate and a gasket that is provided on a non-sliding surface that is a surface opposite to the gear side of the movable side plate and divides a space between the non-sliding surface and the casing into a high-pressure side and a low-pressure side. Gear pump,
    A gear pump in which a recess for forming a liquid film is provided at a switching portion from a low pressure side to a high pressure side on a sliding surface of the movable side plate.
  2. 前記液膜形成用凹部が、有底で低圧側と高圧側を連通しない液だめ穴である請求項1記載の歯車ポンプ。 The gear pump according to claim 1, wherein the liquid film forming recess is a liquid reservoir hole having a bottom and not communicating between the low pressure side and the high pressure side.
  3. 前記液膜形成用凹部が、有底で低圧側と高圧側を連通する液導入溝である請求項1記載の歯車ポンプ。 The gear pump according to claim 1, wherein the liquid film forming recess is a liquid introduction groove having a bottom and communicating the low pressure side and the high pressure side.
PCT/JP2015/063741 2015-05-13 2015-05-13 Gear pump WO2016181520A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018114919A1 (en) * 2016-12-21 2018-06-28 Robert Bosch Gmbh External gear pump for a waste heat recovery system

Citations (4)

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JP2001099071A (en) * 1999-10-01 2001-04-10 Koyo Seiko Co Ltd Gear pump
US20050058566A1 (en) * 2003-09-11 2005-03-17 Christensen Matthew Peter Gear motor start up control
JP2007239501A (en) * 2006-03-06 2007-09-20 Toyota Industries Corp Gear pump
JP2012077686A (en) * 2010-10-01 2012-04-19 Shimadzu Corp Gear pump or motor

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GB1465021A (en) * 1974-05-07 1977-02-16 Bosch Gmbh Robert Externally-meshing gear pump or gear motor
JPS53114604U (en) * 1977-02-22 1978-09-12
JPS5797197U (en) * 1980-12-05 1982-06-15

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001099071A (en) * 1999-10-01 2001-04-10 Koyo Seiko Co Ltd Gear pump
US20050058566A1 (en) * 2003-09-11 2005-03-17 Christensen Matthew Peter Gear motor start up control
JP2007239501A (en) * 2006-03-06 2007-09-20 Toyota Industries Corp Gear pump
JP2012077686A (en) * 2010-10-01 2012-04-19 Shimadzu Corp Gear pump or motor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018114919A1 (en) * 2016-12-21 2018-06-28 Robert Bosch Gmbh External gear pump for a waste heat recovery system

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JPWO2016181520A1 (en) 2017-10-26

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