JP4952719B2 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
JP4952719B2
JP4952719B2 JP2008533020A JP2008533020A JP4952719B2 JP 4952719 B2 JP4952719 B2 JP 4952719B2 JP 2008533020 A JP2008533020 A JP 2008533020A JP 2008533020 A JP2008533020 A JP 2008533020A JP 4952719 B2 JP4952719 B2 JP 4952719B2
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gear
hole
pressure side
bearing hole
eyeglass
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JPWO2008029477A1 (en
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次則 石中
浩司 小松
巧 石原
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Shimadzu Corp
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Shimadzu Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-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
    • F04C2/14—Rotary-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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-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
    • F04C2/14—Rotary-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
    • F04C2/18—Rotary-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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Description

本発明は、特に建設機械、車両用油圧機械等に適用可能な、歯車ポンプに関するものである。
The present invention relates to a gear pump particularly applicable to construction machines, vehicle hydraulic machines, and the like.

従来、図７及び図８に示すように、駆動歯車Ｘ６１と従動歯車Ｘ６２とを噛合わせてなる歯車対Ｘ６と、この歯車対Ｘ６を収納するめがね穴Ｘ４ａを備えたボディＸ４、及びこのボディＸ４の前方ないし後方を被覆するカバーＸ３，Ｘ５を有しこれらを固定用ボルトＸ８により接続してなるケーシングＸ２とを具備する歯車ポンプＸ１が、建設機械、車両用油圧機械等の油圧供給源として広く用いられてきている。この歯車ポンプＸ１は、前記めがね穴Ｘ４ａに連通する低圧側流路口Ｘ４３から作動液を駆動歯車Ｘ６１と従動歯車Ｘ６２との間の空間に供給し、高圧側流路口Ｘ４１から吐出させる機能を有する。   Conventionally, as shown in FIG. 7 and FIG. 8, a gear pair X6 in which a drive gear X61 and a driven gear X62 are meshed, a body X4 having a spectacle hole X4a for accommodating the gear pair X6, and the body X4. A gear pump X1 having a cover X3 and X5 covering the front or rear of the housing and a casing X2 formed by connecting these covers with fixing bolts X8 is widely used as a hydraulic supply source for construction machines, vehicle hydraulic machines, and the like. It has been used. This gear pump X1 has a function of supplying hydraulic fluid to the space between the drive gear X61 and the driven gear X62 from the low pressure side passage port X43 communicating with the eyeglass hole X4a and discharging it from the high pressure side passage port X41.

近年、このような歯車ポンプＸ１の高圧側に、リリーフ弁や流量制御弁等のバルブを取り付ける要望が存在する。その際、高圧側に取り付けたバルブから低圧側への配管が必要な場合があり、このような配管はこの歯車ポンプＸ１の外部に設けることが多い。
特開２００３−３３６５８３号公報 In recent years, there is a demand for attaching a valve such as a relief valve or a flow control valve on the high pressure side of the gear pump X1. In that case, piping from the valve | bulb attached to the high voltage | pressure side to a low voltage | pressure side may be required, and such piping is often provided in the exterior of this gear pump X1.
JP 2003-336583 A

しかし、高圧側にバルブを取り付けた際、歯車ポンプＸ１の外部に上述した配管を設けると、継手や配管パイプ等が必要となり、さらにこの歯車ポンプＸ１近傍に継手や配管パイプ等を設けるためのスペースを確保する必要がある。そこで、この課題を解決すべく、歯車ポンプＸ１内に、バルブから低圧側ポートまでを連通する連通路を設けることが考えられる。   However, when the above-described piping is provided outside the gear pump X1 when the valve is attached to the high pressure side, a joint, a piping pipe, and the like are required, and a space for providing a joint, a piping pipe, and the like in the vicinity of the gear pump X1. It is necessary to ensure. Therefore, in order to solve this problem, it is conceivable to provide a communication path that communicates from the valve to the low-pressure side port in the gear pump X1.

ところが、ボディＸ４のめがね穴Ｘ４ａと前記ボルトＸ８との間の部分、すなわちめがね穴Ｘ４ａに対応する前後方向位置にこのような連通路を設けると、ボディＸ４のめがね穴Ｘ４ａ近傍の部位が極度に薄肉となり、めがね穴Ｘ４ａが受ける油圧に対する強度が十分得られなくなる別の不具合が発生する。   However, if such a communication path is provided at the position between the eyeglass hole X4a of the body X4 and the bolt X8, that is, the position in the front-rear direction corresponding to the eyeglass hole X4a, the portion near the eyehole X4a of the body X4 is extremely Another problem arises that the thickness of the glass hole X4a is insufficient, and the strength against the hydraulic pressure received by the glasses hole X4a cannot be obtained sufficiently.

本発明は、上記課題を解決すべく構成するものである。   The present invention is configured to solve the above problems.

すなわち、本発明に係る歯車ポンプは、駆動歯車と従動歯車とを噛合させてなる１又は複数の歯車対と、この歯車対を収納するケーシングとを具備し、前記ケーシングが、前記歯車対を収納するめがね穴、このめがね穴に連通し前記歯車対を構成する歯車を枢支する軸を挿通させてなる軸受穴、前記めがね穴に連通し低圧の作動液を吸入する低圧側ポート、前記めがね穴に連通し高圧の作動液を排出する高圧側ポート、及びこの高圧側ポート近傍に設けられバルブを取り付け可能なバルブ取付部を有するボディと、このボディの前方又は後方のうち少なくとも一方に設けられ前記めがね穴を閉塞するカバーとを具備するものであって、前記ボディが、前記めがね穴を設けた部位より厚肉な部位で、前記軸受穴に対して該軸受穴に支持させている軸が液圧により受ける作用の向きと略反対側に前記バルブ取付部から低圧側ポートまでを連通する戻り通路をさらに有することを特徴とする。 That is, the gear pump according to the present invention includes one or a plurality of gear pairs formed by meshing a driving gear and a driven gear, and a casing that stores the gear pairs, and the casing stores the gear pairs. A glasses hole, a bearing hole that is inserted into a shaft that is connected to the eyeglass hole and pivotally supports a gear that constitutes the gear pair, a low pressure side port that is connected to the eyeglass hole and sucks a low-pressure working fluid, and the eyeglass hole A body having a high-pressure side port for discharging high-pressure hydraulic fluid, a valve mounting portion provided near the high-pressure side port to which a valve can be attached, and at least one of the front and rear of the body. It is one that comprises a cover for closing the spectacle hole, the body, the at thick site than the site provided with glasses holes, have to be supported in the bearing hole with respect to the bearing hole Axis and having a is et a return passage communicating to a low pressure side port from the valve attachment portion in a direction substantially opposite of the effect experienced by fluid pressure.

このようなものであれば、ボディの前記軸受穴を設けた部位は前記めがね穴を設けた部位よりも厚肉であるため、戻り通路を設けてもボディの強度は大きく損なわれない。すなわち、ボディの強度を大きく損ねることなく戻り通路を設け、このような歯車ポンプ又はモータを配設する際の部品点数及び取り付けスペースの節減を図ることができる。さらに、ボディのめがね穴周囲の部位を厚肉にして該部位に戻り通路を設ける態様と比較して、ボディ自体を従来のものと比較して厚肉に構成する必要がないため、ボディを製造する際の材料費を節減できる。なお、「前記軸受穴に対応する前後方向位置」とは、前記軸受穴が存在し前記めがね穴が存在しない前後方向位置全般を含む概念である。   If it is such, since the site | part which provided the said bearing hole of the body is thicker than the site | part which provided the said spectacle hole, even if it provides a return channel | path, the intensity | strength of a body will not be impaired significantly. That is, it is possible to reduce the number of parts and the mounting space when the return passage is provided without greatly degrading the strength of the body and the gear pump or the motor is disposed. In addition, compared to the case in which the part around the eyeglass hole of the body is made thick and the return passage is provided in the part, the body itself does not need to be made thicker than the conventional one. Can save material costs. The “front-rear direction position corresponding to the bearing hole” is a concept including all front-rear direction positions where the bearing hole exists and the eyeglass hole does not exist.

本発明は、以上説明したような形態で実施され、以下に記載されるような効果を奏する。   The present invention is implemented in the form as described above, and has the following effects.

すなわち、本発明によれば、軸受穴に対応する前後方向位置ではボディが比較的厚肉であることを利用し、このような位置に戻り通路を設けることにより、ボディの強度を大きく損ねることなく戻り通路を設け、このような歯車ポンプ又はモータを配設する際の部品点数及び取り付けスペースの節減を図ることができる。さらに、ボディのめがね穴周囲の部位を厚肉にして該部位に戻り通路を設ける態様と比較して、ボディ自体を従来のものと比較して厚肉に構成する必要がないため、ボディを製造する際の材料費を節減できる。
That is, according to the present invention, utilizing the fact that the body is relatively thick at the position in the front-rear direction corresponding to the bearing hole, and providing the return passage at such a position, the strength of the body is not greatly impaired. By providing a return path, it is possible to reduce the number of parts and the installation space when such a gear pump or motor is disposed. In addition, compared to the case in which the part around the eyeglass hole of the body is made thick and the return passage is provided in the part, the body itself does not need to be made thicker than the conventional one. Can save material costs.

本発明の第１の実施形態における歯車ポンプを示す側面断面図。The side sectional view showing the gear pump in the 1st embodiment of the present invention. 同実施形態における歯車ポンプを示す左側面図。The left view which shows the gear pump in the embodiment. 同実施形態における歯車ポンプを示す右側面図。The right view which shows the gear pump in the embodiment. 図１におけるＸ−Ｘ断面図。XX sectional drawing in FIG. 本発明の第２の実施形態における歯車ポンプを示す側面断面図。Side surface sectional drawing which shows the gear pump in the 2nd Embodiment of this invention. 図５におけるＹ−Ｙ断面図。YY sectional drawing in FIG. 従来の歯車ポンプを示す側面断面図。Side surface sectional drawing which shows the conventional gear pump. 図７におけるＺ−Ｚ断面図。ZZ sectional drawing in FIG.

符号の説明Explanation of symbols

１、Ａ１…歯車ポンプ
２、Ａ２…ケーシング
３、Ａ３…フロントカバー
４、Ａ４…ボディ
４ａ、４ｂ…第１、第２のめがね穴
Ａ４ａ…めがね穴
４ｘ、４ｙ、Ａ４ｘ、Ａ４ｙ…軸受穴
４１、４２…第１、第２の高圧側流路口
Ａ４１…高圧側流路口
４３、Ａ４３…低圧側流路口
４４、Ａ４４…バルブ取付部
４５、Ａ４５…戻り通路
５…リアカバー
６、７…第１、第２の歯車対
Ａ６…歯車対
DESCRIPTION OF SYMBOLS 1, A1 ... Gear pump 2, A2 ... Casing 3, A3 ... Front cover 4, A4 ... Body 4a, 4b ... 1st, 2nd eyeglass hole A4a ... Eyeglass hole 4x, 4y, A4x, A4y ... Bearing hole 41, 42... First and second high pressure side flow path ports A 41. High pressure side flow path ports 43 and A 43. Low pressure side flow path ports 44 and A 44. Valve mounting portion 45 and A 45. 2 gear pairs A6 ... Gear pairs

まず、本発明の第１の実施形態を図１及び図２を参照しつつ以下に説明する。   First, a first embodiment of the present invention will be described below with reference to FIGS.

本発明が提供する歯車ポンプ１は、第１及び第２の歯車対６、７を有する二連歯車ポンプである。この歯車ポンプ１は、縦断面図を図１、左側面図を図２、右側面図を図３、図１におけるＸ−Ｘ断面図を図４にそれぞれ示すように、第１の歯車対６は第１の駆動歯車６１と第１の従動歯車６２とを噛み合わせて構成している。一方、第２の歯車対７は第２の駆動歯車７１と第２の従動歯車７２とを噛み合わせて構成している。そして、これら第１及び第２の歯車対６、７を、フロントカバー３、ボディ４、及びリアカバー５からなるケーシング２内に収納している。   The gear pump 1 provided by the present invention is a dual gear pump having first and second gear pairs 6 and 7. The gear pump 1 has a first gear pair 6 as shown in FIG. 1 as a longitudinal sectional view, FIG. 2 as a left side view, FIG. 3 as a right side view, and FIG. Is constituted by meshing a first drive gear 61 and a first driven gear 62. On the other hand, the second gear pair 7 is configured by meshing a second drive gear 71 and a second driven gear 72. The first and second gear pairs 6 and 7 are accommodated in a casing 2 including a front cover 3, a body 4, and a rear cover 5.

より具体的には、前記ボディ４の前後両端部に第１及び第２のめがね穴４ａ、４ｂを設けているとともに、このボディ４の中間部に両歯車対６、７を区分けする中間隔壁４Ｗが形成されている。前記第１のめがね穴４ａとフロントカバー３とで形成される室内には第１の歯車対６を収納していて、前記第２のめがね穴４ｂとリアカバー５とで形成される室内には第２の歯車対７を収納している。また、前記中間隔壁４Ｗには、前記第１及び第２のめがね穴４ａ、４ｂにそれぞれ連通するとともに、第１の駆動歯車６１を枢支する入出力軸６１１及び第２の駆動歯車７１を枢支する軸７１１を挿通させてなる軸受穴４ｘを設けている。また、前記中間隔壁４Ｗには、前記第１及び第２のめがね穴４ａ、４ｂにそれぞれ連通するとともに、第１の従動歯車６２を枢支する軸６２１及び第２の従動歯車７２を枢支する軸７２１をそれぞれ挿通させてなる軸受穴４ｙも設けている。   More specifically, first and second eyeglass holes 4a and 4b are provided at both front and rear end portions of the body 4, and an intermediate partition wall 4W for dividing the pair of gears 6 and 7 at the intermediate portion of the body 4. Is formed. A first gear pair 6 is housed in a chamber formed by the first eyeglass hole 4a and the front cover 3, and a chamber formed by the second eyeglass hole 4b and the rear cover 5 has a first gear. 2 gear pairs 7 are accommodated. The intermediate partition wall 4W communicates with the first and second eyeglass holes 4a and 4b, and pivots an input / output shaft 611 and a second drive gear 71 that pivotally support the first drive gear 61. A bearing hole 4x through which the supporting shaft 711 is inserted is provided. The intermediate partition wall 4W communicates with the first and second glasses holes 4a and 4b, respectively, and pivotally supports a shaft 621 and a second driven gear 72 that pivotally support the first driven gear 62. A bearing hole 4y through which the shaft 721 is inserted is also provided.

また、フロントカバー３、及びリアカバー５は、この種の二連歯車ポンプに用いられるものとして周知のものと同様の構成を有する。すなわち、フロントカバー３には、前記入出力軸６１１を挿通させてなる軸受穴３ｘ、及び第１の従動歯車６２を枢支する軸６２１を挿通させてなる軸受穴３ｙを設けている。一方、リアカバー５には、第２の駆動歯車７１を枢支する軸７１１を挿通させてなる軸受穴５ｘ、及び第２の従動歯車７２を枢支する軸７２１を挿通させてなる軸受穴５ｙを設けている。そして、フロントカバー３、ボディ４、及びリアカバー５は、固定用ボルト８により一体的に固定している。なお、前記フロントカバー３と前記入出力軸６１１との間には、オイルシール９１を設けている。   Further, the front cover 3 and the rear cover 5 have the same configuration as that known as that used in this type of dual gear pump. That is, the front cover 3 is provided with a bearing hole 3x through which the input / output shaft 611 is inserted and a bearing hole 3y through which the shaft 621 for pivotally supporting the first driven gear 62 is inserted. On the other hand, the rear cover 5 has a bearing hole 5x through which a shaft 711 for pivotally supporting the second drive gear 71 and a bearing hole 5y through which a shaft 721 for pivotally supporting the second driven gear 72 are inserted. Provided. The front cover 3, the body 4, and the rear cover 5 are integrally fixed by fixing bolts 8. An oil seal 91 is provided between the front cover 3 and the input / output shaft 611.

第１の駆動歯車６１は、入出力軸６１１と一体的に形成されている。この入出力軸６１１は、前記フロントカバー３の軸受穴３ｘ内、及び前記ボディ４の軸受穴４ｘ内に配したブッシュ９２によってケーシング２に対して支持されている。第１の従動歯車６２も、軸６２１と一体的に形成されている。この軸６２１は、前記フロントカバー３の軸受穴３ｙ内、及び前記ボディ３の軸受穴４ｙ内に配したブッシュ９２によってケーシング２に対して支持されている。また、第２の駆動歯車７１は、軸７１１と一体的に形成されている。この軸７１１は、第１の駆動歯車６１と同一軸心上にて前記ボディ４の軸受穴４ｘ内、および前記リアカバー５の軸受穴５ｘ内に配したブッシュ９２によってケーシング２に対して支持されている。ここで、この第２の駆動歯車７１を支持する軸７１１は前記入出力軸６１１の軸端に固定していて、従って、第２の駆動歯車７１は第１の駆動歯車６１と同期回転駆動される。さらに、第２の従動歯車７２も、軸７２１と一体的に形成されている。この軸７２１は、第１の従動歯車６２と同一軸心上にて前記ボディ４の軸受穴４ｙ内、および前記リアカバー５の軸受穴５ｙ内に配したブッシュ９２によってケーシング２に対して支持されている。しかし、この第２の従動歯車７２を支持する軸７２１は、第１の従動歯車６２を支持する軸６２１と完全に別体をなし、これら第１の従動歯車６２及び第２の従動歯車７２は、それぞれ第１の駆動歯車６１及び第２の駆動歯車７１により別々に駆動される。   The first drive gear 61 is formed integrally with the input / output shaft 611. The input / output shaft 611 is supported to the casing 2 by a bush 92 disposed in the bearing hole 3x of the front cover 3 and in the bearing hole 4x of the body 4. The first driven gear 62 is also formed integrally with the shaft 621. The shaft 621 is supported to the casing 2 by a bush 92 disposed in the bearing hole 3 y of the front cover 3 and in the bearing hole 4 y of the body 3. Further, the second drive gear 71 is formed integrally with the shaft 711. The shaft 711 is supported on the casing 2 by a bush 92 disposed in the bearing hole 4x of the body 4 and in the bearing hole 5x of the rear cover 5 on the same axis as the first drive gear 61. Yes. Here, the shaft 711 that supports the second drive gear 71 is fixed to the shaft end of the input / output shaft 611, and therefore the second drive gear 71 is driven to rotate synchronously with the first drive gear 61. The Further, the second driven gear 72 is also formed integrally with the shaft 721. The shaft 721 is supported on the casing 2 by a bush 92 disposed in the bearing hole 4 y of the body 4 and in the bearing hole 5 y of the rear cover 5 on the same axis as the first driven gear 62. Yes. However, the shaft 721 that supports the second driven gear 72 is completely separate from the shaft 621 that supports the first driven gear 62, and the first driven gear 62 and the second driven gear 72 are separated from each other. These are driven separately by the first drive gear 61 and the second drive gear 71, respectively.

また、ボディ４には、前記図２及び図３に示すように、一側面に第１及び第２の高圧側流路口４１、４２、他側面には低圧側流路口４３を設けている。第１及び第２の歯車対６、７がポンプとして作動するときは、低圧側流路口４３が流入口となり、第１及び第２の高圧側流路口４１、４２が吐出口となる。第１及び第２の高圧側流路口４１、４２は、それぞれ第１の歯車対６を収納する第１のめがね穴４ａ、及び第２の歯車対７を収納する第２のめがね穴４ｂに連通させている。一方、低圧側流路口４３は、前記第１及び第２のめがね穴４ａ、４ｂに連通し前後方向に延伸する接続部４３１と、この接続部４３１の中間から前記他側面に向けて穿設した開口部４３２とからなる。   Further, as shown in FIGS. 2 and 3, the body 4 is provided with first and second high-pressure side channel ports 41 and 42 on one side surface and a low-pressure side channel port 43 on the other side surface. When the first and second gear pairs 6 and 7 operate as a pump, the low-pressure side passage port 43 serves as an inflow port, and the first and second high-pressure side passage ports 41 and 42 serve as discharge ports. The first and second high-pressure side flow path ports 41 and 42 communicate with the first eye hole 4a for accommodating the first gear pair 6 and the second eye hole 4b for accommodating the second gear pair 7, respectively. I am letting. On the other hand, the low-pressure side channel port 43 is drilled from the middle of the connecting portion 431 toward the other side surface, and a connecting portion 431 communicating with the first and second eyeglass holes 4a and 4b and extending in the front-rear direction. An opening 432.

さらに本実施形態では、ボディ４の前記高圧側流路口４１、４２を設けた一側面に、さらにリリーフ弁に代表されるバルブ（図示略）を取り付け可能なバルブ取付部４４を設けている。そして、このバルブ取付部４４と前記低圧側流路口４３とを連通させるべく、前記軸受穴４ｘ、４ｙと前後位置を一致させて戻り通路４５を設けている。すなわち前記中間隔壁４Ｗに戻り通路４５を設けている。より具体的には、前記開口部４３２から、軸受穴４ｘの軸心からの距離を略一定に保ちつつ前記バルブ取付部４４に達する形状の穴を穿設し、この穴を戻り通路４５としている。   Furthermore, in the present embodiment, a valve attachment portion 44 to which a valve (not shown) represented by a relief valve can be attached on one side surface of the body 4 where the high-pressure side flow path ports 41 and 42 are provided. A return passage 45 is provided in such a manner that the front and rear positions of the bearing holes 4x and 4y coincide with each other so that the valve mounting portion 44 and the low-pressure side passage port 43 communicate with each other. That is, a return passage 45 is provided in the intermediate partition wall 4W. More specifically, a hole having a shape reaching the valve mounting portion 44 is formed from the opening 432 while maintaining a substantially constant distance from the shaft center of the bearing hole 4x, and this hole is used as the return passage 45. .

この歯車ポンプ１の作動時には、従来の二連歯車ポンプと同様に、低圧側流路口４３から作動液を第１の駆動歯車６１と第１の従動歯車６２の歯溝、及び第２の駆動歯車７１と第２の従動歯車７２の歯溝にそれぞれ供給し、第１の駆動歯車６１と第１の従動歯車６２の歯溝に供給した作動液を第１の高圧側流路口４１から、また、第２の駆動歯車７１と第２の従動歯車７２の歯溝に供給した作動液を第２の高圧側流路口４２からそれぞれ吐出する。その際、軸受穴４ｘに支持させている入出力軸６１１及び軸７１１は、液圧により図４における右下方に向かう作用を受ける。   When this gear pump 1 is operated, like the conventional double gear pump, the working fluid is supplied from the low pressure side passage port 43 to the tooth grooves of the first drive gear 61 and the first driven gear 62, and the second drive gear. 71 and the second driven gear 72 are supplied to the tooth grooves of the first drive gear 61 and the first driven gear 62, respectively. The hydraulic fluid supplied to the tooth grooves of the second drive gear 71 and the second driven gear 72 is discharged from the second high-pressure side passage opening 42, respectively. At that time, the input / output shaft 611 and the shaft 711 supported by the bearing hole 4x are subjected to an action toward the lower right in FIG.

そして、前記バルブ取付部４４に取り付けたバルブ（図示略）を作動させた際には、作動液が前記戻り通路４５を経て前記低圧側流路口４３の前記開口部４３２に戻される。   When a valve (not shown) attached to the valve attachment portion 44 is operated, the working fluid is returned to the opening portion 432 of the low-pressure side passage port 43 through the return passage 45.

本実施形態にかかる歯車ポンプ１の構成によれば、前記ボディ４の前記めがね穴４ａを設けた部位よりも厚肉な中間隔壁４Ｗに、前記バルブ取付部４４から低圧側ポート４３までを連通する戻り通路４５を前記軸受穴に前後方向位置を一致させて設けているので、戻り通路４５を設けてもボディ４の強度は大きく損なわれない。また、本実施形態では、前記戻り通路を図４における軸受穴４ｘの上方、すなわち軸受穴４ｘに対して該軸受穴４ｘに支持させている入出力軸６１１及び軸７１１が液圧により受ける作用と略反対側に設けているので、この点からも戻り通路４５を設けることによるボディ４の強度の損失は小さい。すなわち、ボディ４の強度を大きく損ねることなく戻り通路４５を設け、このような歯車ポンプ１及びバルブを配設する際の部品点数及び取り付けスペースの節減を図ることができる。さらに、ボディ４のめがね穴４ａ周囲の部位を厚肉にして該部位にリリーフ通路を設ける態様と比較して、ボディ４自体を従来のものと比較して厚肉に構成する必要がないため、ボディ４を製造する際の材料費も節減できる。   According to the configuration of the gear pump 1 according to the present embodiment, the valve partition 44 and the low-pressure side port 43 are communicated with the intermediate partition wall 4W that is thicker than the portion of the body 4 where the eyeglass holes 4a are provided. Since the return passage 45 is provided so that the position in the front-rear direction coincides with the bearing hole, the strength of the body 4 is not greatly impaired even if the return passage 45 is provided. Further, in this embodiment, the input / output shaft 611 and the shaft 711 supported by the bearing hole 4x above the bearing hole 4x in FIG. Since it is provided on the substantially opposite side, the loss of strength of the body 4 due to the provision of the return passage 45 is small from this point. That is, the return passage 45 can be provided without greatly impairing the strength of the body 4, and the number of parts and the installation space can be reduced when the gear pump 1 and the valve are disposed. Furthermore, since it is not necessary to make the body 4 itself thicker than the conventional one, as compared with the embodiment in which the portion around the eyeglass hole 4a of the body 4 is thickened and the relief passage is provided in the portion, The material cost when manufacturing the body 4 can also be reduced.

次いで、本発明の第２の実施形態を図５及び図６を参照しつつ以下に説明する。   Next, a second embodiment of the present invention will be described below with reference to FIGS.

この実施形態にかかる歯車ポンプＡ１は、縦断面図を図５、図５におけるＹ−Ｙ断面図を図６にそれぞれ示すように、１つの歯車対Ａ６と、この歯車対Ａ６を収納しフロントカバーＡ３及びボディＡ４からなるケーシングＡ２とを具備する。前記歯車対Ａ６は第１の駆動歯車Ａ６１と第１の従動歯車Ａ６２とを噛み合わせて構成している。   The gear pump A1 according to this embodiment accommodates one gear pair A6 and the gear pair A6 as shown in a longitudinal sectional view in FIG. 5 and a YY sectional view in FIG. A casing A2 including A3 and a body A4. The gear pair A6 is configured by meshing a first drive gear A61 and a first driven gear A62.

より具体的には、前記ボディＡ４の前端部にめがね穴Ａ４ａを設けていて、このめがね穴Ａ４ａとフロントカバーＡ３とで形成される空間に歯車対Ａ６を収納している。また、ボディＡ４には、前記めがね穴Ａ４ａに連通するとともに、駆動歯車Ａ６１を枢支する入出力軸Ａ６１１、及び従動歯車Ａ６２を枢支する軸Ａ６２１をそれぞれ挿通させてなる軸受穴Ａ４ｘ、Ａ４ｙを設けている。   More specifically, a spectacle hole A4a is provided in the front end portion of the body A4, and the gear pair A6 is housed in a space formed by the spectacle hole A4a and the front cover A3. In addition, the body A4 has bearing holes A4x and A4y that communicate with the eyeglass hole A4a, and are inserted through an input / output shaft A611 that pivotally supports the drive gear A61 and a shaft A621 that pivotally supports the driven gear A62, respectively. Provided.

また、フロントカバーＡ３は、この種の歯車ポンプに用いられるものとして周知のものと同様の構成を有する。すなわち、フロントカバー３には、前記入出力軸Ａ６１１を挿通させてなる軸受穴Ａ３ｘ、及び従動歯車Ａ６２を枢支する軸Ａ６２１を挿通させてなる軸受穴Ａ３ｙを設けている。そして、フロントカバーＡ３及びボディＡ４は、固定用ボルトＡ８により一体的に固定している。なお、前記フロントカバーＡ３と前記入出力軸Ａ６１１との間には、オイルシールＡ９１を設けている。また、図６において、前記めがね穴Ａ４ａは想像線により示している。   Further, the front cover A3 has the same configuration as that well known as that used in this type of gear pump. That is, the front cover 3 is provided with a bearing hole A3x through which the input / output shaft A611 is inserted and a bearing hole A3y through which the shaft A621 that pivotally supports the driven gear A62 is inserted. The front cover A3 and the body A4 are integrally fixed by a fixing bolt A8. An oil seal A91 is provided between the front cover A3 and the input / output shaft A611. In FIG. 6, the eyeglass hole A4a is indicated by an imaginary line.

駆動歯車Ａ６１は入出力軸Ａ６１１と一体的に形成されている。この入出力軸Ａ６１１は、ケーシングＡ２に対して、前記フロントカバーＡ３の軸受穴Ａ３ｘ内、及び前記ボディの軸受穴Ａ４ｘ内に配したブッシュＡ９２によって支持されている。一方、従動歯車Ａ６２も軸Ａ６２１と一体的に形成されている。この軸Ａ６２１は、ケーシングＡ２に対し、フロントカバーＡ３の軸受穴Ａ３ｙ内、及び前記ボディＡ４の軸受穴Ａ４ｙ内に配したブッシュＡ９２によって支持されている。   The drive gear A61 is formed integrally with the input / output shaft A611. The input / output shaft A611 is supported by the bush A92 disposed in the bearing hole A3x of the front cover A3 and in the bearing hole A4x of the body with respect to the casing A2. On the other hand, the driven gear A62 is also formed integrally with the shaft A621. The shaft A621 is supported with respect to the casing A2 by a bush A92 disposed in the bearing hole A3y of the front cover A3 and in the bearing hole A4y of the body A4.

また、ボディＡ４には、一側面に高圧側流路口Ａ４１、他側面には低圧側流路口Ａ４３を設けている。歯車対Ａ６がポンプとして作動するときは、低圧側流路口Ａ４３が流入口となり、高圧側流路口Ａ４１が吐出口となる。高圧側流路口Ａ４１は、前記歯車機構Ａ６を収納するめがね穴Ａ４ａに連通させている。一方、低圧側流路口Ａ４３は、前記めがね穴Ａ４ａに連通し後方に延伸する接続部Ａ４３１と、この接続部Ａ４３１の後端部から前記他側面に向けて穿設した開口部Ａ４３２とからなる。なお、図６において、前記高圧側流路口Ａ４１は想像線により示している。   The body A4 is provided with a high-pressure side passage port A41 on one side surface and a low-pressure side passage port A43 on the other side surface. When the gear pair A6 operates as a pump, the low-pressure side passage port A43 serves as an inflow port, and the high-pressure side passage port A41 serves as a discharge port. The high-pressure side passage port A41 communicates with an eyeglass hole A4a that houses the gear mechanism A6. On the other hand, the low-pressure side channel port A43 includes a connection portion A431 that communicates with the glasses hole A4a and extends rearward, and an opening portion A432 that is drilled from the rear end portion of the connection portion A431 toward the other side surface. In FIG. 6, the high-pressure channel A41 is indicated by imaginary lines.

さらに本実施形態では、ボディＡ４の前記高圧側流路口Ａ４１を設けた一側面に、さらにリリーフ弁に代表されるバルブ（図示略）を取り付け可能なバルブ取付部Ａ４４を設けている。そして、このバルブ取付部Ａ４４と前記低圧側流路口Ａ４３とを連通させるべく、前記軸受穴Ａ４ｘと前後位置を一致させて戻り通路Ａ４５を設けている。より具体的には、前記開口部Ａ４３２から、第１の軸受穴Ａ４ｘの軸心からの距離を略一定に保ちつつ前記バルブ取付部Ａ４４に達する形状の穴を穿設し、この穴を戻り通路Ａ４５としている。   Further, in the present embodiment, a valve attachment portion A44 to which a valve (not shown) represented by a relief valve can be attached is provided on one side surface of the body A4 where the high-pressure side passage port A41 is provided. And in order to make this valve attachment part A44 and the said low voltage | pressure side flow path opening A43 communicate, the said passage hole A4x and the front-back position correspond, and the return channel | path A45 is provided. More specifically, a hole having a shape reaching the valve mounting portion A44 is formed from the opening A432 while maintaining a substantially constant distance from the axis of the first bearing hole A4x, and the hole is returned to the return passage. A45.

この歯車ポンプＡ１の作動時には、従来の歯車ポンプと同様に、低圧側流路口Ａ４３から作動液を駆動歯車Ａ６１と従動歯車Ａ６２の歯溝に供給し、この空間に供給した作動液を高圧側流路口Ａ４１から吐出する。その際、軸受穴Ａ４ｘに支持させている入出力軸Ａ６１１は、液圧により図６における右下方に向かう作用を受ける。   When this gear pump A1 is operated, like the conventional gear pump, the hydraulic fluid is supplied from the low pressure side passage port A43 to the tooth grooves of the drive gear A61 and the driven gear A62, and the hydraulic fluid supplied to this space is supplied to the high pressure side flow. Discharge from the road entrance A41. At that time, the input / output shaft A611 supported by the bearing hole A4x is subjected to an action toward the lower right in FIG.

そして、前記バルブ取付部Ａ４４に取り付けたバルブ（図示略）を作動させた際には、作動液が前記戻り通路Ａ４５を経て前記低圧側流路口Ａ４３の前記開口部Ａ４３２に戻される。   When a valve (not shown) attached to the valve attachment portion A44 is operated, the working fluid is returned to the opening portion A432 of the low pressure side passage port A43 through the return passage A45.

本実施形態にかかる歯車ポンプＡ１の構成では、上述したように、前記ボディＡ４の前記軸受穴Ａ４ｘに前後方向位置を一致させて前記バルブ取付部Ａ４４から低圧側ポートＡ４３までを連通する戻り通路Ａ４５を設けているが、この部位はめがね穴４ａを設けた部位よりも厚肉である。従って、戻り通路Ａ４５の存在によりボディＡ４の強度を大きく損なわれない。また、本実施形態では、前記通路Ａ４５を図６における軸受穴Ａ４ｘの上方、すなわち軸受穴Ａ４ｘに対して該軸受穴Ａ４ｘに支持させている入出力軸Ａ６１１が液圧により受ける作用と略反対側に設けているので、この点からも戻り通路Ａ４５を設けることによるボディＡ４の強度の損失は小さい。すなわち、ボディＡ４の強度を大きく損ねることなく戻り通路Ａ４５を設け、このような歯車ポンプＡ１及びバルブを配設する際の部品点数及び取り付けスペースの節減を図ることができる。さらに、ボディＡ４のめがね穴Ａ４ａ周囲の部位を厚肉にして該部位に戻り通路を設ける態様と比較して、ボディＡ４自体を従来のものと比較して厚肉に構成する必要がないため、ボディＡ４を製造する際の材料費も節減できる。   In the configuration of the gear pump A1 according to this embodiment, as described above, the return passage A45 that communicates from the valve mounting portion A44 to the low-pressure side port A43 with the position in the front-rear direction aligned with the bearing hole A4x of the body A4. However, this part is thicker than the part provided with the glasses hole 4a. Accordingly, the presence of the return passage A45 does not significantly impair the strength of the body A4. Further, in the present embodiment, the passage A45 is located above the bearing hole A4x in FIG. 6, that is, on the substantially opposite side to the action that the input / output shaft A611 supported by the bearing hole A4x with respect to the bearing hole A4x receives by hydraulic pressure. Therefore, the loss of strength of the body A4 due to the provision of the return passage A45 is small from this point. That is, the return passage A45 can be provided without significantly reducing the strength of the body A4, and the number of parts and the installation space can be reduced when the gear pump A1 and the valve are disposed. Furthermore, since it is not necessary to configure the body A4 itself to be thicker than the conventional one, as compared with the aspect in which the part around the spectacle hole A4a of the body A4 is thickened and the return passage is provided in the part, The material cost for manufacturing the body A4 can also be reduced.

なお、本発明は以上に述べた第１、第２の実施形態に限られない。   The present invention is not limited to the first and second embodiments described above.

例えば、３対以上の歯車対を有する歯車ポンプに本発明を適用してもよい。   For example, the present invention may be applied to a gear pump having three or more pairs of gears.

また、２対の歯車対を有する歯車ポンプを、上述した第１の実施形態のような歯車ポンプでなく高圧側流路口及び低圧側流路口を１つずつ有し２対の歯車対の噛み合わせタイミングをずらした位相差歯車ポンプとして構成してももちろんよい。   In addition, the gear pump having two pairs of gears is not the gear pump as in the first embodiment described above, but has one high-pressure side passage port and one low-pressure side passage port. Of course, it may be configured as a phase difference gear pump with shifted timing.

さらに、上述した第２の実施形態のようにケーシングをフロントカバーとボディとにより構成する代わりに、ボディとリアカバーとによりケーシングを構成し、このケーシングのボディの軸受穴を設けた部位、すなわちめがね穴より前方の部位にリリーフ通路を設けるようにしてもよい。   Further, instead of configuring the casing with the front cover and the body as in the second embodiment described above, the body and the rear cover configure the casing, and the portion of the casing provided with the bearing hole, that is, the eyeglass hole. A relief passage may be provided at a more forward site.

加えて、バルブ取付部に取り付けるバルブは、リリーフ弁に限らず、流量制御弁等、他の種類のバルブであってももちろんよい。   In addition, the valve attached to the valve attachment portion is not limited to the relief valve, and may be other types of valves such as a flow control valve.

その他、本発明の趣旨を損ねない範囲で種々に変更してもよい。
In addition, you may change variously in the range which does not impair the meaning of this invention.

本発明を活用すれば、ボディの軸受穴に対応する前後方向位置ではめがね穴に対応する前後方向位置と比較してボディが比較的厚肉であることを利用し、このような位置に戻り通路を設けることにより、ボディの強度を大きく損ねることなく戻り通路を設け、このような歯車ポンプを配設する際の部品点数及び取り付けスペースの節減を図ることができる。さらに、ボディのめがね穴周囲の部位を厚肉にして該部位に戻り通路を設ける態様と比較して、ボディ自体を従来のものと比較して厚肉に構成する必要がないため、ボディを製造する際の材料費を節減できる。   By utilizing the present invention, it is possible to utilize the fact that the body is relatively thick at the front-rear position corresponding to the bearing hole of the body as compared to the front-rear position corresponding to the spectacle hole, and return to such a position. By providing the return passage, it is possible to reduce the number of parts and the mounting space when such a gear pump is disposed without greatly reducing the strength of the body. In addition, compared to the case in which the part around the eyeglass hole of the body is made thick and the return passage is provided in the part, the body itself does not need to be made thicker than the conventional one. Can save material costs.

Claims (1)

駆動歯車と従動歯車とを噛合させてなる１又は複数の歯車対と、この歯車対を収納するケーシングとを具備し、前記ケーシングが、前記歯車対を収納するめがね穴、このめがね穴に連通し前記歯車対を構成する歯車を枢支する軸を挿通させてなる軸受穴、前記めがね穴に連通し低圧の作動液を吸入する低圧側ポート、前記めがね穴に連通し高圧の作動液を排出する高圧側ポート、及びこの高圧側ポート近傍に設けられバルブを取り付け可能なバルブ取付部を有するボディと、このボディの前方又は後方のうち少なくとも一方に設けられ前記めがね穴を閉塞するカバーとを具備するものであって、
前記ボディが、前記めがね穴を設けた部位より厚肉な部位で、前記軸受穴に対して該軸受穴に支持させている軸が液圧により受ける作用の向きと略反対側に前記バルブ取付部から低圧側ポートまでを連通する戻り通路をさらに有することを特徴とする歯車ポンプ。One or a plurality of gear pairs formed by meshing a drive gear and a driven gear, and a casing that houses the gear pairs, the casing is a glasses hole that houses the gear pairs, and communicates with the glasses holes A bearing hole through which a shaft that pivotally supports the gears constituting the gear pair is inserted, a low-pressure side port that communicates with the eyeglass hole and sucks low-pressure hydraulic fluid, and communicates with the eyeglass hole to discharge high-pressure hydraulic fluid. A body having a high-pressure side port and a valve mounting portion provided in the vicinity of the high-pressure side port to which a valve can be attached; and a cover provided on at least one of the front and rear sides of the body to close the eyeglass hole. And
The valve mounting portion on the side opposite to the direction of the action of the shaft supported by the bearing hole by the hydraulic pressure with respect to the bearing hole at a portion thicker than the portion where the eyeglass hole is provided. a gear pump, characterized in that it comprises in the al return passage communicating to a low pressure side port from.
JP2008533020A 2006-09-08 2006-09-08 Gear pump Active JP4952719B2 (en)

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