JP3919934B2 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
JP3919934B2
JP3919934B2 JP12970898A JP12970898A JP3919934B2 JP 3919934 B2 JP3919934 B2 JP 3919934B2 JP 12970898 A JP12970898 A JP 12970898A JP 12970898 A JP12970898 A JP 12970898A JP 3919934 B2 JP3919934 B2 JP 3919934B2
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Japan
Prior art keywords
tooth
gear
meshing
groove
discharge port
Prior art date
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Expired - Fee Related
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JP12970898A
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Japanese (ja)
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JPH11303766A (en
Inventor
鋭 黄
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Komatsu Ltd
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Komatsu Ltd
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Description

【0001】
【発明の属する技術分野】
本発明は、油圧機器の油圧源となる外歯歯車よりなる歯車ポンプに関する。
【0002】
【従来の技術】
特公昭43−23361号公報には図7に示すように、「噛合線上で二つの有効噛合点A1 とA2 の中間に位置する無効噛合点がピッチ点Pを通るときの噛合位相において、2個の有効噛合点A1 ,A2 によって区切られる原動歯車51と従動歯車52の各歯形曲線、および両有効噛合点A1 ,A2 を結ぶ線分Aの三者を含む図形Sに若干の余裕を外側に付した図形の部分を高圧側と低圧側との間の境界として残して、それぞれ高圧ポート53側に連なる溝(凹所)54、および低圧ポート55側に連なる溝(凹所)56をポンプ歯車側板57に設けて成る歯車ポンプ」の記載がある。
【0003】
【発明が解決しようとする課題】
前記従来の技術は、図7に示すような無効噛合点A3 がピッチ点Pを通る回転状態を基準にして、溝(凹所)54,56の形状を設定しているため、他の回転状態、例えば図7より少し前の回転状態である図8に示す状態から更に回転するとき、バックラッシが小さいため図形S(斜線部)のうちvの部分の容積はとじ込み状態で膨張を開始する。このとき、vの部分は吐出側の逃げ溝54に連通しているため、高圧ポート53から作動油を吸入して容積効率が低下する問題がある。
【0004】
本発明は上記従来技術の問題を解決するためになされたもので、容積効率の高い歯車ポンプを提供することを目的とする。
【0005】
【課題を解決するための手段】
上記の目的を達成するために、本願に係る歯車ポンプの第1の発明は、互いに噛合う外歯歯車よりなる原動歯車および従動歯車と、両歯車のとじ込み容積部を吸入口または吐出口に連通する溝を形成した側板とを有する歯車ポンプにおいて、原動歯車の一つの歯が両歯車の回転中心を結ぶ中心線上に位置するとき、この中心線上の歯に隣接する従動歯車の吐出口側の歯元外形線を、吐出口に連通する溝の境界とし、有効噛合点の中間の噛合点である無効噛合点がピッチ点を通るときの吐出側の噛合中の原動歯車の歯元外形線を原動歯車の吐出側の境界とし、また、前記無効噛合点が前記ピッチ点を通るときの吸入側の噛合中の従動歯車の歯元外形線を従動歯車の吸入側の境界とし、従動歯車の一つの歯が両歯車の回転中心を結ぶ中心線上に位置するとき、この中心線上の歯に隣接する原動歯車の吸入口側の歯元外形線を、吸入口に連通する溝の境界とすることを特徴とする。
【0006】
第1の発明によれば、原動歯車の一つの歯が両歯車の回転中心を結ぶ中心線上に位置する噛合位置から更に回転すると中心線上の原動歯車の歯先と従動歯車の歯底とに囲まれる容積(以後、とじ込み容積という)が増加する。しかし、とじ込み容積は吐出口に連通する溝から遮断されるため、とじ込み容積が吐出口から吐出油を吸入することはない。このため、従来技術で問題になっていた容積効率の低下を防止できる。なお、前記噛合位置まではとじ込み容積は減少するが、このとじ込み容積は溝を介して吐出口に連通されているためとじ込み容積内の高圧油が更に圧縮されることはない。このため、振動、騒音の発生が確実に防止される。
【0007】
両歯車が更に回転して、従動歯車の一つの歯が両歯車の回転中心を結ぶ中心線上に位置する噛合状態から両歯車が更に回転するととじ込み容積が膨張する。しかし、とじ込み容積は吸入口に連通するため吸入口から油が補充されて負圧になることはない。しかも、吸入口から油が補充されるため容積効率が低下することもない。
【0008】
本願に係る歯車ポンプの第2の発明は、互いに噛合う外歯歯車よりなる原動歯車および従動歯車と、両歯車のとじ込み容積部を吸入口または吐出口に連通する溝を形成した側板とを有する歯車ポンプにおいて、原動歯車の一つの歯が両歯車の回転中心を結ぶ中心線上に位置するとき、この中心線上の歯に隣接する従動歯車の吐出口側の歯元外形線に接し、かつ、噛合線上で前記中心線との交点から半ピッチの長さの点で交差する接線を、吐出口に連通する溝の境界とすることを特徴とする。
【0009】
第2の発明によれば、吐出口に連通する溝の境界を、原動歯車の中心線上の歯に隣接する従動歯車の吐出口側の歯元外形線に接し、かつ、噛合線上で前記中心線との交点から半ピッチの長さの点で交差する接線としたため、第1の発明と略同じ形状となる。このため、第1の発明と同様な作用効果が得られる。しかし、吐出口に連通する溝の境界を、第1の発明のように従動歯車の歯元外形線とするのではなく従動歯車の歯元外形線の接線としているため、吐出口に連通する溝ととじ込み容積との連通、遮断域に僅かな不感帯が生じる。このため、吐出口に連通する溝ととじ込み容積とが遮断される時に、とじ込み容積内を充填する吐出口の高圧油が僅かに圧縮されるが、吐出口に連通する溝の境界は直線であるため加工コストが低減される。
【0012】
【発明の実施の形態】
本発明の第1実施例を図1〜図3を参照して詳述する。
図1に示すように、歯車ポンプは、インボリュート曲線により形成され、互いに噛合う外歯歯車よりなる原動歯車1および従動歯車2の両側端部にシール用の側板3(3a,3b)が設置されている。この側板3には、両噛合点A1 ,A2 により閉じられる図形Sの部分(斜線で示す)を吐出口4に連通する溝5、または、図形Sの部分を吸入口6に連通する溝7が形成されている。これら溝5および溝7の境界は次のように設定される。なお、溝5の深さも図1(B)に示す溝7の深さhと略同じに形成される。また、歯車の歯底はトロコイド曲線により成形されている。
【0013】
(1)原動歯車1の一つの歯1aが両歯車1,2の回転中心G1,G2 を結ぶ中心線上に位置するとき、この中心線上の歯1aに隣接する従動歯車2の吐出口側の歯元外形線2bを、従動歯車2の吐出口4に連通する溝5の境界とする。
(2)図2に示すように、無効噛合点(有効噛合点A1 ,A2 の中間の噛合点)がピッチ点Pを通るときの吐出側の噛合中の原動歯車1dの歯元外形線1eを原動歯車1の吐出側の境界とする。また、無効噛合点がピッチ点Pを通るときの吸入側の噛合中の従動歯車2dの歯元外形線2eを従動歯車2の吸入側の境界とする。更に、これら境界に連続して、原動歯車1と従動歯車2の各歯底の一部により境界を形成する。
(3)図3に示すように、従動歯車2の一つの歯2cが両歯車1,2の回転中心G1,G2 を結ぶ中心線上に位置するとき、この中心線上の歯2cに隣接する原動歯車1bの吸入口6側の歯元外形線1cを、原動歯車1bの吸入口6に連通する溝7の境界とする。
(4)更に、以上の(1)〜(3)の各境界に連続する歯底円1f,1gおよび2f,2gにより吐出口4に連通する溝5および吸入口6に連通する溝7を形成している。
【0014】
第1実施例の構成による作用効果について説明する。
図1において、原動歯車1の一つの歯1aが噛合点B1 で従動歯車2と噛み合い、かつ、両歯車1,2の回転中心G1,G2 を結ぶ中心線上に位置する噛合位置から更に回転すると中心線上の原動歯車1aの歯先と従動歯車2の歯底とに囲まれる容積(以後、とじ込み容積vという)が増加する。しかし、とじ込み容積vは吐出口4に連通する溝5から遮断されるため、とじ込み容積vが吐出口4から吐出油を吸入することはない。このため、従来技術で問題になっていた容積効率の低下を防止できる。なお、前記噛合位置まではとじ込み容積vは減少するが、このとじ込み容積vは溝5を介して吐出口4に連通されているため、とじ込み容積v内の高圧油が更に圧縮されることはない。このため、振動、騒音の発生が確実に防止される。
【0015】
図2において、吐出口4に連通する溝5と吸入口6に連通する溝7とは図2の噛合位置を境として原動歯車1の吐出側の境界、あるいは従動歯車2の吸入側の境界のいずれかにより遮断される。従って、とじ込み容積u,vを経由して、吐出口4に連通する溝5と吸入口6に連通する溝7とが連通することがないため容積効率の低下が防止される。
【0016】
図3において、従動歯車2の一つの歯2cが両歯車1,2の回転中心G1,G2 を結ぶ中心線上に位置する噛合位置から、噛合点B3 で原動歯車1と噛み合って更に回転するととじ込み容積uが膨張する。しかし、とじ込み容積uは吸入口6に連通されるため吸入口6から油が補充されて負圧になることはない。しかも、吐出口4ではなく吸入口6から油が補充されるため容積効率が低下することもない。なお、前記噛合位置までは、とじ込み容積uが減少するため更に圧縮されようとするとじ込み容積uの高圧油は、一部分が間隙B4 を介して吸入口6に放出され、他は従来と同様にノッチまたは逃げ溝(図示省略)から溝5に放出して振動、騒音の発生を防止している。なお、前記溝5と溝7の各境界に連続する境界を歯底円1f,1gおよび2f,2gで形成して、溝5と溝7を大きくすると共に吐出側から吸入側への油漏れを防止している。
【0017】
本発明の第2実施例を図4〜図6を参照して詳述する。
第2実施例の構成は、第1実施例の構成に対して、中心線上の歯1aに隣接する従動歯車2aの吐出口4側の歯元外形線2bに接し、かつ、噛合線上で前記中心線との交点Pから法線ピッチの半分(tn/2)の長さの点Qで交差する接線Tと、点Qを通る原動歯車1aの半径線Nとにより、吐出口4に連通する溝5の境界としている他は第1実施例の構成と同様である。
【0018】
第2実施例の構成による作用効果について説明する。
吐出口4に連通する溝5の境界を、原動歯車1の中心線上の歯1aに隣接する従動歯車2aの吐出口4側の歯元外形線に接し、かつ、噛合線上で前記中心線との交点Pから半法線ピッチ(tn/2)の長さの点で交差する接線Tとしたため、第1実施例と略同じ形状となる。このため、第1実施例と同様な作用効果が得られる。しかし、吐出口4に連通する溝5の境界を、第1実施例のように従動歯車2aの歯元外形線2bとするのではなく、従動歯車2aの歯元外形線2bの接線Tとしているため、吐出口4に連通する溝5ととじ込み容積vとの連通、遮断域に僅かな不感帯が生じる。このため、吐出口4に連通する溝5ととじ込み容積vとが遮断される時に、とじ込み容積v内を充填する吐出口の高圧油が僅かに圧縮されるが、吐出口4に連通する溝5の境界は直線であるため加工コストが低減される。
【図面の簡単な説明】
【図1】本発明に係る歯車ポンプの第1実施例の基準噛合状態を示す図で、(A)正面図、(B)は側面図である。
【図2】図1の噛合状態より後の噛合状態を示す図である。
【図3】図2の噛合状態より後の噛合状態を示す図である。
【図4】本発明に係る歯車ポンプの第2実施例の基準噛合状態を示す図で、(A)正面図、(B)は側面図である。
【図5】図4の噛合状態より後の噛合状態を示す図である。
【図6】図5の噛合状態より後の噛合状態を示す図である。
【図7】 従来技術に係る歯車ポンプの基準噛合状態を示す図で、(A)正面図、(B)は側面図である。
【図8】 図7の噛合状態より前の噛合状態を示す図である。
【符号の説明】
1 原動歯車
1a 原動歯車の中心線上の歯
1b 従動歯車の中心線上の歯に隣接する原動歯車の歯
1c,1e 原動歯車の歯元外形線
1f,1g 原動歯車の歯底円
2 従動歯車
2a 原動歯車の中心線上の歯に隣接する従動歯車の歯
2b,2e 従動歯車の歯元外形線
2c 従動歯車の中心線上の歯
2f,2g 従動歯車の歯底円
3 側板
4 吐出口
5 吐出口に連通する溝
6 吸入口
7 吸入口に連通する溝
G1 原動歯車の回転中心
G2 従動歯車の回転中心
T,Ta 接線
Q 接点
R 円弧
B1,B3 噛合点
B2,B4 間隙
[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a gear pump including external gears that serve as a hydraulic source of hydraulic equipment.
[0002]
[Prior art]
In Japanese Patent Publication No. 43-23361, as shown in FIG. 7, “in the meshing phase when the invalid meshing point located between the two effective meshing points A1 and A2 on the meshing line passes through the pitch point P, two A slight margin is added to the outer side of the figure S including the tooth profile curves of the driving gear 51 and the driven gear 52 and the line segment A connecting the two effective meshing points A1 and A2 separated by the effective meshing points A1 and A2. The groove (recess) 54 connected to the high-pressure port 53 side and the groove (recess) 56 connected to the low-pressure port 55 side are respectively left as the boundary between the high-pressure side and the low-pressure side. 57 ”.
[0003]
[Problems to be solved by the invention]
In the prior art, since the shapes of the grooves (recesses) 54 and 56 are set based on the rotation state where the invalid mesh point A3 passes through the pitch point P as shown in FIG. For example, when further rotating from the state shown in FIG. 8, which is the rotating state slightly before FIG. 7, since the backlash is small, the volume of the portion v in the graphic S (shaded portion) starts to expand while being confined. At this time, since the portion v communicates with the escape groove 54 on the discharge side, there is a problem that the hydraulic efficiency is sucked from the high pressure port 53 and the volumetric efficiency is lowered.
[0004]
The present invention has been made to solve the above-described problems of the prior art, and an object thereof is to provide a gear pump with high volumetric efficiency.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, a first invention of a gear pump according to the present application is to communicate a driving gear and a driven gear made of external gears meshing with each other, and a binding volume portion of both gears to a suction port or a discharge port. When a tooth of the driving gear is located on a center line connecting the rotation centers of both gears, the tooth on the discharge port side of the driven gear adjacent to the tooth on the center line Using the original outline as the boundary of the groove communicating with the discharge port, the tooth outline of the driving gear meshing on the discharge side when the ineffective meshing point, which is the middle meshing point of the effective meshing point, passes through the pitch point. The boundary on the discharge side of the gear, and the tooth outline of the driven gear engaged on the suction side when the invalid mesh point passes the pitch point is defined as the boundary on the suction side of the driven gear. The teeth are positioned on the center line connecting the rotation centers of both gears. To time, the dedendum outline of the suction port side of the driving gear adjacent to the teeth of the center line, characterized in that the boundary of the groove which communicates with the intake port.
[0006]
According to the first aspect, when one tooth of the driving gear is further rotated from the engagement position located on the center line connecting the rotational centers of the gears, to the tooth bottom of the tooth tip and a driven gear on the center line of the driving gear The enclosed volume (hereinafter referred to as the binding volume) increases. However, since the binding volume is blocked from the groove communicating with the discharge port, the binding volume does not suck the discharge oil from the discharge port. For this reason, it is possible to prevent a decrease in volumetric efficiency that has been a problem in the prior art. The binding volume decreases up to the meshing position, but since this binding volume is communicated with the discharge port through the groove, the high-pressure oil in the binding volume is not further compressed. For this reason, generation | occurrence | production of a vibration and noise is prevented reliably.
[0007]
When both gears further rotate and both gears further rotate from the meshing state where one tooth of the driven gear is located on the center line connecting the rotation centers of both gears, the binding volume expands. However, since the binding volume communicates with the suction port, oil is replenished from the suction port and does not become negative pressure. Moreover, since the oil is replenished from the suction port, the volumetric efficiency is not lowered.
[0008]
A second invention of the gear pump according to the present application includes a driving gear and a driven gear made of external gears meshing with each other, and a side plate having a groove that communicates the binding volume portion of both gears with the suction port or the discharge port. In a gear pump, when one tooth of a driving gear is located on the center line connecting the rotation centers of both gears, the tooth is in contact with the tooth outline on the discharge port side of the driven gear adjacent to the tooth on the center line and meshed. A tangent line that intersects at a half-pitch length from an intersection with the center line on the line is defined as a boundary of a groove communicating with the discharge port.
[0009]
According to the second invention, the boundary of the groove communicating with the discharge port is in contact with the tooth outline on the discharge port side of the driven gear adjacent to the tooth on the center line of the driving gear, and the center line on the meshing line Since it is a tangent line that intersects at a point of a half pitch length from the intersection point, the shape is substantially the same as in the first invention. For this reason, the same effect as the first invention can be obtained. However, since the boundary of the groove communicating with the discharge port is not the tooth root outline of the driven gear as in the first invention, but the tangent line of the tooth outline of the driven gear, the groove communicating with the discharge port There is a slight dead zone in the cut-off area and communication with the binding volume. Therefore, when the groove communicating with the discharge port and the binding volume are interrupted, the high-pressure oil in the discharge port filling the binding volume is slightly compressed, but the boundary of the groove communicating with the discharge port is a straight line. Therefore, the processing cost is reduced.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
A first embodiment of the present invention will be described in detail with reference to FIGS.
As shown in FIG. 1, the gear pump is formed by an involute curve, and side plates 3 (3a, 3b) for sealing are installed at both end portions of a driving gear 1 and a driven gear 2 made of external gears meshing with each other. ing. The side plate 3 has a groove 5 that communicates the portion of the figure S (shown by hatching) closed by the meshing points A1 and A2 with the discharge port 4 or a groove 7 that communicates the portion of the figure S to the suction port 6. Is formed. The boundaries between the grooves 5 and 7 are set as follows. The depth of the groove 5 is also substantially the same as the depth h of the groove 7 shown in FIG. Further, the tooth bottom of the gear is formed by a trochoid curve.
[0013]
(1) When one tooth 1a of the driving gear 1 is located on the center line connecting the rotation centers G1, G2 of the two gears 1, 2, the tooth on the discharge port side of the driven gear 2 adjacent to the tooth 1a on the center line The original outline 2b is defined as a boundary of the groove 5 communicating with the discharge port 4 of the driven gear 2.
(2) As shown in FIG. 2, the tooth root outline 1e of the driving gear 1d during meshing on the discharge side when the invalid meshing point (meshing point between the effective meshing points A1 and A2) passes through the pitch point P A boundary on the discharge side of the driving gear 1 is used. Further, the tooth outline 2e of the driven gear 2d that is engaged on the suction side when the invalid meshing point passes the pitch point P is defined as a boundary on the suction side of the driven gear 2. Further, a boundary is formed by a part of each tooth bottom of the driving gear 1 and the driven gear 2 continuously from the boundary.
(3) As shown in FIG. 3, when one tooth 2c of the driven gear 2 is located on the center line connecting the rotation centers G1, G2 of the two gears 1, 2, the driving gear adjacent to the tooth 2c on the center line The tooth outline 1c on the suction port 6 side of 1b is defined as the boundary of the groove 7 communicating with the suction port 6 of the driving gear 1b.
(4) Furthermore, a groove 5 communicating with the discharge port 4 and a groove 7 communicating with the suction port 6 are formed by the root circles 1f, 1g and 2f, 2g continuous at the boundaries of the above (1) to (3). is doing.
[0014]
The operational effects of the configuration of the first embodiment will be described.
In FIG. 1, when one tooth 1a of the driving gear 1 meshes with the driven gear 2 at the meshing point B1, and further rotates from the meshing position located on the center line connecting the rotation centers G1, G2 of the two gears 1, 2 , The volume surrounded by the tooth tip of the driving gear 1a on the center line and the tooth bottom of the driven gear 2 (hereinafter referred to as the binding volume v) increases. However, since the binding volume v is blocked from the groove 5 communicating with the discharge port 4, the binding volume v does not suck the discharge oil from the discharge port 4. For this reason, it is possible to prevent a decrease in volumetric efficiency that has been a problem in the prior art. Although the binding volume v decreases up to the meshing position, the binding volume v is communicated with the discharge port 4 through the groove 5, so that the high pressure oil in the binding volume v is not further compressed. . For this reason, generation | occurrence | production of a vibration and noise is prevented reliably.
[0015]
In FIG. 2, the groove 5 communicating with the discharge port 4 and the groove 7 communicating with the suction port 6 are the boundary on the discharge side of the driving gear 1 or the boundary on the suction side of the driven gear 2 with the meshing position in FIG. It is blocked by either. Accordingly, since the groove 5 communicating with the discharge port 4 and the groove 7 communicating with the suction port 6 do not communicate with each other via the binding volumes u and v, a decrease in volume efficiency is prevented.
[0016]
In FIG. 3, when one tooth 2c of the driven gear 2 is meshed with the driving gear 1 at the meshing point B3 from the meshing position located on the center line connecting the rotation centers G1 and G2 of the two gears 1 and 2, the binding volume is increased. u expands. However, since the binding volume u communicates with the suction port 6, oil is not replenished from the suction port 6 and does not become negative pressure. In addition, since the oil is replenished from the suction port 6 instead of the discharge port 4, the volumetric efficiency is not lowered. Until the meshing position, the binding volume u decreases, so that further compression will cause the high pressure oil of the penetration volume u to be partially discharged to the suction port 6 through the gap B4, and the other notches as in the prior art. Or it discharges | emits from the escape groove | channel (illustration omitted) to the groove | channel 5, and generation | occurrence | production of a vibration and noise is prevented. In addition, the boundary which continues to each boundary of the said groove | channel 5 and the groove | channel 7 is formed by the root circle 1f, 1g and 2f, 2g, the groove | channel 5 and the groove | channel 7 are enlarged, and the oil leak from the discharge side to the suction side It is preventing.
[0017]
A second embodiment of the present invention will be described in detail with reference to FIGS.
The configuration of the second embodiment is in contact with the tooth outline 2b on the discharge port 4 side of the driven gear 2a adjacent to the tooth 1a on the center line, and the center on the meshing line as compared with the configuration of the first embodiment. A groove communicating with the discharge port 4 by a tangent line T intersecting at a point Q having a length half the normal pitch (tn / 2) from the intersection point P with the line and a radial line N of the driving gear 1a passing through the point Q The configuration is the same as that of the first embodiment except that the boundary of 5 is used.
[0018]
The operational effects of the configuration of the second embodiment will be described.
The boundary of the groove 5 communicating with the discharge port 4 is in contact with the tooth outline of the driven gear 2a adjacent to the tooth 1a on the center line of the driving gear 1 on the discharge port 4 side, and on the meshing line with the center line. Since the tangent line T intersects at a point having a length of half normal pitch (tn / 2) from the intersection point P, the shape is substantially the same as that of the first embodiment. For this reason, the same effect as the first embodiment can be obtained. However, the boundary of the groove 5 communicating with the discharge port 4 is not the tooth outline 2b of the driven gear 2a as in the first embodiment, but the tangent T of the tooth outline 2b of the driven gear 2a. Therefore, there is a slight dead zone in the communication between the groove 5 communicating with the discharge port 4 and the binding volume v, and in the blocking area. Therefore, when the groove 5 communicating with the discharge port 4 and the binding volume v are blocked, the high-pressure oil at the discharge port filling the binding volume v is slightly compressed, but the groove 5 communicating with the discharge port 4 Since the boundary is a straight line, the processing cost is reduced.
[Brief description of the drawings]
1A and 1B are views showing a reference meshing state of a first embodiment of a gear pump according to the present invention, wherein FIG. 1A is a front view, and FIG. 1B is a side view.
FIG. 2 is a diagram showing a meshing state after the meshing state of FIG. 1;
FIG. 3 is a diagram showing a meshing state after the meshing state of FIG. 2;
4A and 4B are diagrams showing a reference meshing state of a second embodiment of the gear pump according to the present invention, wherein FIG. 4A is a front view, and FIG. 4B is a side view.
FIG. 5 is a diagram showing a meshing state after the meshing state of FIG. 4;
6 is a view showing a meshing state after the meshing state of FIG. 5; FIG.
FIGS. 7A and 7B are diagrams showing a reference meshing state of a gear pump according to the related art, where FIG. 7A is a front view and FIG. 7B is a side view.
FIG. 8 is a diagram showing a meshing state before the meshing state of FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Drive gear 1a Tooth 1b on the center line of the drive gear 1b, 1e of the drive gear adjacent to the tooth on the center line of the drive gear 1f, 1g Tooth root line 1f, 1g of the drive gear The tooth 2b, 2e of the driven gear adjacent to the tooth on the center line of the gear The tooth outline 2c of the driven gear The tooth 2f, 2g on the center line of the driven gear 3 The bottom circle 3 of the driven gear 4 The side plate 4 The discharge port 5 The communication with the discharge port Groove 6 Suction port 7 Groove communicating with the suction port G1 Rotation center G2 of driven gear T2 Rotation center T of driven gear T Tan tangent Q Contact R Arc B1, B3 Engagement point B2, B4 Gap

Claims (2)

互いに噛合う外歯歯車よりなる原動歯車(1) および従動歯車(2) と、両歯車(1,2) のとじ込み容積部を吐出口(4) または吸入口(6) に連通する溝(5,7) を形成した側板(3) とを有する歯車ポンプにおいて、
原動歯車(1) の一つの歯(1a)が両歯車(1,2) の回転中心(G1,G2) を結ぶ中心線上に位置するとき、この中心線上の歯(1a)に隣接する従動歯車(2a)の吐出口(4)側の歯元外形線(2b)を、吐出口(4) に連通する溝(5) の境界とし、
有効噛合点(A1 ,A2 )の中間の噛合点である無効噛合点がピッチ点(P)を通るときの吐出側の噛合中の原動歯車(1d)の歯元外形線(1e)を原動歯車(1)の吐出側の境界とし、また、前記無効噛合点がピッチ点(P)を通るときの吸入側の噛合中の従動歯車(2d)の歯元外形線(2e)を従動歯車(2)の吸入側の境界とし、
従動歯車(2)の一つの歯(2c)が両歯車(1,2) の回転中心(G1,G2) を結ぶ中心線上に位置するとき、この中心線上の歯(2c)に隣接する原動歯車(1b)の吸入口(6) 側の歯元外形線(1c)を、吸入口(6) に連通する溝(7) の境界とする
ことを特徴とする歯車ポンプ。
The driving gear (1) and driven gear (2) consisting of external gears meshing with each other, and a groove (5) that connects the binding volume of both gears (1, 2) to the discharge port (4) or the suction port (6). , 7) and a side plate (3) formed with a gear pump,
When one tooth (1a) of the driving gear (1) is located on the center line connecting the rotation centers (G1, G2) of both gears (1, 2), the driven gear adjacent to the tooth (1a) on this center line The root outline (2b) on the discharge port (4) side of (2a) is defined as the boundary of the groove (5) communicating with the discharge port (4).
When the invalid mesh point, which is an intermediate mesh point between the effective mesh points (A1, A2), passes through the pitch point (P), the tooth outline (1e) of the primed gear (1d) during meshing on the discharge side is represented by the prime gear. The boundary on the discharge side of (1) and the tooth outline (2e) of the meshing driven gear (2d) on the suction side when the invalid meshing point passes through the pitch point (P) are the driven gear (2 )
When one tooth (2c) of the driven gear (2) is located on the center line connecting the rotation centers (G1, G2) of the two gears (1, 2), the driving gear adjacent to the tooth (2c) on this center line A gear pump characterized in that the tooth outline (1c) on the inlet (6) side of (1b) is a boundary of a groove (7) communicating with the inlet (6).
互いに噛合う外歯歯車よりなる原動歯車(1) および従動歯車(2) と、両歯車(1,2) のとじ込み容積部を吐出口(4) または吸入口(6) に連通する溝(5,7) を形成した側板(3) とを有する歯車ポンプにおいて、
原動歯車(1) の一つの歯(1a)が両歯車(1,2) の回転中心(G1,G2) を結ぶ中心線上に位置するとき、この中心線上の歯(1a)に隣接する従動歯車(2a)の吐出口(4)側の歯元外形線(2b)に接し、かつ、噛合線上で前記中心線との交点(P) から半ピッチの長さの点(Q) で交差する接線を、吐出口(4) に連通する溝(5) の境界とする
ことを特徴とする歯車ポンプ。
The driving gear (1) and driven gear (2) consisting of external gears meshing with each other, and a groove (5) that connects the binding volume of both gears (1, 2) to the discharge port (4) or the suction port (6). , 7) and a side plate (3) formed with a gear pump,
When one tooth (1a) of the driving gear (1) is located on the center line connecting the rotation centers (G1, G2) of both gears (1, 2), the driven gear adjacent to the tooth (1a) on this center line A tangent line that touches the tooth outline (2b) on the discharge port (4) side of (2a) and intersects at a half-pitch length point (Q) from the intersection (P) with the center line on the meshing line Is a boundary of the groove (5) communicating with the discharge port (4).
JP12970898A 1998-04-24 1998-04-24 Gear pump Expired - Fee Related JP3919934B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP12970898A JP3919934B2 (en) 1998-04-24 1998-04-24 Gear pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP12970898A JP3919934B2 (en) 1998-04-24 1998-04-24 Gear pump

Publications (2)

Publication Number Publication Date
JPH11303766A JPH11303766A (en) 1999-11-02
JP3919934B2 true JP3919934B2 (en) 2007-05-30

Family

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Family Applications (1)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103758757B (en) * 2014-01-27 2016-02-17 浙江理工大学 Eight blade differential pumps that a kind of Fourier's noncircular gear drives

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