JP5314784B2 - Internal gear pump - Google Patents

Internal gear pump Download PDF

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JP5314784B2
JP5314784B2 JP2012089410A JP2012089410A JP5314784B2 JP 5314784 B2 JP5314784 B2 JP 5314784B2 JP 2012089410 A JP2012089410 A JP 2012089410A JP 2012089410 A JP2012089410 A JP 2012089410A JP 5314784 B2 JP5314784 B2 JP 5314784B2
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gears
pressure
internal gear
teeth
discharge
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JP2012154340A (en
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勝則 石河
春彦 柴田
昌史 成田
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Toyooki Kogyo Co Ltd
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Description

本発明は、複数の吐出ポートを有する内接歯車ポンプに関する。   The present invention relates to an internal gear pump having a plurality of discharge ports.

この種の内接歯車ポンプは、ポンプハウジングの収容孔に、内歯を有するリング状の内歯歯車を回転自在に収容し、この内歯歯車の内歯と内接噛み合いする外歯を有する外歯歯車を内歯歯車の内部に偏心して収容し、両歯車の側面が摺接するポンプハウジングの摺接面としての収装孔の底面には、両歯車の回転に伴い両歯間の噛み合い隙間が増加する吸入域空間に連通して吸入ポートを開口すると共に、両歯間の噛み合い隙間が減少する吐出域空間に連通して、両歯車の回転方向に離間して二つの吐出ポートを開口して形成する。そして、二つの吐出ポートのうちで、両歯車の回転方向の後方側に位置する一方の吐出ポート(特許文献1では第3吐出ポートと記載されている。)を潤滑や冷却のための低圧の油圧回路に連通し、また、一方の吐出ポートより両歯車の回転方向の前方側に位置する他方の吐出ポート(特許文献1では第2吐出ポートと記載されている。)をシフトコントロールバルブ等の高圧の油圧回路に連通し、一つのポンプで二つの供給先に異なる圧力の作動油を供給できるようにしている。   In this type of internal gear pump, a ring-shaped internal gear having internal teeth is rotatably accommodated in an accommodation hole of the pump housing, and an external tooth having external teeth that mesh with the internal teeth of the internal gear. The tooth gear is eccentrically housed inside the internal gear, and the meshing gap between both teeth is formed on the bottom surface of the receiving hole as the sliding contact surface of the pump housing where the side surfaces of both gears are in sliding contact. Opening the suction port in communication with the increasing suction area space, communicating with the discharge area space in which the meshing gap between both teeth is reduced, and opening the two discharge ports apart in the rotational direction of both gears Form. Of the two discharge ports, one discharge port (described as the third discharge port in Patent Document 1) located on the rear side in the rotational direction of both gears is a low pressure for lubrication and cooling. The other discharge port (described as the second discharge port in Patent Document 1) that communicates with the hydraulic circuit and is located on the front side in the rotational direction of both gears from one discharge port is a shift control valve or the like. It communicates with a high-pressure hydraulic circuit so that a single pump can supply hydraulic oil of different pressures to two supply destinations.

特開2001−123967号公報(段落番号0028、0032、0033、図1)JP 2001-123967 A (paragraph numbers 0028, 0032, 0033, FIG. 1)

ところが、かかる従来の内接歯車ポンプでは、両歯車の回転方向の後方側に位置する一方の吐出ポートを低圧とし、両歯車の回転方向の前方側に位置する他方の吐出ポートを高圧としている。このため、低圧となる一方の吐出ポートが開口する箇所では、内歯歯車の内周側に作用する圧力より、高圧となる他方の吐出ポートから内歯歯車の側面を介して外周側に漏出して内歯歯車の外周側に作用する圧力のほうが高くなり、内歯歯車は内周側に作用する圧力と外周側に作用する圧力との圧力差に基づく作用力で吸入ポートが位置する側に向けて収装孔内周面に押圧される。なお、外歯歯車は、外周側に作用する吸入ポートの圧力と一方、他方の吐出ポートの圧力との圧力差に基づく作用力で吸入ポートが位置する側に向けて収装孔内周面に押圧される。よって、内歯歯車が外歯歯車と同一方向に押圧されるから、内歯と外歯との噛み合い位置が、両歯間の噛み合い隙間が最小となる位置近傍にある最適噛み合い位置より回転方向の前方側にずれてしまい、両歯の噛み合いが不安定になって僅かな圧力変動で噛み合い位置が隣接する歯に移ってしまうことがあり、両歯の接触・非接触の繰り返しに伴い騒音、振動が高くなる問題があった。   However, in such a conventional internal gear pump, one discharge port located on the rear side in the rotation direction of both gears is set to a low pressure, and the other discharge port located on the front side in the rotation direction of both gears is set to a high pressure. For this reason, at the location where one discharge port that becomes low pressure opens, the pressure that acts on the inner peripheral side of the internal gear leaks from the other discharge port that becomes high pressure to the outer peripheral side via the side surface of the internal gear. Therefore, the pressure acting on the outer peripheral side of the internal gear is higher, and the internal gear is on the side where the suction port is located by the acting force based on the pressure difference between the pressure acting on the inner peripheral side and the pressure acting on the outer peripheral side. Is pressed toward the inner peripheral surface of the collection hole. The external gear is arranged on the inner peripheral surface of the housing hole toward the side where the suction port is located by the acting force based on the pressure difference between the pressure of the suction port acting on the outer peripheral side and the pressure of the other discharge port. Pressed. Therefore, since the internal gear is pressed in the same direction as the external gear, the meshing position between the internal gear and the external gear is more in the rotational direction than the optimal meshing position in the vicinity of the position where the meshing clearance between the two teeth is minimized. It may shift to the front side, the meshing of both teeth may become unstable, and the meshing position may move to the adjacent tooth with slight pressure fluctuations. Noise and vibration will occur with repeated contact and non-contact of both teeth. There was a problem that increased.

本発明の課題は、一つのポンプで二つの供給先に異なる圧力の作動油を供給し、内歯と外歯とを最適の噛み合い位置で噛み合いし、騒音、振動を低減し得る内接歯車ポンプを提供するものである。   An object of the present invention is to provide an internal gear pump capable of reducing noise and vibration by supplying hydraulic oils having different pressures to two supply destinations with one pump and meshing internal teeth and external teeth at an optimal meshing position. Is to provide.

かかる課題を達成すべく、本発明は次の手段をとった。即ち、
ポンプハウジングの収容孔に内歯を有するリング状の内歯歯車を回転自在に収容し、内歯歯車の内歯と内接噛み合いする外歯を有する外歯歯車を内歯歯車の内部に偏心して収容し、外歯歯車は回転軸に係合して回転駆動され、両歯車間には両歯車の回転により両歯間の噛み合い隙間が増加する領域に吸入域空間を形成すると共に、両歯車の回転により両歯間の噛み合い隙間が減少する領域に吐出域空間を形成し、収容孔に収容した両歯車の側面が摺接するポンプハウジングの摺接面には、吸入域空間に連通して吸入ポートを開口すると共に、吐出域空間に連通して両歯車の回転方向に離間する二つの吐出ポートを開口し、この二つの吐出ポートは、両歯車の回転方向の後方側に位置する一方の吐出ポートの圧力を高圧側に連通し、両歯車の回転方向の前方側に位置する他方の吐出ポートの圧力を一方の吐出ポートの圧力より低圧の低圧側に連通したことを特徴とする内接歯車ポンプがそれである。
In order to achieve this problem, the present invention has taken the following measures. That is,
A ring-shaped internal gear having internal teeth is rotatably accommodated in the housing hole of the pump housing, and the external gear having external teeth that are in mesh with the internal teeth of the internal gear is eccentric to the internal gear. The external gear engages with the rotating shaft and is driven to rotate. Between the two gears, a suction area space is formed in a region where the meshing gap between the two teeth increases due to the rotation of the two gears. A discharge area space is formed in an area where the meshing gap between both teeth is reduced by rotation, and the sliding surface of the pump housing where the side surfaces of both gears accommodated in the accommodation hole are in sliding contact communicates with the suction area space. And two discharge ports that communicate with the discharge area space and are spaced apart in the rotation direction of both gears. The two discharge ports are one discharge port located on the rear side in the rotation direction of both gears. The pressure of the two gears Internal gear pump, characterized in that communicating the pressure of the other discharge ports located at the front side in the direction to the low pressure side of the pressure of the low pressure of one of the discharge port is it.

以上詳述したように、請求項1に記載の発明は、二つの吐出ポートは、両歯車の回転方向の後方側に位置する一方の吐出ポートの圧力を高圧側に連通し、両歯車の回転方向の前方側に位置する他方の吐出ポートの圧力を一方の吐出ポートの圧力より低圧の低圧側に連通する。このため、高圧側に連通する一方の吐出ポートが開口する箇所では、内歯歯車の内周側に作用する圧力が、高圧側に連通する一方の吐出ポートから内歯歯車の側面を介して外周側に漏出して内歯歯車の外周側に作用する圧力より高くなり、内歯歯車は内周側に作用する圧力と外周側に作用する圧力との圧力差に基づく作用力で一方、他方の吐出ポートが位置する側に向けて収装孔内周面に押圧される。なお、外歯歯車は、外周側に作用する吸入ポートの圧力と一方、他方の吐出ポートの圧力との圧力差に基づく作用力で吸入ポートが位置する側に向けて収装孔内周面に押圧される。よって、内歯歯車は外歯歯車が押圧される方向と対向する反対方向に押圧されるから、内歯と外歯との噛み合い位置が、両歯間の噛み合い隙間が最小となる位置近傍にある最適噛み合い位置に安定して位置でき、騒音、振動を低減することができる。   As described above in detail, in the invention described in claim 1, the two discharge ports communicate the pressure of one discharge port located on the rear side in the rotation direction of both gears to the high pressure side, and rotate both gears. The pressure of the other discharge port located on the front side in the direction is communicated to the low pressure side, which is lower than the pressure of one discharge port. For this reason, at the location where one discharge port communicating with the high pressure side opens, the pressure acting on the inner peripheral side of the internal gear is changed from the one discharge port communicating with the high pressure side to the outer periphery via the side surface of the internal gear. The internal gear has an acting force based on the pressure difference between the pressure acting on the inner peripheral side and the pressure acting on the outer peripheral side, while the pressure on the other side of the internal gear is higher than the pressure acting on the outer peripheral side of the internal gear. It is pressed against the inner peripheral surface of the collection hole toward the side where the discharge port is located. The external gear is arranged on the inner peripheral surface of the housing hole toward the side where the suction port is located by the acting force based on the pressure difference between the pressure of the suction port acting on the outer peripheral side and the pressure of the other discharge port. Pressed. Therefore, since the internal gear is pressed in the opposite direction opposite to the direction in which the external gear is pressed, the meshing position between the internal teeth and the external teeth is in the vicinity of the position where the meshing gap between both teeth is minimized. It can be stably positioned at the optimum meshing position, and noise and vibration can be reduced.

本発明の一実施形態を示した内接歯車ポンプの縦断面図である。It is a longitudinal cross-sectional view of the internal gear pump which showed one Embodiment of this invention. 図1の線A−Aに沿った断面図である。It is sectional drawing along line AA of FIG. ポンプ性能の測定結果を示す特性図である。It is a characteristic view which shows the measurement result of pump performance.

以下、自動車の自動変速機のポンプに適用した本発明の一実施形態を図面に基づき説明する。
図1および図2において、1はポンプ本体で、有底の収容孔2を一端面に開口形成している。3は蓋部材で、収容孔2の開口を閉じるようポンプ本体1にボルト部材4で締結している。そして、ポンプ本体1と蓋部材3とでポンプハウジング5を構成している。6はリング状の内歯歯車で、10個の内歯6Aを有し、収容孔2へ回転自在に収容している。7は外歯歯車で、内歯6Aと内接噛み合いする9個の外歯7Aを有し、内歯歯車6の内部に偏心して収容している。そして、両歯車6、7の軸方向一側面は有底の収装孔2の底面2Aに、また、両歯車6、7の軸方向他側面は収容孔2の開口を閉じる蓋部材3の一側面3Aにそれぞれ摺接可能とする。収装孔2の底面2Aおよび蓋部材3の一側面3Aを両歯車6、7の側面が摺接するポンプハウジング5の摺接面としている。外歯歯車7は中心に貫通孔7Bを軸方向へ貫通形成し、貫通孔7Bには潤滑性に優れ焼き付き難くするよう銅合金から成した円筒状の軸受ブッシュ部材8を圧入して固定している。また、貫通孔7Bの径方向へ対向する2箇所に凹部7Cを窪み形成している。
Hereinafter, an embodiment of the present invention applied to a pump of an automatic transmission of an automobile will be described with reference to the drawings.
1 and 2, reference numeral 1 denotes a pump body, which has a bottomed receiving hole 2 formed at one end surface. A lid member 3 is fastened to the pump body 1 with a bolt member 4 so as to close the opening of the accommodation hole 2. The pump main body 1 and the lid member 3 constitute a pump housing 5. Reference numeral 6 denotes a ring-shaped internal gear, which has ten internal teeth 6 </ b> A and is rotatably accommodated in the accommodation hole 2. Reference numeral 7 denotes an external gear, which has nine external teeth 7A that are in mesh with the internal teeth 6A, and is housed eccentrically in the internal gear 6. One side surface in the axial direction of both gears 6, 7 is on the bottom surface 2 A of the bottomed receiving hole 2, and the other side surface in the axial direction of both gears 6, 7 is a part of the lid member 3 that closes the opening of the housing hole 2. Each side surface 3A can be slidably contacted. The bottom surface 2A of the collection hole 2 and one side surface 3A of the lid member 3 are used as the sliding contact surface of the pump housing 5 where the side surfaces of both gears 6 and 7 are in sliding contact. The external gear 7 has a through hole 7B formed in the center in the axial direction, and a cylindrical bearing bush member 8 made of a copper alloy is press-fitted and fixed in the through hole 7B so as to be excellent in lubricity and difficult to seize. Yes. Further, recesses 7C are formed at two locations facing the through hole 7B in the radial direction.

9は固定軸としてのステータシャフトで、ポンプハウジング5の蓋部材3に固定し、先端部がポンプ本体1を貫通して延在し、軸受ブッシュ部材8を摺接自在に外嵌して外歯歯車7を回転自在に軸支している。10は駆動軸としてのオイルポンプドライブハブで、円筒状に形成し、外歯歯車7と同芯にポンプハウジング5のポンプ本体1へ軸受ブッシュ部材11を介して回転自在に軸支し、先端部に径方向の対向する2箇所に凸部10Aを軸方向へ突出して形成し、凸部10Aを外歯歯車7の凹部7Cに挿入して外歯歯車7を回転駆動する。   Reference numeral 9 denotes a stator shaft as a fixed shaft, which is fixed to the lid member 3 of the pump housing 5, has a tip portion extending through the pump body 1, and a bearing bush member 8 is externally fitted so as to be slidable. The gear 7 is rotatably supported. Reference numeral 10 denotes an oil pump drive hub as a drive shaft, which is formed in a cylindrical shape, and is rotatably supported on the pump body 1 of the pump housing 5 via the bearing bush member 11 concentrically with the external gear 7. The convex portions 10A are formed to project in the axial direction at two locations facing each other in the radial direction, and the convex portions 10A are inserted into the concave portions 7C of the external gear 7 to rotationally drive the external gear 7.

Sは吸入域空間、Pは吐出域空間でそれぞれ両歯車6、7間に備え、吸入域空間Sは両歯車6、7の回転により両歯6A、7A間の噛み合い隙間が増加する領域に形成している。また、吐出域空間Pは歯車6、7の回転により両歯6A、7A間の噛み合い隙間が減少する領域に形成している。12A、12Bは吸入域空間Sに連通する吸入ポートで、吸入域空間Sへ軸方向の一方側から連通するポンプ本体1側の吸入ポート12Aは収容孔2の底面2Aに窪み形成して開口し、吸入域空間Sへ軸方向の他方側から連通する蓋部材3側の吸入ポート12Bは蓋部材3の一側面3Aに窪み形成して開口している。13はポンプ本体1に形成の吸入流路で、吸入ポート12A、12Bに接続し、図示しないタンクから吸入する油を流通する。   S is a suction area space, P is a discharge area space, and is provided between the gears 6 and 7, respectively. The suction area space S is formed in a region where the meshing clearance between the teeth 6A and 7A increases as the gears 6 and 7 rotate. doing. Further, the discharge area space P is formed in an area where the meshing gap between the teeth 6A and 7A is reduced by the rotation of the gears 6 and 7. Reference numerals 12A and 12B denote suction ports that communicate with the suction area space S. The suction port 12A on the pump body 1 side that communicates with the suction area space S from one side in the axial direction is formed in the bottom surface 2A of the housing hole 2 so as to be recessed. The suction port 12B on the side of the lid member 3 communicating with the suction area space S from the other side in the axial direction is formed in a recessed manner on one side surface 3A of the lid member 3 and opened. Reference numeral 13 denotes a suction passage formed in the pump body 1, which is connected to the suction ports 12A and 12B and distributes oil sucked from a tank (not shown).

14A、14Bと15A、15Bは吐出域空間Pに連通して両歯車6、7の回転方向Bに離間する二つの吐出ポートで、両歯車6、7の回転方向Bの後方側に位置する一方の吐出ポート14A、14Bと回転方向Bの前方側に位置する他方の吐出ポート15A、15Bとから成る。一方の吐出ポート14A、14Bはポンプ本体1に形成の第1吐出流路16に接続し、この第1吐出流路16よりシフトコントロールバルブ等の高圧の油圧回路に連通して高圧とし、吐出域空間Pへ軸方向の一方側から連通するポンプ本体1側の一方の吐出ポート14Aは収容孔2の底面2Aに窪み形成して開口し、吐出域空間Pへ軸方向の他方側から連通する蓋部材3側の一方の吐出ポート14Bは蓋部材3の一側面3Aに窪み形成して開口している。   14A, 14B and 15A, 15B are two discharge ports that communicate with the discharge area space P and are spaced apart in the rotational direction B of both gears 6, 7, and are located on the rear side in the rotational direction B of both gears 6, 7. The discharge ports 14A and 14B and the other discharge ports 15A and 15B located on the front side in the rotation direction B are formed. One discharge port 14A, 14B is connected to a first discharge flow path 16 formed in the pump body 1, and communicates with the high pressure hydraulic circuit such as a shift control valve from the first discharge flow path 16 to increase the pressure. One discharge port 14A on the pump body 1 side that communicates with the space P from one side in the axial direction is formed by opening a recess in the bottom surface 2A of the receiving hole 2, and a lid that communicates with the discharge region space P from the other side in the axial direction. One discharge port 14 </ b> B on the side of the member 3 is formed in a recessed manner on one side surface 3 </ b> A of the lid member 3 and opened.

他方の吐出ポート15A、15Bは、ポンプ本体1に形成の第2吐出流路17に接続し、この第2吐出流路17より潤滑や冷却のための低圧の油圧回路に連通して一方の吐出ポート14A、14Bの圧力より低圧とし、吐出域空間Pへ軸方向の一方側から連通するポンプ本体1側の他方の吐出ポート15Aは収容孔2の底面2Aに窪み形成して開口し、吐出域空間Pへ軸方向の他方側から連通する蓋部材3側の他方の吐出ポート15Bは蓋部材3の一側面3Aに窪み形成して開口している。   The other discharge ports 15A and 15B are connected to a second discharge flow path 17 formed in the pump body 1, and communicate with a low pressure hydraulic circuit for lubrication and cooling from the second discharge flow path 17 to discharge one of the discharge ports. The other discharge port 15A on the pump main body 1 side communicating with the discharge region space P from one side in the axial direction is formed in a recess in the bottom surface 2A of the receiving hole 2 and opened. The other discharge port 15 </ b> B on the lid member 3 side communicating with the space P from the other side in the axial direction is formed in a recessed manner on one side surface 3 </ b> A of the lid member 3.

次に、かかる構成の作動を説明する。
オイルポンプドライブハブ10により外歯歯車7を回転駆動すると、外歯歯車7と内接噛み合いする内歯歯車6が回転駆動され、吸入流路13の油が吸入ポート12A、12Bより吸入域空間Sに吸入されて吐出域空間Pに搬送され、一方の吐出ポート14A、14Bおよび他方の吐出ポート15A、15Bより吐出され、一方の吐出ポート14A、14Bに吐出された油は第1吐出流路16を流れてシフトコントロールバルブ等の高圧の油圧回路に供給される。また、他方の吐出ポート15A、15Bに吐出された油は第2吐出流路17を流れて潤滑や冷却のための低圧の油圧回路に供給される。
Next, the operation of this configuration will be described.
When the external gear 7 is rotationally driven by the oil pump drive hub 10, the internal gear 6 that is in mesh with the external gear 7 is rotationally driven, and the oil in the suction passage 13 is sucked through the suction ports 12A and 12B through the suction area S. The oil discharged into the discharge area space P and discharged from the one discharge port 14A, 14B and the other discharge port 15A, 15B, and the oil discharged to the one discharge port 14A, 14B is the first discharge flow path 16. And is supplied to a high-pressure hydraulic circuit such as a shift control valve. The oil discharged to the other discharge ports 15A and 15B flows through the second discharge passage 17 and is supplied to a low pressure hydraulic circuit for lubrication and cooling.

かかる作動で、両歯車6、7の回転方向Bの後方側に位置する一方の吐出ポート14A、14Bの圧力を高圧にし、両歯車6、7の回転方向Bの前方側に位置する他方の吐出ポート15A、15Bの圧力を一方の吐出ポート14A、14Bの圧力より低圧にする。このため、高圧となる一方の吐出ポート14A、14Bが開口する箇所では、内歯歯車6の内周側に作用する圧力が、高圧となる一方の吐出ポート14A、14Bから内歯歯車6の側面を介して外周側に漏出して内歯歯車6の外周側に作用する圧力より高くなり、内歯歯車6は内周側に作用する圧力と外周側に作用する圧力との圧力差に基づく作用力で一方、他方の吐出ポート14A、14B、15A、15Bが位置する側、すなわち図2の左方向に向けて矢印Cで示す如き収装孔2内周面に押圧される。なお、外歯歯車7は、外周側に作用する吸入ポート12A、12Bの圧力と一方、他方の吐出ポート14A、14B、15A、15Bの圧力との圧力差に基づく作用力で吸入ポート12A、12Bが位置する側、すなわち図2の右方向に向けて矢印Dで示す如き収装孔2内周面に押圧される。よって、内歯歯車6は外歯歯車7が押圧される方向と対向する反対方向に押圧されるから、内歯6Aと外歯7Aとの噛み合い位置が、両歯6A、7A間の噛み合い隙間が最小となる位置近傍にある最適噛み合い位置Eに安定して位置でき、騒音、振動を低減することができる。   With this operation, the pressure of one discharge port 14A, 14B located on the rear side in the rotation direction B of both gears 6, 7 is increased, and the other discharge located on the front side in the rotation direction B of both gears 6, 7 is performed. The pressure of the ports 15A and 15B is set to be lower than the pressure of one of the discharge ports 14A and 14B. For this reason, in the location where one discharge port 14A, 14B which becomes high pressure opens, the pressure which acts on the inner peripheral side of internal gear 6 is the side of internal gear 6 from one discharge port 14A, 14B which becomes high pressure. The pressure is higher than the pressure acting on the outer peripheral side of the internal gear 6 through leakage to the outer peripheral side, and the internal gear 6 is based on the pressure difference between the pressure acting on the inner peripheral side and the pressure acting on the outer peripheral side. With one force, the other discharge port 14A, 14B, 15A, 15B is pressed to the inner peripheral surface of the collection hole 2 as shown by the arrow C toward the left side in FIG. In addition, the external gear 7 is a suction port 12A, 12B with an action force based on a pressure difference between the pressure of the suction ports 12A, 12B acting on the outer peripheral side and the pressure of the other discharge port 14A, 14B, 15A, 15B. Is pressed against the inner peripheral surface of the collection hole 2 as indicated by the arrow D toward the right side of FIG. Therefore, since the internal gear 6 is pressed in the opposite direction opposite to the direction in which the external gear 7 is pressed, the meshing position between the internal teeth 6A and the external teeth 7A is the meshing gap between both the teeth 6A and 7A. It can be stably positioned at the optimum meshing position E in the vicinity of the minimum position, and noise and vibration can be reduced.

また、外歯歯車7には軸受ブッシュ部材8を備え、ポンプハウジング5には駆動軸としてのオイルポンプドライブハブ10とは別の固定軸としてのステータシャフト9を備え、外歯歯車7を軸受ブッシュ部材8を介してポンプハウジング5のステータシャフト9に回転自在に軸支する。このため、外歯歯車7を径方向へのがたつきを抑制して軸支できるから、外歯歯車7を最適噛み合い位置Eにより一層安定して位置でき、内歯歯車6を最適噛み合い位置Eに安定して位置できることと相俟って、騒音、振動を一層低減することができる。   The external gear 7 includes a bearing bush member 8, the pump housing 5 includes a stator shaft 9 as a fixed shaft different from the oil pump drive hub 10 as a drive shaft, and the external gear 7 is connected to the bearing bush. The shaft 8 is rotatably supported on the stator shaft 9 of the pump housing 5 via the member 8. For this reason, since the external gear 7 can be pivotally supported while suppressing rattling in the radial direction, the external gear 7 can be positioned more stably at the optimal meshing position E, and the internal gear 6 can be positioned at the optimal meshing position E. Therefore, noise and vibration can be further reduced.

いま、内歯歯車6と外歯歯車7の歯形のモジュール7.36、内歯歯車6の歯数10、外歯歯車7の歯数9、押しのけ容積14cc/rev、両歯車6、7の回転方向Bの後方側に位置する一方の吐出ポート14A、14Bの圧力を高圧の2.0MPa、両歯車6、7の回転方向Bの前方側に位置する他方の吐出ポート15A、15Bの圧力を低圧の0.5MPaとした本発明の一実施形態に相当する内接歯車ポンプで、騒音値を測定したところ、回転数1000rpmで72.7dB、回転数1500rpmで74.3dB、回転数2000rpmで73.3dB、回転数2500rpmで75.4dB、回転数3000rpmで79.8dB、回転数3500rpmで83.2dBであった。   Now, the tooth shape module 7.36 of the internal gear 6 and the external gear 7, the number of teeth of the internal gear 6, the number of teeth of the external gear 7, the displacement of 14 cc / rev, the rotation of both gears 6 and 7 The pressure at one discharge port 14A, 14B located on the rear side in the direction B is 2.0 MPa for high pressure, and the pressure on the other discharge port 15A, 15B located on the front side in the rotation direction B for both gears 6, 7 is low. When the noise value was measured with an internal gear pump corresponding to one embodiment of the present invention, which was 0.5 MPa, the rotation speed was 1000 rpm, 72.7 dB, the rotation speed 1500 rpm, 74.3 dB, and the rotation speed 2000 rpm. They were 3 dB, 75.4 dB at a rotational speed of 2500 rpm, 79.8 dB at a rotational speed of 3000 rpm, and 83.2 dB at a rotational speed of 3500 rpm.

しかるに、かかる諸元で両歯車6、7の回転方向Bの後方側に位置する一方の吐出ポート14A、14Bの圧力を低圧の0.5MPa、両歯車6、7の回転方向Bの前方側に位置する他方の吐出ポート15A、15Bの圧力を高圧の2.0MPaとした従来の内接歯車ポンプで、騒音値を測定したところ、回転数1000rpmで73.6dB、回転数1500rpmで75.4dB、回転数2000rpmで81.8dB、回転数2500rpmで82.5dB、回転数3000rpmで83dB、回転数3500rpmで90.7dBであった。   However, in such specifications, the pressure of one discharge port 14A, 14B located on the rear side in the rotational direction B of both gears 6, 7 is set to 0.5 MPa, which is a low pressure, and the front side in the rotational direction B of both gears 6, 7. When the noise value was measured with a conventional internal gear pump in which the pressure of the other discharge port 15A, 15B positioned was 2.0 MPa, which was a high pressure, 73.6 dB at a rotation speed of 1000 rpm, 75.4 dB at a rotation speed of 1500 rpm, The rotation speed was 81.8 dB at 2000 rpm, 82.5 dB at 2500 rpm, 83 dB at 3000 rpm, and 90.7 dB at 3500 rpm.

これらの測定結果は図3に示す如く、前述の一実施形態に相当する内接歯車ポンプの騒音値は線Fに示すように、前述の従来の内接歯車ポンプに相当する線Gに示す騒音値よりいずれの回転数においても低い値が測定された。   These measurement results are shown in FIG. 3, and the noise value of the internal gear pump corresponding to the above-described one embodiment is indicated by the line F. The noise value indicated by the line G corresponding to the above-described conventional internal gear pump is shown in FIG. A value lower than the value at any number of revolutions was measured.

なお、一実施形態では、ポンプハウジング5を有底の収容孔2を開口形成したポンプ本体1と蓋部材3とで構成したが、収容孔を貫通形成したポンプ本体と収容孔の両端開口を閉塞するようポンプ本体の両側に備えた蓋部材とでポンプハウジングを構成しても良い。また、両歯車6、7の両側面が摺接する収容孔2の底面2A(摺接面)と蓋部材3の一側面3A(摺接面)にそれぞれ吸入ポート12A、12Bおよび吐出ポート14A、14B、15A、15Bを開口したが、吸入ポートおよび吐出ポートをいずれか一つの摺接面に開口しても良いことは勿論である。   In one embodiment, the pump housing 5 is constituted by the pump body 1 and the lid member 3 having the bottomed housing hole 2 formed therein, but the both ends of the pump body and the housing hole that are formed through the housing hole are closed. As such, the pump housing may be configured with lid members provided on both sides of the pump body. Also, suction ports 12A and 12B and discharge ports 14A and 14B are provided on the bottom surface 2A (sliding contact surface) of the housing hole 2 where both side surfaces of both gears 6 and 7 are in sliding contact and one side surface 3A (sliding contact surface) of the lid member 3, respectively. 15A and 15B are opened, but it is needless to say that the suction port and the discharge port may be opened on any one of the sliding contact surfaces.

2:収容孔
2A:底面(摺接面)
3A:一側面(摺接面)
5:ポンプハウジング
6:内歯歯車
6A:内歯
7:外歯歯車
7A:外歯
10:オイルポンプドライブハブ(駆動軸)
12A、12B:吸入ポート
14A、14B:一方の吐出ポート
15A、15B:他方の吐出ポート
S:吸入域空間
P:吐出域空間
2: Housing hole 2A: Bottom surface (sliding contact surface)
3A: One side surface (sliding contact surface)
5: Pump housing 6: Internal gear 6A: Internal gear 7: External gear 7A: External gear 10: Oil pump drive hub (drive shaft)
12A, 12B: Suction port 14A, 14B: One discharge port 15A, 15B: The other discharge port S: Suction area space P: Discharge area space

Claims (1)

ポンプハウジングの収容孔に内歯を有するリング状の内歯歯車を回転自在に収容し、内歯歯車の内歯と内接噛み合いする外歯を有する外歯歯車を内歯歯車の内部に偏心して収容し、外歯歯車は回転軸に係合して回転駆動され、両歯車間には両歯車の回転により両歯間の噛み合い隙間が増加する領域に吸入域空間を形成すると共に、両歯車の回転により両歯間の噛み合い隙間が減少する領域に吐出域空間を形成し、収容孔に収容した両歯車の側面が摺接するポンプハウジングの摺接面には、吸入域空間に連通して吸入ポートを開口すると共に、吐出域空間に連通して両歯車の回転方向に離間する二つの吐出ポートを開口し、この二つの吐出ポートは、両歯車の回転方向の後方側に位置する一方の吐出ポートの圧力を高圧側に連通し、両歯車の回転方向の前方側に位置する他方の吐出ポートの圧力を一方の吐出ポートの圧力より低圧の低圧側に連通したことを特徴とする内接歯車ポンプ。   A ring-shaped internal gear having internal teeth is rotatably accommodated in the housing hole of the pump housing, and the external gear having external teeth that are in mesh with the internal teeth of the internal gear is eccentric to the internal gear. The external gear engages with the rotating shaft and is driven to rotate. Between the two gears, a suction area space is formed in a region where the meshing gap between the two teeth increases due to the rotation of the two gears. A discharge area space is formed in an area where the meshing gap between both teeth is reduced by rotation, and the sliding surface of the pump housing where the side surfaces of both gears accommodated in the accommodation hole are in sliding contact communicates with the suction area space. And two discharge ports that communicate with the discharge area space and are spaced apart in the rotation direction of both gears. The two discharge ports are one discharge port located on the rear side in the rotation direction of both gears. The pressure of the two gears Internal gear pump, characterized in that the pressure of the other discharge ports located at the front side in the direction from the pressure of one of the discharge port in communication with the low pressure side of the low pressure.
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JPH05240166A (en) * 1992-02-28 1993-09-17 Toyooki Kogyo Co Ltd Internal gear pump
JPH05263770A (en) * 1992-03-24 1993-10-12 Unisia Jecs Corp Oil pump
JP3424409B2 (en) * 1995-10-30 2003-07-07 アイシン精機株式会社 Oil pump device
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