JP2012193769A - Inscribed planetary reduction gear and gear pump - Google Patents
Inscribed planetary reduction gear and gear pump Download PDFInfo
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- JP2012193769A JP2012193769A JP2011056750A JP2011056750A JP2012193769A JP 2012193769 A JP2012193769 A JP 2012193769A JP 2011056750 A JP2011056750 A JP 2011056750A JP 2011056750 A JP2011056750 A JP 2011056750A JP 2012193769 A JP2012193769 A JP 2012193769A
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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
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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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
- F04C2/084—Toothed wheels
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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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
- F04C2250/201—Geometry of the rotor conical shape
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Retarders (AREA)
- Rotary Pumps (AREA)
Abstract
Description
本発明は、内接型遊星歯車減速機及び歯車ポンプに関する。 The present invention relates to an inscribed planetary gear reducer and a gear pump.
従来、内周面に円弧歯を備えるアウタロータと、外周面にトロコイド歯を有するインナロータとを備えたトロコイドギアが知られている(例えば、特許文献1参照)。 2. Description of the Related Art Conventionally, a trochoid gear including an outer rotor having arc teeth on an inner peripheral surface and an inner rotor having trochoidal teeth on an outer peripheral surface is known (see, for example, Patent Document 1).
しかしながら、この種の内接型遊星歯車減速機及びこれを備えた歯車ポンプでは、インナギアとアウタギアとの噛み合いに伴って発生する振動を抑えることが課題とされる。 However, in this type of inscribed planetary gear speed reducer and a gear pump including the same, it is a problem to suppress vibrations that occur due to the engagement between the inner gear and the outer gear.
本発明は、上記課題に鑑みてなされたものであって、インナギアとアウタギアとの噛み合いに伴って発生する振動を抑えることができる内接型遊星歯車減速機及び歯車ポンプを提供することを目的とする。 The present invention has been made in view of the above problems, and an object thereof is to provide an inscribed planetary gear reducer and a gear pump that can suppress vibrations generated by meshing between an inner gear and an outer gear. To do.
前記課題を解決するために、請求項1に記載の内接型遊星歯車減速機は、入力軸に偏芯状態で取り付けられ、前記入力軸の回転に伴って偏芯回転されるインナギアと、前記インナギアが内接噛合するアウタギアと、を備え、前記インナギア及び前記アウタギアは、互いの噛合面の直径が軸方向に変化している。 In order to solve the above problem, an inscribed planetary gear speed reducer according to claim 1 is attached to an input shaft in an eccentric state, and is rotated eccentrically as the input shaft rotates, The inner gear and the outer gear, the diameters of the meshing surfaces of the inner gear and the outer gear being changed in the axial direction.
この内接型遊星歯車減速機によれば、インナギア及びアウタギアは、互いの噛合面の直径が軸方向に変化しているので、インナギア及びアウタギアの軸方向のがたつきを抑制することができる。これにより、インナギアとアウタギアとの噛み合いに伴って発生する振動を抑えることができる。しかも、互いの噛合面の直径が軸方向に変化しても、インナギアの噛合面とアウタギアの噛合面との噛合状態が確保されているので(噛合面同士が面接触するので)、単位面積あたりの衝撃が少なくなり、振動を更に抑えることができる。 According to this inscribed planetary gear speed reducer, the inner gear and the outer gear have the diameters of the meshing surfaces of each other changed in the axial direction, so that the axial play of the inner gear and the outer gear can be suppressed. As a result, it is possible to suppress vibrations that occur due to the meshing of the inner gear and the outer gear. Moreover, even if the diameters of the meshing surfaces change in the axial direction, the meshing state between the meshing surface of the inner gear and the meshing surface of the outer gear is ensured (because the meshing surfaces are in surface contact with each other). This reduces the impact and further suppresses vibration.
請求項2に記載の内接型遊星歯車減速機は、入力軸に偏芯状態で取り付けられ、前記入力軸の回転に伴って偏芯回転されるインナギアと、前記インナギアが内接噛合するアウタギアと、を備え、前記インナギア及び前記アウタギアは、互いの噛合面に形成された歯の歯厚が軸方向に変化している。 The inscribed planetary gear reducer according to claim 2 is attached to an input shaft in an eccentric state, and is rotated in an eccentric manner as the input shaft rotates, and an outer gear in which the inner gear is in meshed engagement. In the inner gear and the outer gear, tooth thicknesses of teeth formed on the meshing surfaces of the inner gear and the outer gear are changed in the axial direction.
この内接型遊星歯車減速機によれば、インナギア及びアウタギアは、互いの噛合面に形成された歯の歯厚が軸方向に変化しているので、インナギア及びアウタギアの軸方向のがたつきを抑制することができる。これにより、インナギアとアウタギアとの噛み合いに伴って発生する振動を抑えることができる。しかも、歯の歯厚が軸方向に変化しても、インナギアの噛合面とアウタギアの噛合面との噛合状態が確保されているので(噛合面同士が面接触するので)、単位面積あたりの衝撃が少なくなり、振動を更に抑えることができる。 According to this inscribed planetary gear speed reducer, the inner gear and the outer gear have the tooth thicknesses of the teeth formed on the meshing surfaces of the inner gear and the outer gear changed in the axial direction. Can be suppressed. As a result, it is possible to suppress vibrations that occur due to the meshing of the inner gear and the outer gear. Moreover, even if the tooth thickness changes in the axial direction, the meshing state between the meshing surface of the inner gear and the meshing surface of the outer gear is ensured (since the meshing surfaces are in surface contact), so the impact per unit area And vibration can be further suppressed.
請求項3に記載の内接型遊星歯車減速機は、入力軸に偏芯状態で取り付けられ、前記入力軸の回転に伴って偏芯回転されるインナギアと、前記インナギアが内接噛合するアウタギアと、を備え、前記インナギア及び前記アウタギアは、互いの噛合面の直径及び前記噛合面に形成された歯の歯厚が軸方向に変化している。 An inscribed planetary gear reducer according to claim 3 is attached to an input shaft in an eccentric state and is rotated eccentrically with rotation of the input shaft, and an outer gear in which the inner gear is in meshed engagement In the inner gear and the outer gear, the diameter of the meshing surface and the thickness of the teeth formed on the meshing surface are changed in the axial direction.
この内接型遊星歯車減速機によれば、インナギア及びアウタギアは、噛合面の直径及び互いの噛合面に形成された歯の歯厚が軸方向に変化しているので、インナギア及びアウタギアの軸方向のがたつきを抑制することができる。これにより、インナギアとアウタギアとの噛み合いに伴って発生する振動を抑えることができる。しかも、噛合面の直径及び歯の歯厚が軸方向に変化しても、インナギアの噛合面とアウタギアの噛合面との噛合状態が確保されているので(噛合面同士が面接触するので)、単位面積あたりの衝撃が少なくなり、振動を更に抑えることができる。 According to this inscribed planetary gear reducer, since the inner gear and the outer gear have the diameters of the meshing surfaces and the tooth thicknesses of the teeth formed on the meshing surfaces changed in the axial direction, the axial direction of the inner gear and the outer gear Shaking can be suppressed. As a result, it is possible to suppress vibrations that occur due to the meshing of the inner gear and the outer gear. Moreover, even if the diameter of the meshing surface and the tooth thickness of the teeth change in the axial direction, the meshing state between the meshing surface of the inner gear and the meshing surface of the outer gear is ensured (because the meshing surfaces are in surface contact). The impact per unit area is reduced and vibration can be further suppressed.
請求項4に記載の内接型遊星歯車減速機は、請求項1又は請求項3に記載の内接型遊星歯車減速機において、前記インナギア及び前記アウタギアが、前記噛合面の直径が軸方向一端部から他端部に向けて徐々に変化する構成である。 The inscribed planetary gear reducer according to claim 4 is the inscribed planetary gear reducer according to claim 1 or 3, wherein the inner gear and the outer gear have a diameter of the meshing surface at one end in the axial direction. It is the structure which changes gradually toward an other end part from a part.
この内接型遊星歯車減速機によれば、インナギア及びアウタギアは、噛合面の直径が軸方向一端部から他端部に向けて徐々に変化する構成であるので、インナギアの噛合面とアウタギアの噛合面とを容易に形成することができる。 According to this inscribed planetary gear speed reducer, the inner gear and the outer gear are configured such that the diameter of the meshing surface gradually changes from one end to the other end in the axial direction, so that the meshing surface of the inner gear and the outer gear mesh with each other. The surface can be easily formed.
請求項5に記載の内接型遊星歯車減速機は、請求項1又は請求項3に記載の内接型遊星歯車減速機において、前記インナギア及び前記アウタギアが、前記噛合面の直径が軸方向一端部から中間部に向けて徐々に増加すると共に軸方向中間部から他端部に向けて徐々に減少する構成である。 The inscribed planetary gear reducer according to claim 5 is the inscribed planetary gear reducer according to claim 1 or 3, wherein the inner gear and the outer gear have a diameter of the meshing surface at one end in the axial direction. In this configuration, the distance gradually increases from the intermediate portion toward the intermediate portion and gradually decreases from the axially intermediate portion toward the other end portion.
この内接型遊星歯車減速機によれば、インナギア及びアウタギアは、噛合面の直径が軸方向一端部から中間部に向けて徐々に増加すると共に軸方向中間部から他端部に向けて徐々に減少するので、インナギア及びアウタギアの軸方向両側へのがたつきを抑制することができる。 According to this inscribed planetary gear reducer, the inner gear and the outer gear gradually increase in diameter of the meshing surface from one axial end portion toward the intermediate portion and gradually from the axial intermediate portion toward the other end portion. Since it reduces, the shakiness to the axial direction both sides of an inner gear and an outer gear can be suppressed.
請求項6に記載の内接型遊星歯車減速機は、請求項1又は請求項3に記載の内接型遊星歯車減速機において、前記インナギア及び前記アウタギアが、前記噛合面の直径が軸方向中間部を境に異なっている構成である。 The inscribed planetary gear reducer according to claim 6 is the inscribed planetary gear reducer according to claim 1 or 3, wherein the inner gear and the outer gear are arranged such that the diameter of the meshing surface is intermediate in the axial direction. It is the structure which is different on the border.
この内接型遊星歯車減速機によれば、インナギア及びアウタギアは、噛合面の直径が軸方向中間部を境に異なるという簡単な構成であるので、インナギア及びアウタギアを容易に製造することができる。 According to the inscribed planetary gear reducer, the inner gear and the outer gear have a simple configuration in which the diameters of the meshing surfaces are different from each other at the intermediate portion in the axial direction, and therefore the inner gear and the outer gear can be easily manufactured.
請求項7に記載の内接型遊星歯車減速機は、請求項2又は請求項3に記載の内接型遊星歯車減速機において、前記インナギアが、前記噛合面に形成された歯の歯厚が軸方向一端部から他端部に向けて徐々に減少し、前記アウタギアが、前記噛合面に形成された歯の歯厚が軸方向一端部から他端部に向けて徐々に増加する構成である。 The inscribed planetary gear reducer according to claim 7 is the inscribed planetary gear reducer according to claim 2 or 3, wherein the inner gear has a tooth thickness formed on the meshing surface. The outer gear gradually decreases from one end in the axial direction toward the other end, and the tooth thickness of the teeth formed on the meshing surface gradually increases from one end in the axial direction toward the other end. .
この内接型遊星歯車減速機によれば、インナギアは、噛合面に形成された歯の歯厚が軸方向一端部から他端部に向けて徐々に減少し、アウタギアは、噛合面に形成された歯の歯厚が軸方向一端部から他端部に向けて徐々に増加する構成であるので、インナギアの噛合面とアウタギアの噛合面とを容易に形成することができる。 According to this inscribed planetary gear speed reducer, the inner gear has a tooth thickness formed on the meshing surface that gradually decreases from one end to the other in the axial direction, and the outer gear is formed on the meshing surface. Since the tooth thickness of the teeth gradually increases from one axial end to the other end, the inner gear meshing surface and the outer gear meshing surface can be easily formed.
請求項8に記載の内接型遊星歯車減速機は、請求項2又は請求項3に記載の内接型遊星歯車減速機において、前記インナギアが、前記噛合面に形成された歯の歯厚が軸方向一端部から中間部に向けて徐々に増加すると共に軸方向中間部から他端部に向けて徐々に減少し、前記アウタギアが、前記噛合面に形成された歯の歯厚が軸方向一端部から中間部に向けて徐々に減少すると共に軸方向中間部から他端部に向けて徐々に増加する構成である。 The inscribed planetary gear reducer according to claim 8 is the inscribed planetary gear reducer according to claim 2 or 3, wherein the inner gear has a tooth thickness formed on the meshing surface. The outer gear is gradually increased from one axial end portion toward the intermediate portion and gradually decreased from the axial intermediate portion toward the other end portion. It is the structure which decreases gradually toward an intermediate part from a part, and increases gradually toward an other end part from an axial direction intermediate part.
この内接型遊星歯車減速機によれば、インナギアは、噛合面に形成された歯の歯厚が軸方向一端部から中間部に向けて徐々に増加すると共に軸方向中間部から他端部に向けて徐々に減少し、アウタギアは、噛合面に形成された歯の歯厚が軸方向一端部から中間部に向けて徐々に減少すると共に軸方向中間部から他端部に向けて徐々に増加するので、インナギア及びアウタギアの軸方向両側へのがたつきを抑制することができる。 According to this inscribed planetary gear reducer, the inner gear gradually increases the tooth thickness of the teeth formed on the meshing surface from one axial end portion to the intermediate portion and from the axial intermediate portion to the other end portion. The outer gear gradually decreases from the one axial end portion toward the intermediate portion and gradually increases from the axial intermediate portion toward the other end portion. As a result, rattling of the inner gear and the outer gear on both sides in the axial direction can be suppressed.
請求項9に記載の内接型遊星歯車減速機は、請求項2又は請求項3に記載の内接型遊星歯車減速機において、前記インナギア及び前記アウタギアが、前記噛合面に形成された歯の歯厚が軸方向中間部を境に異なっている構成である。 The inscribed planetary gear reducer according to claim 9 is the inscribed planetary gear reducer according to claim 2 or 3, wherein the inner gear and the outer gear are teeth formed on the meshing surface. The tooth thickness is different at the axially intermediate portion.
この内接型遊星歯車減速機によれば、インナギア及びアウタギアは、噛合面に形成された歯の歯厚が軸方向中間部を境に異なっているという簡単な構成であるので、インナギア及びアウタギアを容易に製造することができる。 According to this inscribed planetary gear speed reducer, the inner gear and the outer gear have a simple configuration in which the tooth thicknesses of the teeth formed on the meshing surface are different from each other at the intermediate portion in the axial direction. It can be manufactured easily.
また、前記課題を解決するために、請求項10に記載の歯車ポンプは、前記入力軸としてのモータシャフトを有するモータ部と、請求項1〜請求項9のいずれか一項に記載の内接型遊星歯車減速機を有すると共に、前記インナギア及び前記アウタギアの間の隙間が圧力室とされ、且つ、前記圧力室と連通される吸入ポート及び吐出ポートが形成されたポンプ部と、を備えている。 Moreover, in order to solve the said subject, the gear pump of Claim 10 is a motor part which has a motor shaft as the said input shaft, The internal part as described in any one of Claims 1-9. And a pump portion in which a gap between the inner gear and the outer gear is used as a pressure chamber, and a suction port and a discharge port communicated with the pressure chamber are formed. .
この歯車ポンプによれば、ポンプ部に、請求項1〜請求項9のいずれか一項に記載の内接型遊星歯車減速機を有するので、インナギアとアウタギアとの噛み合いに伴って発生する振動を抑えることができる。 According to this gear pump, since the pump unit has the inscribed planetary gear reducer according to any one of claims 1 to 9, vibration generated with the meshing of the inner gear and the outer gear is generated. Can be suppressed.
[第一実施形態]
以下、本発明の第一実施形態について説明する。
[First embodiment]
Hereinafter, a first embodiment of the present invention will be described.
図1に示されるように、本発明の第一実施形態に係る歯車ポンプ10は、モータ部12と、ポンプ部14とを備えている。モータ部12は、後述する内接型遊星歯車減速機20への入力軸として、モータシャフト16を有している。 As shown in FIG. 1, the gear pump 10 according to the first embodiment of the present invention includes a motor unit 12 and a pump unit 14. The motor unit 12 has a motor shaft 16 as an input shaft to an inscribed planetary gear reducer 20 described later.
ポンプ部14は、ハウジング18の内部に設けられた内接型遊星歯車減速機20を有している。内接型遊星歯車減速機20は、インナギア22とアウタギア24とを備えている。 The pump unit 14 has an inscribed planetary gear speed reducer 20 provided inside the housing 18. The inscribed planetary gear reducer 20 includes an inner gear 22 and an outer gear 24.
インナギア22は、モータシャフト16に偏芯状態で取り付けられており、モータシャフト16の回転に伴って偏芯回転される。アウタギア24には、インナギア22が内接噛合されている。このインナギア22及びアウタギア24は、ハウジング18に内嵌されたスペーサ26により径方向の動きが規制されており、また、ケーシング28及びカバー30により軸方向の動きが規制されている。 The inner gear 22 is attached to the motor shaft 16 in an eccentric state, and is eccentrically rotated as the motor shaft 16 rotates. An inner gear 22 is in mesh with the outer gear 24. The inner gear 22 and the outer gear 24 are restricted in radial movement by a spacer 26 fitted in the housing 18, and are restricted in axial movement by a casing 28 and a cover 30.
このインナギア22及びアウタギア24の間の隙間は、圧力室32とされている。また、カバー30及びケーシング28には、圧力室32と連通される吸入ポート34及び吐出ポート36がそれぞれ形成されている。 A gap between the inner gear 22 and the outer gear 24 is a pressure chamber 32. In addition, the cover 30 and the casing 28 are formed with a suction port 34 and a discharge port 36 that communicate with the pressure chamber 32, respectively.
そして、このポンプ部14では、インナギア22が偏芯回転されると共に、アウタギア24が回転されることに伴って、圧力室32の位置が変化し、これにより、吸入ポート34を介して外部から圧力室32に流体が吸入され、この流体が圧力室32から吐出ポート36を介して外部に吐出される。 In the pump unit 14, the inner gear 22 is eccentrically rotated, and the outer gear 24 is rotated, so that the position of the pressure chamber 32 is changed, whereby the pressure from the outside via the suction port 34 is changed. A fluid is sucked into the chamber 32, and this fluid is discharged from the pressure chamber 32 to the outside through the discharge port 36.
ここで、上述の内接型遊星歯車減速機20を構成するインナギア22とアウタギア24とは、より具体的には、次のように構成されている。すなわち、図2〜図5に示されるように、インナギア22は、噛合面22Aの直径D1が軸方向一端部22B1から他端部22B2に向けて徐々に小さくなるように変化している。同様に、アウタギア24は、噛合面24Aの直径D2が軸方向一端部24B1から他端部24B2に向けて徐々に小さくなるように変化している。この直径D1,D2の変化の割合は、インナギア22とアウタギア24とで同一となっている。つまり、噛合面22A,24Aは、平行に形成されている。 Here, more specifically, the inner gear 22 and the outer gear 24 constituting the above-described inscribed planetary gear speed reducer 20 are configured as follows. That is, as shown in FIGS. 2 to 5, the inner gear 22 changes so that the diameter D1 of the meshing surface 22A gradually decreases from the one end 22B1 in the axial direction toward the other end 22B2. Similarly, the outer gear 24 changes so that the diameter D2 of the meshing surface 24A gradually decreases from the one axial end 24B1 toward the other end 24B2. The rate of change in the diameters D1 and D2 is the same for the inner gear 22 and the outer gear 24. That is, the meshing surfaces 22A and 24A are formed in parallel.
さらに、インナギア22は、噛合面22Aに形成された歯22Cの歯厚(円ピッチ上の歯の厚さ)T1が軸方向一端部22B1から他端部22B2に向けて徐々に減少しており、アウタギア24は、噛合面24Aに形成された歯24Cの歯厚T2が軸方向一端部24B1から他端部24B2に向けて徐々に増加している。この歯厚T1,T2の変化の割合も、インナギア22とアウタギア24とで同一となっている。 Further, in the inner gear 22, the tooth thickness (tooth thickness on the circular pitch) T1 of the teeth 22C formed on the meshing surface 22A gradually decreases from the one end 22B1 in the axial direction toward the other end 22B2. In the outer gear 24, the tooth thickness T2 of the teeth 24C formed on the meshing surface 24A is gradually increased from the one end 24B1 in the axial direction toward the other end 24B2. The rate of change of the tooth thicknesses T1 and T2 is also the same for the inner gear 22 and the outer gear 24.
次に、本発明の第一実施形態の作用及び効果について説明する。 Next, the operation and effect of the first embodiment of the present invention will be described.
この内接型遊星歯車減速機20によれば、インナギア22及びアウタギア24は、互いの噛合面22A,24Aの直径D1,D2及び歯22C,24Cの歯厚T1,T2が軸方向に変化しているので、インナギア22及びアウタギア24の軸方向のがたつきを抑制することができる。これにより、インナギア22とアウタギア24との噛み合いに伴って発生する振動を抑えることができる。しかも、噛合面22A,24Aの直径D1,D2及び歯22C,24Cの歯厚T1,T2が軸方向に変化しても、インナギア22の噛合面22Aとアウタギア24の噛合面24Aとの噛合状態が確保されているので(噛合面22A,24A同士が面接触するので)、単位面積あたりの衝撃が少なくなり、振動を更に抑えることができる。 According to the inscribed planetary gear speed reducer 20, the inner gear 22 and the outer gear 24 have the diameters D1 and D2 of the meshing surfaces 22A and 24A and the tooth thicknesses T1 and T2 of the teeth 22C and 24C changed in the axial direction. Therefore, the shakiness of the inner gear 22 and the outer gear 24 in the axial direction can be suppressed. As a result, it is possible to suppress vibrations that occur due to the engagement between the inner gear 22 and the outer gear 24. Moreover, even if the diameters D1 and D2 of the meshing surfaces 22A and 24A and the tooth thicknesses T1 and T2 of the teeth 22C and 24C change in the axial direction, the meshing state between the meshing surface 22A of the inner gear 22 and the meshing surface 24A of the outer gear 24 is maintained. Since it is ensured (because the meshing surfaces 22A and 24A are in surface contact), the impact per unit area is reduced, and vibration can be further suppressed.
また、インナギア22及びアウタギア24は、噛合面22A,24Aの直径D1,D2が軸方向一端部22B1,24B1から他端部22B2,24B2に向けて徐々に小さくなるように変化する構成である。また、インナギア22は、歯22Cの歯厚T1が軸方向一端部22B1から他端部22B2に向けて徐々に減少し、アウタギア24は、歯24Cの歯厚T2が軸方向一端部24B1から他端部24B2に向けて徐々に増加する構成である。従って、インナギア22の噛合面22Aとアウタギア24の噛合面24Aとを容易に形成することができる。 Further, the inner gear 22 and the outer gear 24 are configured such that the diameters D1 and D2 of the meshing surfaces 22A and 24A change so as to gradually decrease from the axial one end 22B1 and 24B1 toward the other end 22B2 and 24B2. In the inner gear 22, the tooth thickness T1 of the tooth 22C gradually decreases from the one axial end 22B1 toward the other end 22B2, and the outer gear 24 has the tooth thickness T2 of the tooth 24C from the axial one end 24B1 to the other end. It is the structure which increases gradually toward the part 24B2. Therefore, the meshing surface 22A of the inner gear 22 and the meshing surface 24A of the outer gear 24 can be easily formed.
[第二実施形態]
次に、本発明の第二実施形態について説明する。
[Second Embodiment]
Next, a second embodiment of the present invention will be described.
本発明の第二実施形態では、上述の内接型遊星歯車減速機20(図2〜図5)に代えて、図6〜図8に示される内接型遊星歯車減速機40が用いられている。 In the second embodiment of the present invention, an inscribed planetary gear reducer 40 shown in FIGS. 6 to 8 is used in place of the above inscribed planetary gear reducer 20 (FIGS. 2 to 5). Yes.
この内接型遊星歯車減速機40において、インナギア22は、噛合面22Aの直径D1が軸方向一端部22B1から中間部22B3に向けて徐々に増加すると共に軸方向中間部22B3から他端部22B2に向けて徐々に減少している。同様に、アウタギア24は、噛合面24Aの直径D2が軸方向一端部24B1から中間部24B3に向けて徐々に増加すると共に軸方向中間部24B3から他端部24B2に向けて徐々に減少している。この直径D1,D2の変化の割合は、インナギア22とアウタギア24とで同一となっている。つまり、噛合面22A,24Aは、平行に形成されている。 In this inscribed planetary gear speed reducer 40, the inner gear 22 is configured such that the diameter D1 of the meshing surface 22A gradually increases from the one axial end 22B1 toward the intermediate 22B3 and from the axial intermediate 22B3 to the other end 22B2. It is gradually decreasing toward. Similarly, in the outer gear 24, the diameter D2 of the meshing surface 24A gradually increases from the axial one end 24B1 toward the intermediate portion 24B3 and gradually decreases from the axial intermediate portion 24B3 toward the other end 24B2. . The rate of change in the diameters D1 and D2 is the same for the inner gear 22 and the outer gear 24. That is, the meshing surfaces 22A and 24A are formed in parallel.
さらに、インナギア22は、歯22Cの歯厚T1が軸方向一端部22B1から中間部22B3に向けて徐々に増加すると共に軸方向中間部22B3から他端部22B2に向けて徐々に減少し、アウタギア24は、歯24Cの歯厚T2が軸方向一端部24B1から中間部24B3に向けて徐々に減少すると共に軸方向中間部24B3から他端部24B2に向けて徐々に増加している。この歯厚T1,T2の変化の割合も、インナギア22とアウタギア24とで同一となっている。 Further, in the inner gear 22, the tooth thickness T1 of the tooth 22C gradually increases from the axial one end portion 22B1 toward the intermediate portion 22B3 and gradually decreases from the axial intermediate portion 22B3 toward the other end portion 22B2. The tooth thickness T2 of the tooth 24C gradually decreases from the axial one end 24B1 toward the intermediate portion 24B3 and gradually increases from the axial intermediate portion 24B3 toward the other end 24B2. The rate of change of the tooth thicknesses T1 and T2 is also the same for the inner gear 22 and the outer gear 24.
なお、アウタギア24は、図8に示されるように、軸方向中間部24B3にて第一部材42及び第二部材44に分割されている。 As shown in FIG. 8, the outer gear 24 is divided into a first member 42 and a second member 44 at an axial intermediate portion 24B3.
次に、本発明の第二実施形態の作用及び効果について説明する。 Next, the operation and effect of the second embodiment of the present invention will be described.
この内接型遊星歯車減速機40によっても、インナギア22及びアウタギア24は、互いの噛合面22A,24Aの直径D1,D2及び歯22C,24Cの歯厚T1,T2が軸方向に変化しているので、インナギア22及びアウタギア24の軸方向のがたつきを抑制することができる。これにより、インナギア22とアウタギア24との噛み合いに伴って発生する振動を抑えることができる。しかも、噛合面22A,24Aの直径D1,D2及び歯22C,24Cの歯厚T1,T2が軸方向に変化しても、インナギア22の噛合面22Aとアウタギア24の噛合面24Aとの噛合状態が確保されているので(噛合面22A,24A同士が面接触するので)、単位面積あたりの衝撃が少なくなり、振動を更に抑えることができる。 Also with this inscribed planetary gear reducer 40, the inner gear 22 and the outer gear 24 have the diameters D1 and D2 of the meshing surfaces 22A and 24A and the tooth thicknesses T1 and T2 of the teeth 22C and 24C changed in the axial direction. Therefore, the shakiness of the inner gear 22 and the outer gear 24 in the axial direction can be suppressed. As a result, it is possible to suppress vibrations that occur due to the engagement between the inner gear 22 and the outer gear 24. Moreover, even if the diameters D1 and D2 of the meshing surfaces 22A and 24A and the tooth thicknesses T1 and T2 of the teeth 22C and 24C change in the axial direction, the meshing state between the meshing surface 22A of the inner gear 22 and the meshing surface 24A of the outer gear 24 is maintained. Since it is ensured (because the meshing surfaces 22A and 24A are in surface contact), the impact per unit area is reduced, and vibration can be further suppressed.
また、インナギア22及びアウタギア24は、噛合面22A,24Aの直径D1,D2が軸方向一端部22B1,24B1から中間部22B3,24B3に向けて徐々に増加すると共に軸方向中間部22B3,24B3から他端部22B2,24B2に向けて徐々に減少する構成である。また、インナギア22は、歯22Cの歯厚T1が軸方向一端部22B1から中間部22B3に向けて徐々に増加すると共に軸方向中間部22B3から他端部22B2に向けて徐々に減少し、アウタギア24は、歯24Cの歯厚T2が軸方向一端部24B1から中間部24B3に向けて徐々に減少すると共に軸方向中間部24B3から他端部24B2に向けて徐々に増加する構成である。従って、インナギア22及びアウタギア24の軸方向両側へのがたつきを抑制することができる。 Further, the inner gear 22 and the outer gear 24 are such that the diameters D1 and D2 of the meshing surfaces 22A and 24A gradually increase from the axial one end portions 22B1 and 24B1 toward the intermediate portions 22B3 and 24B3, and from the axial intermediate portions 22B3 and 24B3 to the other. It is the structure which decreases gradually toward edge part 22B2, 24B2. In the inner gear 22, the tooth thickness T1 of the teeth 22C gradually increases from the axial one end 22B1 toward the intermediate portion 22B3 and gradually decreases from the axial intermediate portion 22B3 toward the other end 22B2. The tooth thickness T2 of the tooth 24C gradually decreases from the axial one end 24B1 toward the intermediate portion 24B3 and gradually increases from the axial intermediate portion 24B3 toward the other end 24B2. Therefore, rattling of the inner gear 22 and the outer gear 24 on both sides in the axial direction can be suppressed.
[第三実施形態]
次に、本発明の第三実施形態について説明する。
[Third embodiment]
Next, a third embodiment of the present invention will be described.
本発明の第三実施形態では、上述の内接型遊星歯車減速機20(図2〜図5)に代えて、図9に示される内接型遊星歯車減速機50が用いられている。 In the third embodiment of the present invention, an inscribed planetary gear reducer 50 shown in FIG. 9 is used in place of the inscribed planetary gear reducer 20 (FIGS. 2 to 5) described above.
この内接型遊星歯車減速機50において、インナギア22及びアウタギア24は、噛合面22A,24Aの直径D1,D2が軸方向中間部22B3,24B3を境に異なっている。つまり、インナギア22における噛合面22Aの直径D1は、軸方向一端部22B1から中間部22B3までの方が軸方向中間部22B3から他端部22B2までよりも小さくなっている。同様に、アウタギア24における噛合面24Aの直径D2は、軸方向一端部24B1から中間部24B3までの方が軸方向中間部24B3から他端部24B2までよりも小さくなっている。 In the inscribed planetary gear speed reducer 50, the inner gear 22 and the outer gear 24 have different diameters D1 and D2 of the meshing surfaces 22A and 24A with respect to the axial intermediate portions 22B3 and 24B3. That is, the diameter D1 of the meshing surface 22A of the inner gear 22 is smaller from the axial one end portion 22B1 to the intermediate portion 22B3 than from the axial intermediate portion 22B3 to the other end portion 22B2. Similarly, the diameter D2 of the meshing surface 24A in the outer gear 24 is smaller from the axial one end 24B1 to the intermediate portion 24B3 than from the axial intermediate portion 24B3 to the other end 24B2.
なお、アウタギア24は、軸方向中間部24B3にて第一部材42及び第二部材44に分割されている。 The outer gear 24 is divided into a first member 42 and a second member 44 at the axial intermediate portion 24B3.
次に、本発明の第三実施形態の作用及び効果について説明する。 Next, the operation and effect of the third embodiment of the present invention will be described.
この内接型遊星歯車減速機20によっても、インナギア22及びアウタギア24は、互いの噛合面22A,24Aの直径D1,D2が軸方向に変化しているので、インナギア22及びアウタギア24の軸方向のがたつきを抑制することができる。これにより、インナギア22とアウタギア24との噛み合いに伴って発生する振動を抑えることができる。しかも、噛合面22A,24Aの直径D1,D2が軸方向に変化しても、インナギア22の噛合面22Aとアウタギア24の噛合面24Aとの噛合状態が確保されているので(噛合面22A,24A同士が面接触するので)、単位面積あたりの衝撃が少なくなり、振動を更に抑えることができる。 Also with this inscribed planetary gear reducer 20, the inner gear 22 and the outer gear 24 have the diameters D1 and D2 of the meshing surfaces 22A and 24A of the inner gear 22 and the outer gear 24 changed in the axial direction. Shaking can be suppressed. As a result, it is possible to suppress vibrations that occur due to the engagement between the inner gear 22 and the outer gear 24. Moreover, even if the diameters D1 and D2 of the meshing surfaces 22A and 24A change in the axial direction, the meshing state between the meshing surface 22A of the inner gear 22 and the meshing surface 24A of the outer gear 24 is secured (meshing surfaces 22A and 24A). Since they are in surface contact with each other, the impact per unit area is reduced and vibration can be further suppressed.
また、インナギア22及びアウタギア24は、噛合面22A,24Aの直径D1,D2が軸方向中間部22B3,24B3を境に異なるという簡単な構成であるので、インナギア22及びアウタギア24を容易に製造することができる。 Further, since the inner gear 22 and the outer gear 24 have a simple configuration in which the diameters D1 and D2 of the meshing surfaces 22A and 24A are different from each other at the intermediate portions 22B3 and 24B3 in the axial direction, the inner gear 22 and the outer gear 24 can be easily manufactured. Can do.
なお、インナギア22及びアウタギア24は、歯22C,24Cの歯厚T1,T2が軸方向に均一でも良いが、歯22C,24Cの歯厚T1,T2が軸方向中間部22B3,24B3を境に異なっていても良い。このように構成されていても、インナギア22及びアウタギア24を容易に製造することができる。 In the inner gear 22 and the outer gear 24, the tooth thicknesses T1 and T2 of the teeth 22C and 24C may be uniform in the axial direction, but the tooth thicknesses T1 and T2 of the teeth 22C and 24C are different from each other at the axial intermediate portions 22B3 and 24B3. May be. Even if comprised in this way, the inner gear 22 and the outer gear 24 can be manufactured easily.
また、インナギア22及びアウタギア24は、噛合面22A,24Aの直径D1,D2が軸方向に均一とされた上で、歯22C,24Cの歯厚T1,T2が軸方向中間部22B3,24B3を境に異なっていても良い。 Further, in the inner gear 22 and the outer gear 24, the diameters D1 and D2 of the meshing surfaces 22A and 24A are made uniform in the axial direction, and the tooth thicknesses T1 and T2 of the teeth 22C and 24C are bounded by the axial intermediate portions 22B3 and 24B3. May be different.
また、インナギア22は、軸方向中間部22B3,24B3にて第一部材及び第二部材に分割されていても良い。 Further, the inner gear 22 may be divided into a first member and a second member at the axial intermediate portions 22B3 and 24B3.
以上、本発明の一実施形態について説明したが、本発明は、上記に限定されるものでなく、上記以外にも、その主旨を逸脱しない範囲内において種々変形して実施可能であることは勿論である。 Although one embodiment of the present invention has been described above, the present invention is not limited to the above, and other various modifications can be made without departing from the spirit of the present invention. It is.
10・・・歯車ポンプ、16・・・モータシャフト(入力軸)、20,40,50・・・内接型遊星歯車減速機、22・・・インナギア、24・・・アウタギア、22A,24A・・・噛合面、22C,24C・・・歯、26・・・スペーサ、28・・・ケーシング、30・・・カバー、32・・・圧力室、34・・・吸入ポート、36・・・吐出ポート、42・・・第一部材、44・・・第二部材 DESCRIPTION OF SYMBOLS 10 ... Gear pump, 16 ... Motor shaft (input shaft), 20, 40, 50 ... Inscribed planetary gear reducer, 22 ... Inner gear, 24 ... Outer gear, 22A, 24A ..Meshing surface, 22C, 24C ... teeth, 26 ... spacer, 28 ... casing, 30 ... cover, 32 ... pressure chamber, 34 ... suction port, 36 ... discharge Port, 42 ... first member, 44 ... second member
Claims (10)
前記インナギアが内接噛合するアウタギアと、
を備え、
前記インナギア及び前記アウタギアは、互いの噛合面の直径が軸方向に変化している、
内接型遊星歯車減速機。 An inner gear attached to the input shaft in an eccentric state and rotated eccentrically with the rotation of the input shaft;
An outer gear in which the inner gear meshes internally,
With
In the inner gear and the outer gear, the diameters of the meshing surfaces of each other change in the axial direction.
Inscribed planetary gear reducer.
前記インナギアが内接噛合するアウタギアと、
を備え、
前記インナギア及び前記アウタギアは、互いの噛合面に形成された歯の歯厚が軸方向に変化している、
内接型遊星歯車減速機。 An inner gear attached to the input shaft in an eccentric state and rotated eccentrically with the rotation of the input shaft;
An outer gear in which the inner gear meshes internally,
With
The inner gear and the outer gear have tooth thicknesses of teeth formed on the meshing surfaces of each other changed in the axial direction.
Inscribed planetary gear reducer.
前記インナギアが内接噛合するアウタギアと、
を備え、
前記インナギア及び前記アウタギアは、互いの噛合面の直径及び前記噛合面に形成された歯の歯厚が軸方向に変化している、
内接型遊星歯車減速機。 An inner gear attached to the input shaft in an eccentric state and rotated eccentrically with the rotation of the input shaft;
An outer gear in which the inner gear meshes internally,
With
In the inner gear and the outer gear, the diameter of each meshing surface and the thickness of teeth formed on the meshing surface are changed in the axial direction.
Inscribed planetary gear reducer.
請求項1又は請求項3に記載の内接型遊星歯車減速機。 In the inner gear and the outer gear, the diameter of the meshing surface gradually changes from one axial end to the other end.
The inscribed planetary gear reducer according to claim 1 or 3.
請求項1又は請求項3に記載の内接型遊星歯車減速機。 In the inner gear and the outer gear, the diameter of the meshing surface gradually increases from one axial end portion toward the intermediate portion and gradually decreases from the axial intermediate portion toward the other end portion.
The inscribed planetary gear reducer according to claim 1 or 3.
請求項1又は請求項3に記載の内接型遊星歯車減速機。 The inner gear and the outer gear have different diameters of the meshing surfaces at an axially intermediate portion,
The inscribed planetary gear reducer according to claim 1 or 3.
前記アウタギアは、前記噛合面に形成された歯の歯厚が軸方向一端部から他端部に向けて徐々に増加する、
請求項2又は請求項3に記載の内接型遊星歯車減速機。 In the inner gear, the tooth thickness of the teeth formed on the meshing surface gradually decreases from one end in the axial direction toward the other end,
In the outer gear, the tooth thickness of the teeth formed on the meshing surface gradually increases from one axial end to the other end.
The inscribed planetary gear reducer according to claim 2 or 3.
前記アウタギアは、前記噛合面に形成された歯の歯厚が軸方向一端部から中間部に向けて徐々に減少すると共に軸方向中間部から他端部に向けて徐々に増加する、
請求項2又は請求項3に記載の内接型遊星歯車減速機。 The inner gear, the tooth thickness of the teeth formed on the meshing surface gradually increases from one axial end portion toward the intermediate portion and gradually decreases from the axial intermediate portion toward the other end portion,
In the outer gear, the tooth thickness of the teeth formed on the meshing surface gradually decreases from one axial end portion toward the intermediate portion and gradually increases from the axial intermediate portion toward the other end portion.
The inscribed planetary gear reducer according to claim 2 or 3.
請求項2又は請求項3に記載の内接型遊星歯車減速機。 The inner gear and the outer gear have different tooth thicknesses of teeth formed on the meshing surface with an axial middle portion as a boundary,
The inscribed planetary gear reducer according to claim 2 or 3.
請求項1〜請求項9のいずれか一項に記載の内接型遊星歯車減速機を有すると共に、前記インナギア及び前記アウタギアの間の隙間が圧力室とされ、且つ、前記圧力室と連通される吸入ポート及び吐出ポートが形成されたポンプ部と、
を備えた歯車ポンプ。 A motor unit having a motor shaft as the input shaft;
The internal planetary gear reducer according to any one of claims 1 to 9, wherein a gap between the inner gear and the outer gear serves as a pressure chamber and communicates with the pressure chamber. A pump part formed with a suction port and a discharge port;
Gear pump with
Priority Applications (1)
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JP2011056750A JP2012193769A (en) | 2011-03-15 | 2011-03-15 | Inscribed planetary reduction gear and gear pump |
Applications Claiming Priority (1)
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JP2011056750A JP2012193769A (en) | 2011-03-15 | 2011-03-15 | Inscribed planetary reduction gear and gear pump |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2016017507A (en) * | 2014-07-11 | 2016-02-01 | アイシン精機株式会社 | Oil pump |
JP2016075221A (en) * | 2014-10-07 | 2016-05-12 | 日本電産サンキョー株式会社 | Gear pump |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0579463A (en) * | 1991-07-08 | 1993-03-30 | Mitsubishi Materials Corp | Internal gear type fluid pressure device |
JP2000027769A (en) * | 1998-07-08 | 2000-01-25 | Unisia Jecs Corp | Internal gear pump or motor, and manufacture thereof |
JP2001323966A (en) * | 2000-05-12 | 2001-11-22 | Fuji Xerox Co Ltd | Torque transmitting mechanism |
JP2007218128A (en) * | 2006-02-15 | 2007-08-30 | Toyota Industries Corp | Gear pump |
EP1930595A2 (en) * | 2006-12-01 | 2008-06-11 | Robert Bosch Gmbh | Conveying unit |
-
2011
- 2011-03-15 JP JP2011056750A patent/JP2012193769A/en active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0579463A (en) * | 1991-07-08 | 1993-03-30 | Mitsubishi Materials Corp | Internal gear type fluid pressure device |
JP2000027769A (en) * | 1998-07-08 | 2000-01-25 | Unisia Jecs Corp | Internal gear pump or motor, and manufacture thereof |
JP2001323966A (en) * | 2000-05-12 | 2001-11-22 | Fuji Xerox Co Ltd | Torque transmitting mechanism |
JP2007218128A (en) * | 2006-02-15 | 2007-08-30 | Toyota Industries Corp | Gear pump |
EP1930595A2 (en) * | 2006-12-01 | 2008-06-11 | Robert Bosch Gmbh | Conveying unit |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2016017507A (en) * | 2014-07-11 | 2016-02-01 | アイシン精機株式会社 | Oil pump |
JP2016075221A (en) * | 2014-10-07 | 2016-05-12 | 日本電産サンキョー株式会社 | Gear pump |
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