WO2016056103A1 - 内接歯車ポンプ - Google Patents
内接歯車ポンプ Download PDFInfo
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- WO2016056103A1 WO2016056103A1 PCT/JP2014/077073 JP2014077073W WO2016056103A1 WO 2016056103 A1 WO2016056103 A1 WO 2016056103A1 JP 2014077073 W JP2014077073 W JP 2014077073W WO 2016056103 A1 WO2016056103 A1 WO 2016056103A1
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- teeth
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- tooth
- internal gear
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Classifications
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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
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/10—Rotary-piston machines or engines 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
- F01C1/103—Rotary-piston machines or engines 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
-
- 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
- F04C2240/00—Components
- F04C2240/20—Rotors
-
- 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
Definitions
- the external gear is eccentrically accommodated inside the internal gear so that the internal teeth of the internal gear and the external teeth of the external gear are in meshed with each other, and the number of teeth of the internal teeth is the number of teeth of the external teeth. More than one 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 toothed gear is eccentrically housed inside the internal gear, the internal gear is rotated by the rotational drive of the external gear, the liquid is sucked from the suction port, and the maximum volume formed by the external teeth and the internal teeth It discharges from a discharge port through space.
- a tooth base part is formed with a hypocycloid curve
- a tooth tip part is formed with an epicycloid curve
- a meshing part between a tooth tip part and a tooth bottom part is formed with an involute curve.
- the internal teeth of the internal gear are formed by envelopes of the respective tooth profile curves of the external teeth.
- the involute curve is not related to the amount of eccentricity between the external gear and the internal gear, and there is a degree of freedom in setting the amount of eccentricity, and the amount of eccentricity is increased to enable a large discharge amount.
- the gap between the outer teeth and the inner teeth is minimized on the maximum volume space side and the deepest engagement portion side where the outer teeth and the inner teeth are engaged most deeply, and between the maximum volume space and the deepest engagement portion.
- the clearance between the external teeth and the internal teeth can be set large on the suction port side and the discharge port side, and the mechanical efficiency is improved by avoiding contact between the external teeth and the internal teeth on all the teeth on the entire circumference. Yes.
- the external teeth are formed by a hypocycloid curve at the root, an epicycloid curve at the tip, and an involute curve at the meshing portion. Will mesh with three different curves and move between discontinuous curves. In this case, due to fluctuations in the load or movement due to the gap between the internal gear and the housing, the meshing between the internal teeth and the external teeth is disturbed, and noise is easily generated.
- the present invention is an internal gear pump, A ring-like internal gear having internal teeth, and an external gear having external teeth that are in mesh with the internal teeth of the internal gear and arranged eccentrically inside the internal gear,
- the internal gear pump in which the number of teeth of the internal teeth is one more than that, either one of the external teeth and the internal teeth is formed by forming a tooth tip portion and a meshing portion with one continuous curvature curve. This curve is formed by the equations (1) to (5) in which the apex of the tooth tip is the maximum curvature and the curvature gradually decreases toward the tooth bottom.
- either one of the external tooth and the internal tooth is formed by one continuous curvature curve of the tooth tip portion and the meshing portion, and this curve has a maximum curvature at the top of the tooth tip, Gradually decrease the curvature toward.
- the envelope curve created by the curve that forms the tooth tip portion and the meshing portion is a curved portion that intersects between the tooth tip portion and the meshing portion. It is possible to avoid contact with all the teeth, and the advantage of improving the mechanical efficiency is not impaired.
- the tooth tip part and the meshing part are formed with a curve with one continuous curvature, the top of the tooth tip being the maximum curvature, and gradually decreasing the curvature toward the root, from the meshing part to the tooth tip part It is possible to suppress the meshing speed from fluctuating discontinuously. As a result, even if there is a disturbance in the meshing between the internal teeth and the external teeth due to load fluctuations or movement due to the gap between the internal gear and the housing, the meshing between the internal teeth and the external teeth Transitions smoothly and noise generation can be reduced.
- FIG. 2 is a schematic diagram of a tooth profile according to Formula 1.
- FIG. 2-5 is a schematic diagram of the envelope curve L1 created by the curve L which forms the tooth tip part and meshing part of one Embodiment.
- a ring-shaped internal gear 1 has 16 internal teeth 1 ⁇ / b> A, and is housed in a housing 2 so as to be rotatable about a rotation center H.
- the external gear 3 has 15 external teeth 3A that are in mesh with the internal teeth 1A.
- the external gear 3 is accommodated in the internal gear 1 so as to be rotatable about a rotation center H1 that is eccentric from the rotation center H. Yes.
- the eccentricity E1 between the internal gear 1 and the external gear 3 is a dimension (distance) between the rotation center H of the internal gear 1 and the rotation center H1 of the external gear 3.
- the drive shaft 4 is a drive shaft that rotationally drives the external gear 3, and engages with the external gear 3.
- a suction port 5 for sucking oil and a discharge port 6 for discharging oil are formed in the housing 2 so as to be provided at symmetrical positions with a straight line passing through the rotation centers H and H1 as symmetry axes.
- FIG. 2 shows details of tooth profile shapes of the internal teeth 1 ⁇ / b> A of the internal gear 1 and the external teeth 3 ⁇ / b> A of the external gear 3.
- the internal tooth 1A is formed of a tooth tip portion 7A, a meshing portion 7B, a connecting portion 7C, and a tooth bottom portion 7D from the tooth tip to the tooth bottom, and these constitute the left half from the vertex a of the tooth tip.
- the right half from the apex a of the tooth tip is formed symmetrically with the left half, with the straight line passing through the center H of the internal gear 1 and the apex a as the axis of symmetry.
- the tooth tip portion 7A and the meshing portion 7B are formed by a curve L having the vertex a as the maximum curvature and gradually decreasing the curvature toward the tooth bottom.
- the curve L is formed by a curve connecting the points ab.
- the curve L is obtained by the following equations (1) to (5).
- FIG. 3 shows a schematic diagram of a tooth profile according to Formula 1.
- FIG. 3 shows the radius r of the curve L on the vertical axis, the parametric variable ⁇ on the horizontal axis, and r changing from ro-dr to ro as ⁇ changes from 0 to ⁇ / 2. Show.
- FIG. 4 shows a schematic diagram of the tooth profile according to equations 2 to 5.
- FIG. 4 shows the X and Y coordinates of the orbit center P of radius r forming the curve L (see also FIG. 2) and the X and Y coordinates of the point Q on the curve L generated by the orbit center P as parameters. It is shown that it changes according to ⁇ .
- the tooth bottom portion 7D forms an arc of radius R1 having a center 7E, and is formed by an arc connecting points cd among the arcs.
- the arc of radius R1 is formed as an arc that is slightly larger than the envelope curve created by the tooth tip portion 8A of the external gear 3A described later.
- the center 7E is located on a line passing through the rotation center H of the internal gear 1 and the circumferential center of the tooth bottom portion 7B.
- the connecting portion 7C is formed by an arc having a radius R3 having a smaller diameter than the radius R1 and a center 7F. Specifically, of the arcs, the arc connecting the points bd is the connecting portion 7C.
- the external tooth 3A includes a tooth tip portion 8A, a connection portion 8B, a meshing portion 8C, and a tooth bottom portion 8D.
- the tooth tip portion 8A, the meshing portion 8C, and the tooth bottom portion 8D are formed by an envelope curve L1 created by a curve L that forms the tooth tip portion 7A and the meshing portion 7B of the internal tooth 1A.
- the tooth tip portion 8A is configured by a portion corresponding to the point CD in the envelope curve L1
- the meshing portion 8C and the tooth bottom portion 8D are configured by a portion corresponding to the point AB in the envelope curve L1.
- the connecting portion 8B is a portion that rounds and connects between the tooth tip portion 8A and the meshing portion 8C, and is formed by an arc having a radius R4. Specifically, it is constituted by a portion corresponding to between the points BD in an arc having a radius R4.
- FIG. 5 the schematic diagram of the envelope curve L1 created by the curve L which forms the tooth tip part 7A and the meshing part 7B of the internal tooth 1A is shown.
- the envelope curve L1 is an intersecting curved portion 8E between the tooth tip portion 8A and the meshing portion 8C, and this location is not created as a tooth profile.
- the above-mentioned connection part 8B is formed by rounding the location of the curved part 8E.
- the inner tooth 1A is formed by a curved line L having a continuous curvature of the tooth tip portion 7A and the meshing portion 7B.
- the curve L has a maximum curvature at the vertex a of the tooth tip and gradually decreases toward the tooth bottom. did.
- an envelope curve L1 that is created by a curve L that forms the tooth tip portion 7A and the meshing portion 7B of the inner tooth 1A, and that forms the tooth tip portion 8A, the meshing portion 8C, and the tooth bottom portion 8D of the external tooth 3A is Since the curved portion 8E intersects between the tooth tip portion 8A and the meshing portion 8C, it can be avoided that the outer teeth 3A and the inner teeth 1A are in contact with all the teeth on the entire circumference.
- the tooth tip portion 7A and the meshing portion 7B are formed with a curve L that has one continuous curvature, the vertex a of the tooth tip is the maximum curvature, and gradually decreases toward the tooth bottom, the meshing portion 7B. Therefore, it is possible to suppress the meshing speed from changing discontinuously in the tooth tip portion 7A. For this reason, even if a disturbance occurs in the engagement between the internal teeth 1A and the external teeth 3A due to load fluctuations or movement due to the gap between the internal gear 1A and the housing 2, the internal teeth 1A and the external teeth 1A The meshing with the teeth 3A is smoothly changed, and the generation of noise can be reduced.
- the inner tooth 1A is formed by a curve L in which the tip portion a and the meshing portion 7B have a maximum curvature at the apex a of the tooth tip and gradually reduce the curvature toward the tooth bottom.
- the tooth tip portion 8A, the meshing portion 8C, and the tooth bottom portion 8D are formed by the envelope curve L1 created by the curve L.
- the tooth tip portion and the meshing portion of the external tooth 3A are connected to the tooth tip. Is formed with a curve that gradually decreases the curvature toward the tooth bottom, and the tooth tip portion, the meshing portion, and the tooth bottom portion of the inner tooth 1A are respectively connected to the tooth tip portion and the meshing portion of the outer tooth 3A.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
内歯を有するリング状の内歯歯車と、内歯歯車の内歯と内接噛み合いする外歯を有し内歯歯車の内部に偏心して配置される外歯歯車とを収容し、前記外歯よりも前記内歯の歯数が1枚多い内接歯車ポンプにおいて、前記外歯と前記内歯とのいずれか一方は、歯先部と噛合部とを一つの連続した曲率の曲線で形成し、この曲線は、歯先の頂点を最大曲率とし、歯底に向けて漸次曲率を小さくする式(1)から(5)で形成されることを特徴とする。
Px=(ro-dr)+1/4dr{1-cos(2θ)} 式(2)
Py=1/4dr{-2θ+sin(2θ)} 式(3)
Qx=Px-r・cosθ 式(4)
Qy=Py+r・sinθ 式(5)
但し、
rは曲線の半径、
roは基準径、
drは変分量、
θは媒介変数、
Pxは軌道中心のX座標、
Pyは軌道中心のY座標、
Qxは軌道中心(Px,Py)により生成される曲線上の点のX座標、
Qyは軌道中心(Px,Py)により生成される曲線上の点のY座標、
である。
1A:内歯
3:外歯歯車
3A:外歯
7A、8A:歯先部
7B、8C:噛合部
L:曲線
図1において、リング状の内歯歯車1は、16枚の内歯1Aを有し、回転中心Hを中心として回転自在にハウジング2に収容されている。外歯歯車3は、内歯1Aと内接噛み合いする15枚の外歯3Aを有し、内歯歯車1の内部に、回転中心Hと偏心した回転中心H1を中心として回転自在に収容されている。内歯歯車1と外歯歯車3との偏心量E1は、内歯歯車1の回転中心Hと外歯歯車3の回転中心H1との間の寸法(距離)である。駆動軸4は、外歯歯車3を回転駆動する駆動軸であり、外歯歯車3に係合する。油を吸入する吸入ポート5、油を吐出する吐出ポート6が、回転中心H、H1を通る直線を対称軸として対称な位置に設けられるように、ハウジング2に穿設されている。
内歯1Aは、歯先から歯底に向けて、歯先部7Aと噛合部7Bと接続部7Cと歯底部7Dとで形成され、これらにより歯先の頂点aから左半分が構成されている。歯先の頂点aから右半分は、内歯歯車1の中心Hと頂点aとを通る直線を対称軸とし、左半分と対称形状に形成されている。歯先部7Aと噛合部7Bとは、頂点aを最大曲率とし、歯底に向けて漸次曲率を小さくする曲線Lで形成される。具体的には、曲線Lのうち、点ab間を結ぶ曲線で形成される。曲線Lは以下の式(1)~(5)で求める。
Px=(ro-dr)+1/4dr{1-cos(2θ)} 式(2)
Py=1/4dr{-2θ+sin(2θ)} 式(3)
Qx=Px-r・cosθ 式(4)
Qy=Py+r・sinθ 式(5)
但し、
rは曲線の半径、
roは基準径、
drは変分量、
θは媒介変数、
Pxは軌道中心のX座標、
Pyは軌道中心のY座標、
Qxは軌道中心(Px,Py)により生成される曲線上の点のX座標、
Qyは軌道中心(Px,Py)により生成される曲線上の点のY座標、
である。
包絡曲線L1は、歯先部8Aと噛合部8Cとの間においては、交差した曲線部8Eとなり、この箇所は歯形として創生されない。そして、曲線部8Eの箇所を丸めて前述の接続部8Bを形成している。
駆動軸4により外歯歯車3を回転方向Aに回転駆動すると、外歯歯車3と内接噛み合いする内歯歯車1が回転駆動され、吸入ポート5より吸入された油が吐出ポート6より吐出される。
Claims (1)
- 内歯を有するリング状の内歯歯車と、内歯歯車の内歯と内接噛み合いする外歯を有し内歯歯車の内部に偏心して配置される外歯歯車とを収容し、前記外歯よりも前記内歯の歯数が1枚多い内接歯車ポンプにおいて、
前記外歯と前記内歯とのいずれか一方は、歯先部と噛合部とを一つの連続した曲率の曲線で形成し、この曲線は、歯先の頂点を最大曲率とし、歯底に向けて漸次曲率を小さくする式(1)から(5)で形成されることを特徴とする内接歯車ポンプ。
r=ro-dr・cosθ 式(1)
Px=(ro-dr)+1/4dr{1-cos(2θ)} 式(2)
Py=1/4dr{-2θ+sin(2θ)} 式(3)
Qx=Px-r・cosθ 式(4)
Qy=Py+r・sinθ 式(5)
但し、
rは曲線の半径、
roは基準径、
drは変分量、
θは媒介変数、
Pxは軌道中心のX座標、
Pyは軌道中心のY座標、
Qxは軌道中心(Px,Py)により生成される曲線上の点のX座標、
Qyは軌道中心(Px,Py)により生成される曲線上の点のY座標、
である。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2014/077073 WO2016056103A1 (ja) | 2014-10-09 | 2014-10-09 | 内接歯車ポンプ |
CN201480081354.1A CN106605065B (zh) | 2014-10-09 | 2014-10-09 | 内齿轮泵 |
US15/505,166 US10066620B2 (en) | 2014-10-09 | 2014-10-09 | Internal gear pump |
EP14903766.5A EP3205880B1 (en) | 2014-10-09 | 2014-10-09 | Internal gear pump |
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PCT/JP2014/077073 WO2016056103A1 (ja) | 2014-10-09 | 2014-10-09 | 内接歯車ポンプ |
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EP (1) | EP3205880B1 (ja) |
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WO (1) | WO2016056103A1 (ja) |
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JP2014206071A (ja) * | 2013-04-11 | 2014-10-30 | 豊興工業株式会社 | 内接歯車ポンプ |
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2014
- 2014-10-09 EP EP14903766.5A patent/EP3205880B1/en active Active
- 2014-10-09 CN CN201480081354.1A patent/CN106605065B/zh active Active
- 2014-10-09 US US15/505,166 patent/US10066620B2/en active Active
- 2014-10-09 WO PCT/JP2014/077073 patent/WO2016056103A1/ja active Application Filing
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US10066620B2 (en) | 2018-09-04 |
EP3205880A4 (en) | 2018-04-04 |
EP3205880A1 (en) | 2017-08-16 |
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