WO2013054412A1 - 燃料ポンプ - Google Patents
燃料ポンプ Download PDFInfo
- Publication number
- WO2013054412A1 WO2013054412A1 PCT/JP2011/073514 JP2011073514W WO2013054412A1 WO 2013054412 A1 WO2013054412 A1 WO 2013054412A1 JP 2011073514 W JP2011073514 W JP 2011073514W WO 2013054412 A1 WO2013054412 A1 WO 2013054412A1
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- WIPO (PCT)
- Prior art keywords
- impeller
- pump
- fuel
- casing
- groove
- Prior art date
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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
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/086—Sealings especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/02—Selection of particular materials
- F04D29/026—Selection of particular materials especially adapted for liquid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/188—Rotors specially for regenerative pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/40—Organic materials
- F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
Definitions
- the present invention relates to a fuel pump, and more particularly, to a fuel pump having an impeller and a pump casing that rotatably accommodates the impeller.
- a fuel pump is known as a device for supplying fuel in a fuel tank to an internal combustion engine (for example, an automobile engine or the like).
- This type of fuel pump usually has a pump portion.
- the pump unit includes a casing and a substantially disk-shaped impeller that is rotatably accommodated in the casing.
- a blade groove portion is formed in an annular shape along the outer peripheral portion of the impeller on the surface of the impeller facing the fuel suction side.
- a blade groove portion is formed on the surface of the impeller facing the fuel discharge side at a position corresponding to the blade groove portion formed on the suction side.
- the blade groove portions formed on the suction side surface and the discharge side surface of the impeller communicate with each other at the bottom portion.
- Each of the inner surface of the casing facing the intake side and the discharge side of the impeller is formed with a pump passage extending from the upstream end to the downstream end along the rotation direction of the impeller in a region facing the blade groove formed in the impeller. Yes.
- the upstream end of the suction-side pump passage communicates with the outside of the casing through a fuel suction port, and the downstream end of the discharge-side pump passage communicates with the outside of the casing through a fuel discharge port.
- the fuel pump configured as described above, when the impeller rotates, fuel is sucked into the pump casing from the suction port, and the sucked fuel is introduced into the impeller blade groove and the pump passage. Centrifugal force due to the rotation of the impeller acts on the fuel sucked into the pump casing. The fuel sucked into the pump casing flows downstream along the pump passage while being pressurized by the centrifugal force of the impeller, and is discharged out of the pump casing from the discharge port.
- the thrust direction In such a fuel pump, in order to prevent reduction in pump discharge efficiency due to leakage loss, which occurs in the gap between the impeller surface and the pump cover and pump base sliding surface in contact with the impeller surface, the thrust direction The gap is very small.
- the present invention has been made in view of the above-described circumstances, and has a simple and inexpensive configuration, prevents the occurrence of problems such as an increase in the rotational resistance of the impeller and the lock of the pump chamber, and ensures reliability and pump performance. It aims at providing the fuel pump which made maintenance compatible.
- a fuel pump according to the present invention is a fuel pump comprising a disk-shaped impeller, a casing including a pump cover and a pump body that rotatably accommodates the impeller, and a motor unit that rotationally drives the impeller.
- Each of the front and back surfaces of the impeller is formed with a recess group that repeats in the circumferential direction in a region extending in the circumferential direction at a predetermined distance from the outer periphery to the inner side, and the pump cover facing the impeller surface has an impeller A first groove extending from the upstream end to the downstream end is formed in a region facing the recess group of the pump, and the pump body facing the impeller back surface has a region facing the recess group of the impeller downstream from the upstream end.
- a second groove extending to the end is formed, and the casing has a fuel discharge port that communicates the vicinity of the downstream end of the first groove and the outside of the casing, and an upstream of the second groove.
- a fuel inlet that communicates the vicinity with the outside of the casing is formed, and when viewed in the rotation direction of the impeller, between the upstream end and the downstream end of the first groove of the pump cover, and the upstream end and the downstream of the pump body
- the swelling amount of the recess group of the impeller is predicted at a position facing the recess group of the impeller of at least one seal portion of the casing.
- a concave shape of micron order is formed.
- the fuel pump of the present invention with a simple and inexpensive configuration, it is possible to prevent the occurrence of problems such as an increase in the rotational resistance of the impeller and the lock of the pump chamber, thereby ensuring both reliability and maintaining pump performance.
- a fuel pump can be obtained.
- FIG. 1 is a longitudinal sectional view showing the overall configuration of a fuel pump according to Embodiment 1 of the present invention.
- FIG. 2 is an enlarged longitudinal sectional view of a pump part in FIG. 1 is a plan view of an impeller according to Embodiment 1 of the present invention.
- FIG. 3 is a plan view of the pump body according to the first embodiment of the present invention as viewed from the impeller side.
- FIG. 3 is a plan view of the pump cover according to the first embodiment of the present invention viewed from the impeller side. It is a fragmentary sectional view of pump part 12 in Embodiment 1 of this invention.
- Embodiment 1 FIG. Embodiment 1 of the present invention will be described with reference to FIGS.
- symbol shall show the same or an equivalent part.
- FIG. 1 is a longitudinal sectional view showing the overall configuration of the fuel pump according to the first embodiment of the present invention.
- the fuel pump 10 includes a motor unit 70 and a pump unit 12.
- the motor unit 70 includes a housing 72, a motor cover 73, magnets 74 and 75, and a rotor 76.
- the housing 72 is formed in a substantially cylindrical shape.
- the motor cover 73 is fixed to the housing 72 by caulking the upper end 72a of the housing 72 (the upper and lower sides in FIG. 1 are the upper and lower sides of the fuel pump 10) inward.
- the motor cover 73 is formed with a discharge port 73a that opens upward.
- Magnets 74 and 75 are fixed to the inner wall of housing 72.
- the rotor 76 has a main body 77 composed of a laminated iron core and coils, and a shaft 78 that penetrates the main body 77 up and down.
- An upper end portion 78 a of the shaft 78 is rotatably attached to the motor cover 73 via a bearing 81.
- a lower end portion 78 b of the shaft 78 is rotatably attached to the pump cover 14 of the pump portion 12 via a bearing 82.
- the motor unit 70 has the same configuration as that of the conventional fuel pump, further detailed description thereof is omitted.
- FIG. 2 shows an enlarged view of the pump portion of FIG.
- the pump unit 12 includes a casing 18 and an impeller 20.
- the impeller 20 has a substantially disk shape.
- a first blade groove group 20b that is continuous in the circumferential direction is formed in an annular shape with a predetermined distance from the outer peripheral surface 20e. That is, the first blade groove group 20 b is separated from the outer peripheral surface 20 e of the impeller 20 by the outer peripheral wall 20 d of the impeller 20.
- the surface on the fuel discharge side of the impeller 20 is circumferentially positioned at a position corresponding to the first blade groove group 20b formed on the suction side surface of the impeller 20 (that is, a region separated from the outer peripheral surface 20e by a predetermined distance).
- a continuous second blade groove group 20c is formed in an annular shape.
- the bottom part of the 1st blade groove group 20b and the bottom part of the 2nd blade groove group 20c are connected by the communication hole (illustration omitted).
- an engagement hole 20a having a substantially D-shaped cross section perpendicular to the axis passing through in the thickness direction is formed.
- a shaft 78 is engaged with the engagement hole 20a. When the coil of the rotor 77 is energized, the shaft 78 rotates and thereby the impeller 20 rotates.
- the casing 18 is a combination of the pump cover 14 and the pump body 16.
- the impeller side surface of the pump cover 14 (that is, the lower surface in FIG. 1) is formed with a circular recess 14 a in plan view.
- the diameter of the recess 14 a is substantially the same as the diameter of the impeller 20, and the depth of the recess 14 a is substantially the same as the thickness of the impeller 20.
- the impeller 20 is rotatably fitted in the recess 14a.
- a groove-shaped second pump passage 31 extending in the circumferential direction in a region facing the second blade groove group 20c of the impeller 20 is provided. Is formed.
- the upstream end 31a of the second pump passage 31 is formed in the vicinity of a position facing an upstream end 30a of the first pump passage 30 described later.
- a fuel discharge port 41 is formed at the downstream end 31 b of the second pump passage 31. The fuel discharge port 41 extends from the second pump passage 31 to the upper surface of the pump cover 14 (upper surface in FIG. 1), and communicates the second pump passage 31 with the outside of the casing 18 (specifically, inside the housing 72). ing.
- a slight axial gap A shown in FIG. 6 is formed between the impeller 20 and the recess 14 a of the pump cover 14, and between the impeller 20 and the inner peripheral surface 14 b of the recess 14 a of the pump cover 14. Is formed with a slight radial gap B shown in FIG. These gaps A and B are provided for the impeller 20 to rotate smoothly.
- the gap between the impeller 20 and the pump cover 14 is schematically shown wide, but in actuality, it is about several ⁇ m to several tens of ⁇ m.
- a groove-shaped first pump passage 30 extending in the circumferential direction in a region facing the first blade groove group 20 b of the impeller 20 is formed.
- a fuel inlet 40 is provided at the upstream end 30 a of the first pump passage 30.
- a vapor removal hole 30c penetrating the pump body 16 up and down (up and down in FIG. 1).
- a recess 16b is formed in the central portion of the pump body 16, and a thrust bearing 33 is disposed concentrically with the shaft 78 in the recess 16b. The thrust bearing 33 receives the thrust load of the rotor 76.
- the casing 18 including the pump cover 14 and the pump body 16 is fixed to the housing 72 by caulking the lower end 72b of the housing 72 inward with the impeller 20 assembled in the recess 14a of the pump cover 14.
- the lower end portion 78 b of the shaft 78 is inserted into the engagement hole 20 a of the impeller 20 at a portion further below the portion supported by the bearing 82.
- a thrust bearing 33 is interposed between the lower end of the shaft 78 and the pump body 16.
- the fuel in the fuel tank (not shown) is sucked into the casing 18 through the fuel inlet 40.
- the The fuel sucked into the casing 18 first flows into the upstream end 30 a of the first pump passage 30.
- the fuel that has flowed into the first pump passage 30 forms a swirl flow S between the first pump passage 30 and the first blade groove group 20b by the rotation of the impeller 20, and is boosted thereby.
- the fuel that has flowed into the first pump passage 30 flows through the first pump passage 30 from the upstream end 30a toward the downstream end 30b while being pressurized by the rotation of the impeller.
- the fuel discharged from the fuel discharge port 41 formed at the downstream end of the second pump passage 31 to the motor unit 70 flows through the motor unit 70 and is discharged from the discharge port 73a formed in the motor cover 73 to the fuel pump 10. It is discharged outside.
- the slight gap A in the axial direction shown in FIG. 6 is one of the factors that greatly influence the discharge performance of the fuel pump 10. That is, if the clearance is widened, the smooth flow of the swirl flow S is hindered, and at the same time, the leakage loss in the casing 18 increases, resulting in a decrease in the amount of fuel discharged from the fuel discharge port 41. cause. That is, maintaining and managing the clearance as small as possible is an extremely important issue in maintaining the discharge performance of the pump.
- the impeller 20 is formed of a thermosetting or thermoplastic resin material. As described above, since the impeller 20 is usually used in a state of being always immersed in fuel, a dimensional change (swelling) due to moisture absorption. Is known to happen.
- the amount of swelling in the blade portion 20f is large compared to other portions (planar portion, outer peripheral portion 20e).
- a concave shape that anticipates the amount of swelling is provided in advance in the portion of the casing 18 facing the impeller blade portion 20f on the sliding surface.
- the concave portions 35 and 36 on the order of microns that allow the impeller 20 to swell are formed in the seal portions provided between the upstream end 30a and the downstream end 30b of the pump passages 30 and 31, and between the upstream end 31a and the downstream end 31b. Establishing partial clearance expansion.
- the fuel pump of the first embodiment of the present invention configured as described above, even when the blade portion 20f swells, the occurrence of problems such as an increase in rotational resistance of the impeller 20 or a pump chamber lock is prevented. Can do. At the same time, since the area where the clearance is enlarged is limited to only the necessary area, the pump discharge performance is not greatly reduced.
- the concave shapes 35 and 36 formed on the inner surface of the casing 18 have been described as being formed on each of the pump body 16 and the pump cover 14, but can be formed only on one of them. .
- the concave shape is formed only in the pump body 16 and the pump cover 14 or the impeller 20, so that the other parts use conventional configurations (parts). It is something that can be done.
- the present invention is suitable as a fuel pump for supplying the fuel in the fuel tank to an internal combustion engine (for example, an automobile engine).
- an internal combustion engine for example, an automobile engine.
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Abstract
Description
インペラの吸入側面と吐出側面に対向するケーシング内面のそれぞれには、インペラに形成された羽根溝部と対向する領域を、インペラの回転方向に沿って上流端から下流端まで延びるポンプ通路が形成されている。吸入側のポンプ通路の上流端は、燃料吸入口によってケーシング外と連通されており、吐出側のポンプ通路の下流端は燃料吐出口によってケーシング外と連通されている。
このような燃料ポンプでは、インペラの表面と、これに接する、ポンプカバー、ポンプベースの摺動面との間の間隙で発生する、漏れ損失によるポンプの吐出効率の低下を防止するため、スラスト方向の間隙を非常に微小にしている。このため羽根溝の回転によりポンプ室内の燃料圧力が燃料吸入口からポンプ室出口に向けて上昇すると、インペラはポンプケーシングにあるポンプ室出口付近とポンプケーシングにある燃料吸入口付近との間の圧力アンバランスによって、ポンプケーシングにおけるポンプ室出口に対向する位置に接触しながら回転する。
そこで、この接触を防止するために、ポンプケーシングの摺動面のポンプ出口近傍に、インペラの表面とポンプケーシングとの間の微小間隙より大きい間隙を形成して、当り逃し部を形成することが知られている。(例えば、特許文献1参照。)
この発明の実施の形態1について、図1~図6を参照して説明する。
なお、各図中、同一符号は、同一または相当部分を示すものとする。
図1はこの発明の実施の形態1の燃料ポンプの全体構成を示す縦断面図であり、図1に示されるように、燃料ポンプ10は、モータ部70とポンプ部12とから構成されている。
モータ部70は、ハウジング72とモータカバー73とマグネット74、75と回転子76を備えている。ハウジング72は略円筒状に形成されている。モータカバー73は、ハウジング72の上端72a(図1の上下を燃料ポンプ10の上下とする)を内側にかしめることによってハウジング72に固定されている。モータカバー73には、上方に向かって開口している吐出ポート73aが形成されている。マグネット74、75は、ハウジング72の内壁に固定されている。回転子76は、積層鉄心とコイル等によって構成される本体77と、本体77を上下に貫くシャフト78を有している。シャフト78の上端部78aは、ベアリング81を介してモータカバー73に回転可能に装着されている。シャフト78の下端部78bは、ベアリング82を介してポンプ部12のポンプカバー14に回転可能に装着されている。ここで、モータ部70については、従来の燃料ポンプと同様の構成のため、これ以上の詳細な説明は省略する。
ポンプ部12は、ケーシング18とインペラ20を備えている。
図3に示すようにインペラ20は略円盤状である。インペラ20の燃料吸入側の面には、外周面20eから所定の距離を隔てて、周方向に連続する第1羽根溝群20bが環状に形成されている。すなわち、第1羽根溝群20bは、インペラ20の外周壁20dによってインペラ20の外周面20eから隔てられている。インペラ20の燃料吐出側の面には、インペラ20の吸入側面に形成される第1羽根溝群20bに対応する位置(すなわち、外周面20eから所定の距離を隔てた領域)に、周方向に連続する第2羽根溝群20cが環状に形成されている。なお、第1羽根溝群20bの底部と第2羽根溝群20cの底部は連通孔(図示省略)により連通されている。インペラ20の中心部には、厚さ方向に貫通する軸直角方向断面が略D字状の係合孔20aが形成されている。係合孔20aにはシャフト78が係合されている。回転子77のコイルに通電すると、シャフト78が回転し、これによってインペラ20が回転する。
凹部14aに、インペラ20が回転可能に嵌まり込んでいる。
第2ポンプ通路31の下流端31bには燃料吐出口41が形成されている。
燃料吐出口41は、第2ポンプ通路31からポンプカバー14の上面(図1の上面)まで伸びており、第2ポンプ通路31とケーシング18外(詳細には、ハウジング72内)とを連通している。
なお、図では、模式的にインペラ20とポンプカバー14の隙間を広く示しているが、実際には数μm~数十μm程度である。
スラストベアリング33は回転子76のスラスト荷重を受止める。
また、ケーシング18がハウジング72に固定された状態では、シャフト78の下端部78bは、ベアリング82に支持されている部位よりさらに下方の部位で、インペラ20の係合穴20aに嵌挿されている。シャフト78の下端とポンプボディ16の間にはスラストベアリング33が介装されている。
吸湿による膨潤量が軸方向に設けられたクリアランスAに近づいた場合、インペラとケーシングの干渉により回転運動が阻害されることで回転磨耗抵抗が増大し、燃料ポンプの吐出効率が低下を引き起こし、更に設定クリアランスAを超えてインペラ20が膨潤した場合、最悪のケースではポンプ室のロックに至る懸念がある。上記背景から、クリアランスは燃料浸漬によるインペラの膨潤を見込んだ上で、ロック等が発生しない程度に小さく設定・管理する必要がある。
具体的には、ポンプボディ16、およびポンプカバー14の摺動面上に設けられた略C字上のポンプ通路30、31に対し、それらを円周方向に延長する方向に沿って、換言すれば、ポンプ通路30、31の上流端30aと下流端30b、及び上流端31aと下流端31bの間に設けられるシール部に、インペラ20の膨潤量を見込んだミクロンオーダーの凹形状35、36を設け、部分的なクリアランスの拡大を行っている。
また、本明細書または図面に説明した技術要素は、単独であるいは各種の組合せによって技術的有用性を発揮するものであり、出願時の請求項記載の組合せに限定されるものではない。また、本明細書または図面に例示した技術は、複数目的を同時に達成するものであり、そのうちの一つの目的を達成すること自体で技術的有用性を持つものである。
18:ケーシング、20:インペラ、
20b:第1羽根溝群(凹所群)、
20c:第2羽根溝群(凹所群)、30、31:ポンプ通路、
30a:ポンプ通路30の上流端、30b:ポンプ通路30の下流端、
31a:ポンプ通路31の上流端、31b:ポンプ通路31の下流端、
35:凹形状(ポンプボディ側)、36:凹形状(ポンプカバー側)、
40:燃料吸入口、41:燃料吐出口、
50a、50b:凹形状(インペラ側)、
70:モータ部、72:ハウジング、73:モータカバー、
74、75:マグネット、
76:回転子、78:シャフト。
Claims (4)
- 円盤状のインペラ(20)と、そのインペラを回転可能に収容するポンプカバー(14)とポンプボディ(16)とからなるケーシング(18)、および、前記インペラを回転駆動するモータ部(70)とを備える燃料ポンプ(10)であって、
前記インペラ(20)の表裏両面のそれぞれには、外周から内側に所定の距離を隔てて周方向に伸びる領域に周方向に繰返す凹所群(20b、20c)が形成され、
前記インペラ表面に対向するポンプカバー(14)には、インペラの凹所群(20c)に対向する領域を上流端(31a)から下流端(31b)まで伸びている第1溝(31)が形成され、
前記インペラ裏面に対向するポンプボディ(16)には、インペラの凹所群(20b)に対向する領域を上流端(30a)から下流端(30b)まで伸びている第2溝(30)が形成され、
前記ケーシング(18)には、前記第1溝(31)の下流端(31b)近傍とケーシング(18)外とを連通する燃料吐出口(41)と、第2溝(30)の上流端(30a)近傍とケーシング(18)外とを連通する燃料吸入口(40)とが形成され、
前記インペラの回転方向に見て、前記ポンプカバー(14)の第1溝(31)の上流端と下流端の間、及び上記ポンプボディ(16)の上流端と下流端の間に、それぞれシール部が設けられている燃料ポンプにおいて、
前記ケーシング(18)の少なくとも一方のシール部の前記インペラの凹所群(20b、20c)に対向する位置に、前記インペラ(20)の凹所群(20b、20c)の膨潤量を予測したミクロンオーダーの凹形状(35、36)を形成したことを特徴とする燃料ポンプ。 - 前記ポンプカバー(14)およびポンプボディ(16)の双方に上記凹形状(35、36)を形成したことを特徴とする 請求項1に記載の燃料ポンプ。
- 前記インペラ(20)の凹所群(20b、20c)の形状を、該インペラの凹所群の膨潤量を予測した凹形状(50a、50b)としたことを特徴とする請求項1に記載の燃料ポンプ。
- 円盤状のインペラ(20)と、そのインペラを回転可能に収容するポンプカバー(14)とポンプボディ(16)とからなるケーシング(18)、および、前記インペラを回転駆動するモータ部(70)とを備える燃料ポンプ(10)であって、
前記インペラ(20)の表裏両面のそれぞれには、外周から内側に所定の距離を隔てて周方向に伸びる領域に周方向に繰返す凹所群(20b、20c)が形成され、
前記インペラ表面に対向するポンプカバー(14)には、インペラの凹所群(20c)に対向する領域を上流端(31a)から下流端(31b)まで伸びている第1溝(31)が形成され、
前記インペラ裏面に対向するポンプボディ(16)には、インペラの凹所群(20b)に対向する領域を上流端(30a)から下流端(30b)まで伸びている第2溝(30)が形成され、
前記ケーシング(18)には、前記第1溝(31)の下流端(31b)近傍とケーシング(18)外とを連通する燃料吐出口(41)と、第2溝(30)の上流端(30a)近傍とケーシング外(18)外とを連通する燃料吸入口(40)とが形成され、
前記インペラ回転方向に見て、前記ポンプカバー(14)の第1溝(31)の上流端と下流端の間、及び上記ポンプボディ(16)の上流端と下流端の間に、それぞれシール部が設けられている燃料ポンプにおいて、前記インペラ(20)の凹所群(20b、20c)の形状を、該インペラの凹所群の膨潤量を予測した凹形状(50a、50b)としたことを特徴とする燃料ポンプ。
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2011/073514 WO2013054412A1 (ja) | 2011-10-13 | 2011-10-13 | 燃料ポンプ |
KR1020147000527A KR20140021064A (ko) | 2011-10-13 | 2011-10-13 | 연료펌프 |
US14/232,119 US20140169960A1 (en) | 2011-10-13 | 2011-10-13 | Fuel pump |
JP2013538368A JP5653531B2 (ja) | 2011-10-13 | 2011-10-13 | 燃料ポンプ |
CN201180074162.4A CN104040180A (zh) | 2011-10-13 | 2011-10-13 | 燃料泵 |
DE112011105737.7T DE112011105737T5 (de) | 2011-10-13 | 2011-10-13 | Kraftstoffpumpe |
TW100149138A TWI464321B (zh) | 2011-10-13 | 2011-12-28 | 燃料泵 |
IN2439CHN2014 IN2014CN02439A (ja) | 2011-10-13 | 2014-04-01 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2011/073514 WO2013054412A1 (ja) | 2011-10-13 | 2011-10-13 | 燃料ポンプ |
Publications (1)
Publication Number | Publication Date |
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WO2013054412A1 true WO2013054412A1 (ja) | 2013-04-18 |
Family
ID=48081489
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2011/073514 WO2013054412A1 (ja) | 2011-10-13 | 2011-10-13 | 燃料ポンプ |
Country Status (8)
Country | Link |
---|---|
US (1) | US20140169960A1 (ja) |
JP (1) | JP5653531B2 (ja) |
KR (1) | KR20140021064A (ja) |
CN (1) | CN104040180A (ja) |
DE (1) | DE112011105737T5 (ja) |
IN (1) | IN2014CN02439A (ja) |
TW (1) | TWI464321B (ja) |
WO (1) | WO2013054412A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11371511B2 (en) | 2019-02-15 | 2022-06-28 | Toyota Jidosha Kabushiki Kaisha | Diagnostic apparatus for fuel pump |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
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CN106232976A (zh) * | 2013-12-27 | 2016-12-14 | 罗伯特博世有限公司 | 燃料分配单元 |
KR20180127842A (ko) * | 2017-05-22 | 2018-11-30 | 삼성전자주식회사 | 다중 캐리어 시스템에서 셀의 송신 전력 조절 방법 및 장치 |
EP3913228A4 (en) * | 2019-01-16 | 2022-10-26 | Mitsuba Corporation | NON-POSITIVE DISPLACEMENT TYPE PUMP AND LIQUID SUPPLY DEVICE |
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JPH0814184A (ja) * | 1994-06-30 | 1996-01-16 | Nippondenso Co Ltd | ウエスコポンプ |
JP2002168188A (ja) * | 2000-09-20 | 2002-06-14 | Mitsuba Corp | 再生式ポンプ |
JP2007211679A (ja) * | 2006-02-09 | 2007-08-23 | Mitsubishi Electric Corp | 円周流ポンプ |
JP2007247634A (ja) * | 2006-03-20 | 2007-09-27 | Aisan Ind Co Ltd | 燃料ポンプ |
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DE4243544C2 (de) * | 1992-12-22 | 2003-04-17 | Bosch Gmbh Robert | Kraftstofförderpumpe |
DE4318122C2 (de) * | 1993-06-01 | 2002-01-17 | Bosch Gmbh Robert | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeugs |
DE19634900A1 (de) * | 1996-08-29 | 1998-03-05 | Bosch Gmbh Robert | Strömungspumpe |
US6669437B2 (en) * | 2001-10-04 | 2003-12-30 | Visteon Global Technologies, Inc. | Regenerative fuel pump with leakage prevent grooves |
US6890144B2 (en) * | 2002-09-27 | 2005-05-10 | Visteon Global Technologies, Inc. | Low noise fuel pump design |
DE10348008A1 (de) * | 2003-10-15 | 2005-05-19 | Siemens Ag | Kraftstoffpumpe |
JP2007056705A (ja) * | 2005-08-22 | 2007-03-08 | Aisan Ind Co Ltd | 燃料ポンプ |
JP4889419B2 (ja) * | 2006-09-15 | 2012-03-07 | 愛三工業株式会社 | ウエスコポンプ |
JP4889432B2 (ja) * | 2006-10-06 | 2012-03-07 | 愛三工業株式会社 | 燃料ポンプ |
JP2010144609A (ja) * | 2008-12-18 | 2010-07-01 | Mitsubishi Electric Corp | 燃料ポンプ |
-
2011
- 2011-10-13 KR KR1020147000527A patent/KR20140021064A/ko not_active Application Discontinuation
- 2011-10-13 DE DE112011105737.7T patent/DE112011105737T5/de not_active Withdrawn
- 2011-10-13 CN CN201180074162.4A patent/CN104040180A/zh active Pending
- 2011-10-13 JP JP2013538368A patent/JP5653531B2/ja active Active
- 2011-10-13 US US14/232,119 patent/US20140169960A1/en not_active Abandoned
- 2011-10-13 WO PCT/JP2011/073514 patent/WO2013054412A1/ja active Application Filing
- 2011-12-28 TW TW100149138A patent/TWI464321B/zh not_active IP Right Cessation
-
2014
- 2014-04-01 IN IN2439CHN2014 patent/IN2014CN02439A/en unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH0814184A (ja) * | 1994-06-30 | 1996-01-16 | Nippondenso Co Ltd | ウエスコポンプ |
JP2002168188A (ja) * | 2000-09-20 | 2002-06-14 | Mitsuba Corp | 再生式ポンプ |
JP2007211679A (ja) * | 2006-02-09 | 2007-08-23 | Mitsubishi Electric Corp | 円周流ポンプ |
JP2007247634A (ja) * | 2006-03-20 | 2007-09-27 | Aisan Ind Co Ltd | 燃料ポンプ |
Cited By (1)
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US11371511B2 (en) | 2019-02-15 | 2022-06-28 | Toyota Jidosha Kabushiki Kaisha | Diagnostic apparatus for fuel pump |
Also Published As
Publication number | Publication date |
---|---|
TW201315894A (zh) | 2013-04-16 |
US20140169960A1 (en) | 2014-06-19 |
JP5653531B2 (ja) | 2015-01-14 |
IN2014CN02439A (ja) | 2015-08-07 |
CN104040180A (zh) | 2014-09-10 |
KR20140021064A (ko) | 2014-02-19 |
DE112011105737T5 (de) | 2014-07-31 |
JPWO2013054412A1 (ja) | 2015-03-30 |
TWI464321B (zh) | 2014-12-11 |
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