WO2006028243A1 - 燃料ポンプ - Google Patents
燃料ポンプ Download PDFInfo
- Publication number
- WO2006028243A1 WO2006028243A1 PCT/JP2005/016696 JP2005016696W WO2006028243A1 WO 2006028243 A1 WO2006028243 A1 WO 2006028243A1 JP 2005016696 W JP2005016696 W JP 2005016696W WO 2006028243 A1 WO2006028243 A1 WO 2006028243A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- impeller
- fuel
- suction port
- vortex
- fuel pump
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/08—Feeding by means of driven pumps electrically driven
-
- 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
-
- 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
- F04D5/007—Details of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2250/00—Geometry
- F05B2250/50—Inlet or outlet
- F05B2250/503—Inlet or outlet of regenerative pumps
Definitions
- the present invention belongs to the technical field of a fuel pump provided in a fuel tank of a vehicle.
- some of these types of fuel pumps are configured to include an outer partition wall in which a suction port is formed, an inner partition wall in which a discharge port is formed, and an impeller accommodated between the partition walls.
- an annular fuel flow path is formed on each partition wall on the surface facing the impeller at a position facing the blade body formed on the outer periphery of the impeller, and the fuel flow is formed in the outer partition wall.
- a suction port that communicates with the passage is formed, and a discharge port that communicates with the fuel flow path is formed on the inner partition wall, and in this way, the fuel pump is an in-tank type.
- the fuel flowing in from the suction port as the impeller rotates flows in along the cylindrical cylinder, so that the fuel flows as a vortex swirling along the circumferential surface of the cylinder. Therefore, there is a problem that a low-pressure part is formed at the center of the vortex and bubbles are easily generated, and the flow rate decreases as the temperature of the fuel increases (the flow rate of the high-temperature characteristics decreases).
- the outer end and the inner end of the suction port are formed so as to be offset, the generation of eddy currents is more remarkable, and improvement is strongly desired.
- the present invention has been created in order to solve these problems in view of the above circumstances, and the invention of claim 1 is characterized in that an outer partition wall in which a suction port is formed and a discharge port are formed.
- a ring-shaped fuel that communicates with the suction port and the discharge port at a portion facing the blade body on the outer periphery of the impeller of each partition wall.
- the intake port is provided with an eddy current blocking unit for blocking the inflowing fuel from becoming a vortex.
- the invention of claim 2 is the invention according to claim 1, wherein the eddy current blocking portion is provided on the front side in the rotation direction of the impeller at the suction port. By doing so, the rotation of the impeller is followed. Therefore, it is possible to effectively prevent vortex formation due to the flowing fuel.
- the eddy current blocking portion is constituted by a vortex flow blocking surface orthogonal to the rotation direction of the impeller. By doing so, the impeller can be rotated. It is possible to effectively prevent vortex formation due to the following fuel flow.
- the invention of claim 4 is any one of claims 1 to 3, wherein the outer end facing the outside of the suction port has a larger diameter than the inner end facing the impeller and is biased toward the inner diameter side. By doing so, it is possible to reduce the size of the fuel pump.
- the invention of claim 5 is the invention according to any one of claims 1 to 4, wherein the connecting portion from the suction port to the fuel flow path can be cut out in an inclined shape and / or a curved shape, By doing in this way, the notch part of the said connection part can be ensured large, without increasing the plate
- the invention of claim 6 is the invention according to claims 1 to 5, wherein the eddy current blocking portion extends to the rear side in the rotation direction of the impeller with respect to the eddy current blocking surface orthogonal to the rotation direction of the impeller and the vortex flow blocking surface It is composed of an arcuate guide surface. By doing so, it is possible to further prevent vortex formation.
- eddy currents are not formed, and not only generation of bubbles can be prevented, but also suction resistance can be prevented, and furthermore, the vortex center is prevented from being locally depressurized.
- suction resistance can be prevented, and furthermore, the vortex center is prevented from being locally depressurized.
- the fuel pump can be miniaturized. According to the invention of claim 5, it is possible to secure a large notch portion of the connecting portion without increasing the plate thickness of the outer partition wall, and to reduce a decrease in flow rate due to flow separation.
- the invention of claim 6 can further prevent vortex formation.
- FIGS. 1 (A), (B), (C) and (D) are a side view, a front view, a side view and a side view of the fuel pump with the end force par removed, respectively. It is.
- FIGS. 2 (A), (B), and (C) are a side view of the second plate, a sectional view taken along line XX in FIG. 2 (A), and a side view, respectively. ⁇
- FIG. 3 is an enlarged perspective view of the main part.
- FIG. 4 is a cross-sectional view of the main part.
- FIG. 5 is a table showing a change in the discharge amount with respect to a temperature change between the fuel pump of the present embodiment and the conventional fuel pump.
- FIG. 6 is an enlarged perspective view of the main part in the second embodiment.
- FIGS. 7 (A), (B), (C), and (D) are pattern diagrams of main parts in the third, fourth, fifth, and sixth embodiments, respectively.
- FIGS. 8 (A), (B), and (C) are cross-sectional views of the main parts in the seventh, eighth, and ninth embodiments, respectively.
- reference numeral 1 denotes a fuel pump disposed in a fuel tank.
- the fuel pump 1 includes a motor part M on one end side of a cylindrical casing 2 and a pump part P on the other end side.
- the motor shaft 3 of the motor part M is rotatably supported via a bearing 4a on a bracket 4 arranged so that one end thereof covers the cylindrical end on one end side of the casing 2.
- the other end portion 3a of the motor shaft 3 is arranged so as to cover the cylinder end on the other end side of the casing 2 as described later, and is rotated to the pump casing 5 constituting the pump portion P of the present invention. It is supported in such a way that it can freely move in the axial direction.
- Reference numeral 6 denotes a force par that covers the outer periphery of the casing 2, the bracket 4, and the pump casing 5.
- the capper 6 is caulked to the outer periphery of the force par 2, the placket 4, and the pump casing 5. It is set so that they are integrated by being fitted in a state where they are attached.
- Reference numeral 7 denotes an armature core that is integrally fitted to the motor shaft 3
- 8 is a permanent magnet fixed to the inner peripheral surface of the casing
- 4b is an end force par arranged so as to cover the placket 4.
- the pump casing 5 includes first and second plates 9 and 10 corresponding to the inner partition wall and the outer partition wall of the present invention.
- the first and second plates 9 and 10 are formed in a disc shape. Formed and arranged in parallel in the axial direction of the motor shaft 3.
- the other end 3 a of the motor shaft 3 is inserted into the through hole 9 a of the first plate 9 located on the inner side.
- the bearing 3 b is rotatably supported through the arranged bearing 3 b, and the penetrating tip is inserted into the recess 10 0 a of the second plate 10 located on the outside via the thrust bearing 3 c. It is supported.
- the motor shaft 3 is set so that the axial movement of the motor shaft 3 is restricted by the pump casing 5 and supported in a rotatable state.
- An impeller 11 is installed in a gap formed between the first and second plates 9 and 10 facing each other.
- the impeller 11 is a disc-shaped member set to a predetermined thickness.
- a motor shaft through hole 11a for externally fitting to the motor shaft 3 is formed at the center of the plate body (disk body).
- the chamfered portion 3d is formed in the other end 3c of the motor shaft, and when the impeller 11 is externally fitted to the other end 3a of the motor shaft, the impeller 11 is prevented from rotating around the motor shaft 3. And is configured to rotate integrally with the motor shaft 3.
- the impeller 11 is formed with a plurality of through-holes 1 lb penetrating in the plate thickness direction in the outer diameter portion in parallel with the circumferential direction, so that the outer diameter portion of the impeller 11 1 is formed in the outer diameter portion.
- a plurality of blade bodies 1 1 c arranged in the circumferential direction are formed between the adjacent through-holes 1 1 b, and are further integrated in the circumferential direction on the outer diameter side of these blade bodies 1 1 c.
- a ring-shaped part 1 1 d is formed.
- the impeller 11 of the first plate 9 serving as the inner partition wall is located on the interior side (outside and other end side) surface of the impeller blade body 1 1 c and on one end side.
- a recessed inner ring-shaped groove 9 b is formed.
- the second plate 10 serving as the outer partition wall it is located on the outer diameter side of the recessed portion 10 a forming portion, that is, on the portion facing the impeller blade body 11 c, and on the other end side.
- a concave outer ring-shaped groove 1 0 b is formed, and the inner ring-shaped groove 9 b and the outer ring-shaped groove 1 O b are impeller 1 when pump operation is performed by the impeller 1 1.
- a discharge port 9c facing in the axial direction communicating with the inner ring-shaped concave groove 9 is opened so as to communicate with the motor part M side (inside the casing 2).
- a suction port 12 communicating with the outer ring-shaped concave groove 10 b is provided on the outer diameter side of the second plate 10, and the present invention is implemented in the suction port 12.
- the suction port 12 is formed in a cylindrical body that protrudes outward from the outer surface of the second plate 10, and has a flange end 10 c facing the impeller and an outer end 12 facing the outside. a and is integrally formed with the second plate 10.
- the outer end 12 a of the suction port 12 is formed to have a larger diameter than the heel end 10 c and is formed to be offset toward the inner diameter side from the inner end 10 c.
- the opening shape of the heel side end 10 c is formed in a substantially square shape, the front side portion 10 d located on the front side with respect to the rotation direction of the impeller 11 1, the rear side located on the rear side Surrounded by the four sides of the side part 10 e, the inner diameter side part 10 f located on the inner diameter side with respect to the disc center of the second plate 10, and the outer diameter side part 10 g located on the outer diameter side It consists of a space.
- the portion located on the front side in the rotational direction of the impeller 11 1 is formed to be thick and the inner diameter side
- an eddy current blocking surface (vortex blocking portion) 1 2 b perpendicular to the rotation direction of the impeller 1 1 is formed, and the eddy current blocking surface 1 2 b is formed on the inner end side.
- the side portion 10 d it is formed in a state orthogonal to the plate surface of the second plate 10.
- the fuel flowing in from the outer end 1 2 a of the suction port 1 2 abuts against the eddy current blocking surface 1 2 b and is prevented from forming a vortex and becomes a vortex flow in the cylinder of the suction port 1 2. Is set to be prevented. Further, on the cylinder inner peripheral surface from the outer end 12a of the suction port 12 to the inner end 10c, the rear side part 10e, the inner diameter side part 10f, the outer diameter side part 10 Inclined surfaces 1 2 c, 1 2 d, and 1 2 e are formed between g and the outer end 1 2 a, respectively.
- the inner end tip side 10 d following the eddy current blocking surface 12 b and the outer ring-shaped recess 10 b serving as the fuel flow path are connected in a substantially orthogonal shape.
- the part is notched in a curved shape and formed in the R-shaped part 1 2 f.
- the vortex blocking surface 1 2 b is formed by increasing the thickness of the front portion of the impeller 11 1 in the rotational direction in the cylindrical portion constituting the suction port 1 2.
- the radius of curvature of the R-shaped part 12 f formed by chamfering the ring-shaped concave part 10 b is ensured to be large.
- the fuel to be swung in the clockwise direction is forced to change the flow direction by abutting against (contacting with) the eddy current blocking surface 1 2 b, thereby preventing the formation of the eddy current by the fuel. Therefore, it is set to prevent the generation of bubbles.
- the change in the fuel discharge flow rate with respect to the temperature change is measured.
- the results are shown in the table of Fig. 5.
- the conventional fuel pump has a structure in which the discharge flow rate decreases as the temperature of the fuel increases, and the fuel pump 1 of the present embodiment has a high discharge flow rate even when the temperature becomes high.
- the effect of the eddy current blocking surface 1 2 b formed at the suction port 1 2 can be confirmed without any decrease.
- the pump when the impeller 11 is rotated based on the drive of the motor unit M, as described above, the pump is operated so that the fuel flows from the outer end 1 2 a of the intake port 1 2 to the inner end. After 10 c, it flows into the pump chamber.
- the fuel flows in along the cylinder of the suction port 1 2
- the fuel flow is formed on the peripheral surface of the cylinder of the suction port 1 2 even if it tries to form a vortex along the rotation direction of the impeller 1 1. It is blocked by abutting against the eddy current blocking surface 1 2 b, so that not only is it possible to prevent the generation of bubbles due to low pressure in the vicinity of the suction port 10 c but also the prevention of suction resistance.
- local pressure reduction at the center of the vortex is prevented, and performance degradation due to flow rate reduction can be avoided.
- the vortex blocking surface 1 2 b is formed at the front side in the rotation direction of the impeller 1 1 at the suction port 1 2, so that the inflow follows the rotation of the impeller 1 1.
- the vortex blocking surface 1 2 b is a surface orthogonal to the impeller rotation direction, so that the flow direction is forced to be orthogonal to the fuel flow flowing into the suction port. Since the change is made, it becomes possible to effectively prevent eddy currents.
- the outer end 1 2 a of the suction port 12 has a larger diameter than the inner end lc, and the clamping force is provided with its forming position biased toward the inner diameter side. It is possible to reduce the diameter of the power par 6 and to secure a force squeeze margin of the force par 6 that can be caulked so that the pump part P and the motor part M are integrated.
- the outer end 1 2 a is offset with respect to the inner end 1 c, the generation of eddy current becomes more remarkable, but in this case, the eddy current blocking surface 1 2 b is formed. Therefore, vortex flow is prevented, and an excellent fuel pump capable of preventing vortex flow while realizing compactness can be obtained.
- the suction port 1 2 when forming the eddy current blocking surface 1 2 b, the suction port 1 2 is formed with a thick wall, so that the portion from the vortex flow blocking surface 1 2 b to the outer ring-shaped groove 10 b Is formed between the suction port 1 2 and the pump chamber so that the radius of curvature of the R-shaped portion can be secured large without increasing the plate thickness of the second plate 10. It is possible to secure a large area of the fuel introduction part and to prevent the fuel flow from being separated, and to further effectively suppress the decrease in the flow rate in the high temperature characteristics, and to obtain an excellent fuel pump.
- the present invention is not limited to the above-described embodiment, and may be the second embodiment shown in FIG.
- the fuel guide path 14 formed in communication with the suction port 1 3 a of the second plate (outer partition wall) 1 3 is a vortex blocking surface 14 4 a perpendicular to the impeller rotation direction.
- An arcuate guide surface 1 4 b extending in the rearward direction of the impeller is formed with respect to the eddy current blocking surface 1 4 a.
- the fuel that enters 4 flows toward the vortex blocking surface 1 4 a side along the guide surface 1 4 b, thereby further preventing the formation of vortex flow and reducing the generation of bubbles.
- the inner end and the outer end of the suction port are formed so as to be offset, but the opening center of the inner end (the center of the radial length of the impeller blade body) Position) and the suction port where the outer center of the cylinder is approximately the same position, the vortex flow can be prevented by swirling along the inner circumferential surface of the suction port by forming a vortex block. Therefore, the flow rate can be reduced in the high temperature characteristics.
- FIGS. 7 (A) to (D) may be employed.
- the radial plate-like body 15a that faces the rotation direction of the impeller from the cylinder center O of the suction port 15 is provided to prevent the vortex flow perpendicular to the vortex flow.
- Surface 15 b is formed, and the generation of eddy currents can be reduced by doing so.
- the suction ports 16 and 17 are circular, and the outer shape is circular, but the inner cylinder shape is a triangular shape whose top is located on the front side in the rotational direction of the impeller. Or, it is a quadrangular shape where the position side piece is located at the front side of the impeller in the rotational direction.
- the cylinder inner peripheral surface 18a of the suction port 18 can be an eddy current blocking portion constituted by a plurality of curved surfaces bulging toward the inner diameter side. Even with this configuration, eddy currents can be reduced.
- FIGS. 8 (A), (B), and (C) may be employed.
- the outer bulkhead 1 9, 2 Opening holes 19 a, 20 a, and 21 a penetrating in the plate thickness direction are formed in 0 and 21, respectively, while the outer partition walls 19, 20 and 21 are configured by integrally connecting the base end portions of cylindrical suction ports 22, 23 and 24 formed separately.
- the vortex flow blocking surfaces 22a, 23a, which are perpendicular to the rotation direction of the impeller 11 1 are arranged on the inner periphery of the front side of the impeller 11 1 in the suction ports 22, 23, 24. By forming 2a, the formation of vortex is prevented and the flow rate can be reduced in the high temperature characteristics.
- the fuel flow path 19b side is notched in the region from the suction port 22 (vortex blocking surface 22a) to the fuel flow path 19b of the outer partition wall 19.
- 24a is cut away to form curved R-shaped parts 23b and 24b, and fuel flow paths 20b and 21b are cut away to form inclined inclined surfaces 20c and 21c. Prevents a decrease in flow rate due to flow separation.
- the step portion 24 c is formed in the suction port 24 to shorten the length in the cylinder length direction on the fuel flow path 21 b side, and the inclined surface on the fuel flow path 21 b side.
- 21 c is configured to ensure a large amount, so that the volume of the portion from the vortex blocking surface 24 a to the fuel flow path 21 b increases to prevent further reduction in the flow rate. I have to. Industrial applicability
- the fuel pump according to the present invention is useful as a fuel pump or the like provided in a fuel tank of a vehicle, and in particular, the outer end and the inner end of the suction port that generate vortex flow are offset. It is suitable for fuel pumps that are formed in the same way, and when you want to make the fuel pump smaller and lighter.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006535861A JP4912149B2 (ja) | 2004-09-08 | 2005-09-06 | 燃料ポンプ |
DE112005002121.1T DE112005002121B4 (de) | 2004-09-08 | 2005-09-06 | Kraftstoffpumpe |
US11/661,928 US7828508B2 (en) | 2004-09-08 | 2005-09-06 | Fuel pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004260689 | 2004-09-08 | ||
JP2004-260689 | 2004-09-08 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006028243A1 true WO2006028243A1 (ja) | 2006-03-16 |
Family
ID=36036522
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/016696 WO2006028243A1 (ja) | 2004-09-08 | 2005-09-06 | 燃料ポンプ |
Country Status (4)
Country | Link |
---|---|
US (1) | US7828508B2 (ja) |
JP (1) | JP4912149B2 (ja) |
DE (1) | DE112005002121B4 (ja) |
WO (1) | WO2006028243A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012163099A (ja) * | 2011-02-04 | 2012-08-30 | Ti Group Automotive Systems Llc | インペラ及び流体ポンプ |
JP2015004354A (ja) * | 2013-06-24 | 2015-01-08 | 株式会社デンソー | 燃料ポンプ |
JPWO2020149382A1 (ja) * | 2019-01-16 | 2021-12-02 | 株式会社ミツバ | 非容積型ポンプ及び液体供給装置 |
CN114320936A (zh) * | 2021-12-28 | 2022-04-12 | 中国航空工业集团公司金城南京机电液压工程研究中心 | 一种具有火焰抑制的多作用排气装置 |
KR20220089059A (ko) * | 2020-12-21 | 2022-06-28 | (주)모토닉 | 터빈형 연료펌프 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11117890A (ja) * | 1997-10-16 | 1999-04-27 | Aisan Ind Co Ltd | フューエルポンプ |
JP2004011556A (ja) * | 2002-06-07 | 2004-01-15 | Hitachi Unisia Automotive Ltd | タービン型燃料ポンプ |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH073237B2 (ja) * | 1986-10-20 | 1995-01-18 | 株式会社ユニシアジェックス | タ−ビン型燃料ポンプ |
DE4343078B4 (de) * | 1993-12-16 | 2007-09-13 | Robert Bosch Gmbh | Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine |
JP3463356B2 (ja) * | 1994-06-30 | 2003-11-05 | 株式会社デンソー | ウエスコポンプ |
JP2003293880A (ja) * | 2002-03-29 | 2003-10-15 | Denso Corp | 燃料ポンプ |
-
2005
- 2005-09-06 DE DE112005002121.1T patent/DE112005002121B4/de not_active Expired - Fee Related
- 2005-09-06 US US11/661,928 patent/US7828508B2/en not_active Expired - Fee Related
- 2005-09-06 JP JP2006535861A patent/JP4912149B2/ja active Active
- 2005-09-06 WO PCT/JP2005/016696 patent/WO2006028243A1/ja active Application Filing
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11117890A (ja) * | 1997-10-16 | 1999-04-27 | Aisan Ind Co Ltd | フューエルポンプ |
JP2004011556A (ja) * | 2002-06-07 | 2004-01-15 | Hitachi Unisia Automotive Ltd | タービン型燃料ポンプ |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012163099A (ja) * | 2011-02-04 | 2012-08-30 | Ti Group Automotive Systems Llc | インペラ及び流体ポンプ |
CN102678574A (zh) * | 2011-02-04 | 2012-09-19 | Ti集团自动推进系统有限责任公司 | 叶轮和流体泵 |
KR101935839B1 (ko) * | 2011-02-04 | 2019-01-07 | 티아이 그룹 오토모티브 시스템즈 엘엘씨 | 임펠러 및 유체 펌프 |
JP2015004354A (ja) * | 2013-06-24 | 2015-01-08 | 株式会社デンソー | 燃料ポンプ |
JPWO2020149382A1 (ja) * | 2019-01-16 | 2021-12-02 | 株式会社ミツバ | 非容積型ポンプ及び液体供給装置 |
JP7350020B2 (ja) | 2019-01-16 | 2023-09-25 | 株式会社ミツバ | 非容積型ポンプ及び液体供給装置 |
KR20220089059A (ko) * | 2020-12-21 | 2022-06-28 | (주)모토닉 | 터빈형 연료펌프 |
KR102566780B1 (ko) * | 2020-12-21 | 2023-08-16 | (주)모토닉 | 터빈형 연료펌프 |
CN114320936A (zh) * | 2021-12-28 | 2022-04-12 | 中国航空工业集团公司金城南京机电液压工程研究中心 | 一种具有火焰抑制的多作用排气装置 |
Also Published As
Publication number | Publication date |
---|---|
DE112005002121B4 (de) | 2017-11-02 |
JPWO2006028243A1 (ja) | 2008-05-08 |
US20080031733A1 (en) | 2008-02-07 |
JP4912149B2 (ja) | 2012-04-11 |
US7828508B2 (en) | 2010-11-09 |
DE112005002121T5 (de) | 2007-08-16 |
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