WO2008029477A1 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
WO2008029477A1
WO2008029477A1 PCT/JP2006/317872 JP2006317872W WO2008029477A1 WO 2008029477 A1 WO2008029477 A1 WO 2008029477A1 JP 2006317872 W JP2006317872 W JP 2006317872W WO 2008029477 A1 WO2008029477 A1 WO 2008029477A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
pressure side
hole
eyeglass
gear pump
Prior art date
Application number
PCT/JP2006/317872
Other languages
English (en)
Japanese (ja)
Inventor
Tsugunori Ishinaka
Koji Komatsu
Takumi Ishihara
Original Assignee
Shimadzu Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shimadzu Corporation filed Critical Shimadzu Corporation
Priority to JP2008533020A priority Critical patent/JP4952719B2/ja
Priority to KR1020097004368A priority patent/KR101146501B1/ko
Priority to CN2006800557822A priority patent/CN101512158B/zh
Priority to PCT/JP2006/317872 priority patent/WO2008029477A1/fr
Priority to TW096131675A priority patent/TWI378181B/zh
Publication of WO2008029477A1 publication Critical patent/WO2008029477A1/fr

Links

Classifications

    • 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
    • F04C2/086—Carter
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Definitions

  • the present invention relates to a gear pump that is particularly applicable to construction machines, vehicle hydraulic machines, and the like.
  • a gear pump XI comprising a cover X3, X5 covering the front and rear sides of the body X4 and a casing X2 formed by connecting the covers X3 and X5 with fixing bolts X8, a construction machine, a hydraulic machine for vehicles Have been widely used as a hydraulic supply source.
  • This gear pump XI has a function of supplying hydraulic fluid to the space between the drive gear X61 and the driven gear X62 from the low-pressure side passage port X43 communicating with the above-mentioned glasses hole X4a and discharging it from the high-pressure side passage X41.
  • Patent Document 1 Japanese Patent Laid-Open No. 2003-336583
  • the present invention is configured to solve the above problems.
  • the gear pump according to the present invention includes one or a plurality of gear pairs formed by combining a driving gear and a driven gear, and a casing that houses the gear pairs, and the casing force
  • the gear pair A bearing hole formed by passing through a shaft for pivotally supporting the gear constituting the gear pair, a low pressure side port communicating with the glasses hole and sucking low pressure hydraulic fluid, A body having a high-pressure side port that communicates with the eyeglass hole and discharges high-pressure hydraulic fluid, a valve mounting portion provided in the vicinity of the high-pressure side port to which a valve can be attached, and at least one of the front and rear of the body A cover that is provided on one side and closes the eyeglass hole, wherein the body communicates with the bearing hole a return passage that communicates from the valve mounting portion to the low pressure side port. And further comprising a front-rear direction position.
  • the portion of the body provided with the bearing hole is thicker than the portion provided with the eyeglass hole, so that the strength of the body is not greatly impaired even if a return passage is provided. . That is, it is possible to reduce the number of parts and the installation space when arranging such a gear pump or motor by providing a return passage without significantly reducing the strength of the body. Furthermore, the body itself does not need to be made thicker than the conventional one as compared with the aspect in which the part around the eyeglass hole of the body is made thicker and the return passage is provided in the part. Material costs for manufacturing can be reduced.
  • the “front-rear direction position corresponding to the bearing hole” is a concept including all the front-rear direction positions where the bearing hole exists and the eyeglass hole does not exist.
  • the strength of the body is provided by providing a return passage at such a position.
  • a return passage is provided without greatly impairing the number of parts, and the number of parts and the installation space when such a gear pump or motor is disposed can be reduced.
  • the body itself does not need to be made thicker than the conventional one, as compared to a mode in which the part around the eyeglass hole of the body is thickened and a return passage is provided in the part. The material cost when manufacturing the body can be saved.
  • FIG. 1 is a side sectional view showing a gear pump according to a first embodiment of the present invention.
  • FIG. 2 is a left side view showing the gear pump in the same embodiment.
  • FIG. 3 is a right side view showing the gear pump in the same embodiment.
  • FIG. 4 is a sectional view taken along line XX in FIG.
  • FIG. 5 is a side sectional view showing a gear pump according to a second embodiment of the present invention.
  • FIG. 6 Y—Y sectional view in FIG.
  • FIG. 7 is a side sectional view showing a conventional gear pump.
  • FIG. 8 is a ZZ cross-sectional view in FIG.
  • the gear pump 1 provided by the present invention is a dual gear pump having first and second gear pairs 6 and 7.
  • This gear pump 1 has a first gear pair 6 as shown in FIG. 1 for a longitudinal sectional view, FIG. 2 for a left side view, FIG. 3 for a right side view, and FIG. 4 for a XX sectional view in FIG.
  • the first driving gear 61 and the first driven gear 62 are combined together.
  • the second gear pair 7 is configured by combining a second drive gear 71 and a second driven gear 72 together.
  • the first and second gear pairs 6 and 7 are accommodated in a casing 2 that also has front cover 3, body 4 and rear cover 5 force.
  • first and second eyeglass holes 4 a and 4 b are provided at both front and rear ends of the body 4, and the pair of gears 6 and 7 are divided into an intermediate portion of the body 4.
  • An intermediate partition wall 4W is formed.
  • a first gear pair 6 is housed in the chamber formed by the first eyeglass hole 4a and the front cover 3, and the room formed by the second eyeglass hole 4b and the rear cover 5 is 2 gear pairs 7 are housed.
  • the intermediate partition wall 4W communicates with the first and second eyeglass holes 4a and 4b, respectively, and pivots an input / output shaft 611 and a second drive gear 71 that pivotally support the first drive gear 61.
  • a bearing hole 4x through which the supporting shaft 711 is inserted is provided.
  • the intermediate partition wall 4W communicates with the first and second eyeglass holes 4a and 4b, respectively, and pivotally supports a shaft 621 and a second driven gear 72 that pivot the first driven gear 62. There are also provided bearing holes 4y through which the shafts 721 to be inserted are inserted.
  • the front cover 3 and the rear cover 5 have the same configuration as that known for use in this type of dual gear pump. That is, the front cover 3 is provided with a bearing hole 3x through which the input / output shaft 611 is inserted and a bearing hole 3y through which the shaft 621 pivotally supporting the first driven gear 62 is inserted.
  • the rear cover 5 has a bearing hole 5x through which a shaft 711 for pivotally supporting the second drive gear 71 and a shaft 721 for pivotally supporting the second driven gear 72 are inserted. 5y is provided.
  • the front cover 3, the body 4, and the rear cover 5 are integrally fixed by fixing bolts 8.
  • the Freon An oil seal 91 is provided between the cover 3 and the input / output shaft 611.
  • the first drive gear 61 is formed integrally with the input / output shaft 611.
  • the input / output shaft 611 is supported to the casing 2 by a bush 92 disposed in the bearing hole 3x of the front cover 3 and in the bearing hole 4x of the body 4.
  • the first driven gear 62 is also formed integrally with the shaft 621.
  • the shaft 621 is supported to the casing 2 by a bush 92 disposed in the bearing hole 3y of the front cover 3 and in the bearing hole 4y of the body 3.
  • the second drive gear 71 is formed integrally with the shaft 711.
  • the shaft 711 is supported to the casing 2 by a bush 92 arranged in the bearing hole 4x of the body 4 and in the bearing hole 5x of the rear cover 5 on the same axis as the first drive gear 61. ing.
  • the shaft 711 supporting the second drive gear 71 is fixed to the shaft end of the input / output shaft 611, and therefore the second drive gear 71 is synchronized with the first drive gear 61.
  • the second driven gear 72 is also formed integrally with the shaft 721.
  • the shaft 721 is supported on the casing 2 by a bush 92 disposed in the bearing hole 4y of the body 4 and in the bearing hole 5y of the rear cover 5 on the same axis as the first driven gear 62. ing.
  • the shaft 721 that supports the second driven gear 72 is completely separate from the shaft 621 that supports the first driven gear 62, and the first driven gear 62 and the second driven gear 72 are These are driven separately by the first drive gear 61 and the second drive gear 71, respectively.
  • the body 4 has first and second high-pressure side flow paths 41 and 42 on one side and a low-pressure side flow path 43 on the other side.
  • the low pressure side flow path B 43 becomes an inflow port
  • the first and second high pressure side flow paths B 41 and 42 become discharge ports.
  • the first and second high pressure side passages 41 and 42 are respectively provided in the first eye hole 4a for accommodating the first gear pair 6 and the second eye hole 4b for accommodating the second gear pair 7. Communicate.
  • the low pressure side flow path B 43 is connected to the first and second eyeglass holes 4a, 4b and extends in the front-rear direction, and is drilled from the middle of the connection part 431 toward the other side surface.
  • the opening 432 is made of.
  • a return passage 45 is provided in such a way that the front and rear positions of the bearing holes 4x and 4y are made to communicate with the valve mounting portion 44 and the low pressure side flow passage 43. That is, a return passage 45 is provided in the intermediate partition wall 4W. More specifically, a hole having a shape reaching the nozzle mounting portion 44 is drilled from the opening 432 while keeping the distance from the shaft center of the bearing hole 4x substantially constant, and this hole is returned to the return passage 45. It is said.
  • the working fluid is supplied from the low pressure side flow path B 43 to the tooth grooves of the first drive gear 61 and the first driven gear 62, and
  • the hydraulic fluid supplied to the tooth grooves of the second drive gear 71 and the second driven gear 72 respectively and supplied to the tooth grooves of the first drive gear 61 and the first driven gear 62 is supplied to the first high-pressure side flow path.
  • B and the hydraulic fluid supplied to the tooth spaces of the second drive gear 71 and the second driven gear 72 are discharged from the second high-pressure side flow passage b.
  • the input / output shaft 611 and the shaft 711 supported by the bearing hole 4x are subjected to an action of urging to the lower right in FIG.
  • the intermediate wall 4W that is thicker than the portion of the body 4 where the eyeglass holes 4a are provided is connected to the low pressure side port from the valve mounting portion 44. Since the return passage 45 communicating up to 43 is provided in the bearing hole so that the position in the front-rear direction coincides, the strength of the body 4 is not greatly impaired even if the return passage 45 is provided.
  • the input / output shaft 611 and the shaft 711 are supported by the hydraulic pressure by supporting the return passage above the bearing hole 4x in FIG. 4, that is, with respect to the bearing hole 4x. From this point, the loss of strength of the body 4 due to the provision of the return passage 45 is small.
  • the return passage 45 can be provided without greatly degrading the strength of the body 4, and the number of parts and the mounting space can be reduced when the gear pump 1 and the valve are disposed. Furthermore, the body 4 itself does not need to be made thicker than the conventional one as compared to the case where the part around the eyeglass hole 4a of the body 4 is made thicker and the relief passage is provided in the part. Material costs for manufacturing the body 4 can also be reduced.
  • the gear pump Al that works in this embodiment has a gear pair A6 and a gear pair A6 as shown in FIG. 5 in a longitudinal sectional view and in FIG. 6 in a YY sectional view in FIG.
  • a casing A2 comprising a front cover A3 and a body A4 is provided.
  • the gear pair A6 is constructed by combining a first drive gear A61 and a first driven gear A62.
  • a spectacle hole A4a is provided in the front end portion of the body A4, and the gear pair A6 is housed in a space formed by the spectacle hole A4a and the front cover A3.
  • the body A4 is connected to the eyeglass hole A4a, and the bearing holes A4x, A4y are formed by inserting the input / output shaft A611 that pivotally supports the drive gear A61 and the shaft A621 that pivotally supports the driven gear A62, respectively. Is provided.
  • the front cover A3 has the same configuration as that well known as that used in this type of gear pump. That is, the front cover 3 is provided with a bearing hole A3x through which the input / output shaft A611 is inserted and a bearing hole A3y through which the shaft A621 pivotally supporting the driven gear A62 is inserted.
  • the front cover A3 and the body A4 are integrally fixed with fixing bolts A8.
  • An oil seal A91 is provided between the front cover A3 and the input / output shaft A611.
  • the eyeglass hole A 4a is indicated by an imaginary line.
  • the drive gear A61 is formed integrally with the input / output shaft A611.
  • the input / output shaft A611 is supported with respect to the casing A2 by a bush A92 disposed in the bearing hole A3x of the front cover A3 and in the bearing hole A4x of the body.
  • the driven gear A 62 is also formed integrally with the shaft A621.
  • the shaft A621 is supported by the bush A92 disposed in the bearing hole A3y of the front cover A3 and the bearing hole A4y of the body A4 with respect to the casing A2.
  • the body A4 is provided with a high-pressure side channel port A41 on one side surface and a low-pressure side channel port A43 on the other side surface.
  • the low pressure side flow path A43 serves as the inlet
  • the high pressure side flow path A41 serves as the discharge port.
  • the high-pressure side flow path A41 is in communication with a glass hole A4a that houses the gear mechanism A6.
  • the low-pressure side flow path A43 is formed from a connection portion A431 that communicates with the above-described glass hole A4a and extends rearward, and an opening portion A432 that is drilled from the rear end portion of the connection portion A431 toward the other side surface. Become.
  • the high-pressure side flow path B41 is indicated by an imaginary line.
  • a valve mounting portion A44 to which a valve (not shown) represented by a relief valve can be attached is provided on one side surface of the body A4 where the high-pressure side flow path A41 is provided. ing.
  • a return passage A45 is provided so that the front and rear positions of the bearing hole A4x for communicating the valve mounting portion A44 and the low pressure side flow path B43 are aligned. More specifically, a hole having a shape reaching the valve mounting part A44 is formed from the opening A432 while keeping the distance of the axial center force of the first bearing hole A4x substantially constant, and the hole is returned to this hole. Passage A4 5! /
  • the position from the valve mounting portion A44 to the low-pressure side port A43 is communicated with the bearing hole A4x of the body A4 by matching the position in the front-rear direction.
  • the force providing the return passage A45 This part is thicker than the part provided with the glasses hole 4a. Therefore, the presence of the return passage A45 does not greatly impair the strength of the body A4.
  • the passage A45 is supported above the bearing hole A4x in FIG. 6, that is, the bearing hole A4x with respect to the bearing hole A4x, so that the input / output shaft A611 is substantially affected by the hydraulic pressure.
  • the present invention is not limited to the first and second embodiments described above.
  • the present invention may be applied to a gear pump having three or more pairs of gears.
  • the gear pump having two pairs of gears has two pairs of high pressure side flow passages and one low pressure side flow passage port instead of the gear pumps as in the first embodiment described above.
  • it may be configured as a phase difference gear pump in which the timing of meshing the gear pairs is shifted.
  • the casing is configured by the body and the rear cover, and the bearing hole of the body of the casing is provided. You may make it provide a relief channel
  • valve attached to the valve mounting portion is not limited to the relief valve, but may be other types of valves such as a flow control valve! /.
  • the body is relatively thick at the front-rear position corresponding to the bearing hole of the body as compared with the front-rear position corresponding to the eyeglass hole.
  • the return passage can be provided without greatly reducing the strength of the body, and the number of parts and the installation space can be reduced when installing such a gear pump.
  • the body itself does not need to be made thicker than the conventional one, as compared to a mode in which the part around the eyeglass hole of the body is made thicker and a return passage is provided in the part. Material costs for manufacturing can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

La présente invention concerne une pompe à engrenages (1) qui nécessite un nombre réduit de matériaux et un espace d'installation plus petit et qui est produite avec des frais matériels réduits. La pompe à engrenages (1) possède une ou plusieurs paires d'engrenages (6, 7) dans lesquelles des engrenages entraînants (61, 71) et des engrenages entraînés (62, 72) sont engrenés les uns avec les autres, et possède également un carter (2) pour recevoir les paires d'engrenages (6, 7). Le carter (2) est construit à partir d'un corps (4), un couvercle avant (3), et un couvercle arrière (5). Le corps (4) comporte des orifices en forme de monocle (4a, 4b) pour recevoir les paires d'engrenages, des orifices de palier (4x, 4y) qui communiquent avec les orifices en forme de monocle (4a, 4b) et dans lesquels des arbres (611, 621, 711, 721) pour supporter des engrenages (61, 62, 71, 72) qui forment les paires d'engrenages sont insérés, un orifice côté basse pression (43) qui communique avec l'orifice en forme de monocle (4a) et aspire un liquide de fonctionnement à basse pression, des orifices côté haute pression (41, 42) qui communiquent avec l'orifice en forme de monocle (4a) et évacuent un liquide de fonctionnement à haute pression, une section d'installation de soupape (44) prévue près des orifices côté haute pression (41, 42) et sur laquelle une soupape peut être installée, et un passage de retour (45) qui va de la section d'installation de soupape (44) jusqu'à l'orifice côté basse pression (43) et est positionné dans la direction avant-arrière de façon correspondante aux orifices de palier (4x, 4y). Le couvercle avant (3) et le couvercle arrière (5) sont agencés au niveau des côtés avant et arrière du corps (4) pour fermer l'orifice en forme de monocle (4a).
PCT/JP2006/317872 2006-09-08 2006-09-08 Pompe à engrenages WO2008029477A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2008533020A JP4952719B2 (ja) 2006-09-08 2006-09-08 歯車ポンプ
KR1020097004368A KR101146501B1 (ko) 2006-09-08 2006-09-08 기어펌프
CN2006800557822A CN101512158B (zh) 2006-09-08 2006-09-08 齿轮泵
PCT/JP2006/317872 WO2008029477A1 (fr) 2006-09-08 2006-09-08 Pompe à engrenages
TW096131675A TWI378181B (en) 2006-09-08 2007-08-27 Gear pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2006/317872 WO2008029477A1 (fr) 2006-09-08 2006-09-08 Pompe à engrenages

Publications (1)

Publication Number Publication Date
WO2008029477A1 true WO2008029477A1 (fr) 2008-03-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2006/317872 WO2008029477A1 (fr) 2006-09-08 2006-09-08 Pompe à engrenages

Country Status (5)

Country Link
JP (1) JP4952719B2 (fr)
KR (1) KR101146501B1 (fr)
CN (1) CN101512158B (fr)
TW (1) TWI378181B (fr)
WO (1) WO2008029477A1 (fr)

Cited By (4)

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WO2010082966A1 (fr) * 2009-01-19 2010-07-22 Access Business Group International Llc Procédé et appareil de distribution de compositions de fluide
WO2011062063A1 (fr) * 2009-11-20 2011-05-26 ジヤトコ株式会社 Pompe à engrenages hélicoïdaux
CN102257275A (zh) * 2008-12-16 2011-11-23 罗伯特·博世有限公司 内齿轮泵
RU2448272C2 (ru) * 2010-05-20 2012-04-20 Мирослав Георгиевич Георгиевский Шестеренная гидромашина

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TWI699480B (zh) * 2015-04-01 2020-07-21 義大利商薩蒂瑪機械股份有限公司 齒輪傳動正排量式機器
CN112012924B (zh) * 2020-08-22 2021-06-08 苏州讯如电子科技有限公司 谐波型线的齿轮式调压油泵
KR102659308B1 (ko) 2022-11-09 2024-04-22 (주)동일산업 저점도용 고압 기어펌프

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JPH08210210A (ja) * 1994-11-22 1996-08-20 Robert Bosch Gmbh 内燃機関の燃料噴射ポンプのための燃料搬送ポンプ
JPH094571A (ja) * 1995-06-15 1997-01-07 Hydroperfect Internatl (Hpi) 液圧ポンプ装置
JPH10205317A (ja) * 1997-01-20 1998-08-04 Unisia Jecs Corp 内燃機関用オイルポンプ

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DE2554470A1 (de) * 1975-12-04 1977-06-08 Daimler Benz Ag Zahnrad-oelpumpe fuer brennkraftmaschinen

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Publication number Priority date Publication date Assignee Title
JPH08210210A (ja) * 1994-11-22 1996-08-20 Robert Bosch Gmbh 内燃機関の燃料噴射ポンプのための燃料搬送ポンプ
JPH094571A (ja) * 1995-06-15 1997-01-07 Hydroperfect Internatl (Hpi) 液圧ポンプ装置
JPH10205317A (ja) * 1997-01-20 1998-08-04 Unisia Jecs Corp 内燃機関用オイルポンプ

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102257275A (zh) * 2008-12-16 2011-11-23 罗伯特·博世有限公司 内齿轮泵
WO2010082966A1 (fr) * 2009-01-19 2010-07-22 Access Business Group International Llc Procédé et appareil de distribution de compositions de fluide
US8224481B2 (en) 2009-01-19 2012-07-17 Access Business Group International Llc Method and apparatus for dispensing fluid compositions
CN102355943B (zh) * 2009-01-19 2015-01-07 捷通国际有限公司 用于配送流体组合物的方法与仪器
WO2011062063A1 (fr) * 2009-11-20 2011-05-26 ジヤトコ株式会社 Pompe à engrenages hélicoïdaux
JP2011127584A (ja) * 2009-11-20 2011-06-30 Jatco Ltd ヘリカルギヤポンプ
CN102597522A (zh) * 2009-11-20 2012-07-18 加特可株式会社 螺旋齿轮泵
US8801413B2 (en) 2009-11-20 2014-08-12 Jatco Ltd Helical gear pump
RU2448272C2 (ru) * 2010-05-20 2012-04-20 Мирослав Георгиевич Георгиевский Шестеренная гидромашина

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TW200813331A (en) 2008-03-16
KR101146501B1 (ko) 2012-05-29
KR20090042291A (ko) 2009-04-29
CN101512158B (zh) 2013-11-06
CN101512158A (zh) 2009-08-19

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