WO2016181520A1 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
WO2016181520A1
WO2016181520A1 PCT/JP2015/063741 JP2015063741W WO2016181520A1 WO 2016181520 A1 WO2016181520 A1 WO 2016181520A1 JP 2015063741 W JP2015063741 W JP 2015063741W WO 2016181520 A1 WO2016181520 A1 WO 2016181520A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
pressure
sliding surface
pressure side
side plate
Prior art date
Application number
PCT/JP2015/063741
Other languages
English (en)
Japanese (ja)
Inventor
次則 石中
Original Assignee
株式会社 島津製作所
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 株式会社 島津製作所 filed Critical 株式会社 島津製作所
Priority to PCT/JP2015/063741 priority Critical patent/WO2016181520A1/fr
Priority to JP2017517536A priority patent/JP6350744B2/ja
Publication of WO2016181520A1 publication Critical patent/WO2016181520A1/fr

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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
    • F04C2/12—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 feeds hydraulic fluid using a tooth space of a drive gear and a driven gear that form a pair of meshing gears.
  • the non-sliding surface side has a higher pressure at the high / low pressure switching portion.
  • the force that the movable side plate receives due to the pressure difference between the sliding surface side and the non-sliding surface side varies with the passage of time because the gear rotates. Therefore, the sizes of the high-pressure side and the low-pressure side region on the non-sliding surface side are usually determined so that the average of the magnitudes of the forces is appropriate (see, for example, Patent Document 1).
  • the magnitude of the action that the movable side plate receives toward the sliding surface side may be larger than the average.
  • no high pressure hydraulic fluid is introduced into the sliding surface at the high / low pressure switching site. For these reasons, a liquid film breakage may occur between the side surface of the gear and the sliding surface of the movable side plate, and abnormal wear may occur.
  • the present invention pays attention to the above points, and by utilizing the hydraulic pressure regardless of the number of teeth and the shape of the teeth by suppressing the occurrence of liquid film breakage between the gear and the movable side plate and the accompanying abnormal wear.
  • An object is to enable the movable side plate to be designed to be pressed against the gear with an appropriate force.
  • the gear pump according to the present invention has a configuration as described below. That is, the gear pump according to the present invention includes a casing having a gear housing chamber for housing a pair of gears, and a high-pressure side on a sliding surface that is a surface that is interposed between the casing and the gear and faces the gear.
  • the movable side plate having a high-pressure introduction groove at the portion and a non-sliding surface which is a surface opposite to the gear side of the movable side plate are provided with a space between the non-sliding surface and the casing in the high-pressure side and the low-pressure side.
  • a gear pump having a gasket divided into a side and a liquid film forming recess is provided at a switching portion from the low pressure side to the high pressure side on the sliding surface of the movable side plate.
  • the “switching portion from the low pressure side to the high pressure side” means a portion facing the tooth of the corresponding rotation phase between the low pressure side edge of the gasket and the low pressure side edge of the high pressure introduction groove. It is the concept which shows.
  • Examples of specific embodiments of the recess for forming a liquid film include a liquid reservoir hole that is bottomed and does not communicate between the low pressure side and the high pressure side, and a liquid introduction groove that is bottomed and communicates between the low pressure side and the high pressure side.
  • the movable side plate is geared using the hydraulic pressure regardless of the number of teeth and the shape of the teeth. Can be designed to be pressed with an appropriate force toward
  • the gear pump P mainly includes a casing 1 having a gear housing chamber 11 a therein, and a circumscribed portion that is housed and held in the gear housing chamber 11 a of the casing 1 and meshes with each other.
  • a gear pair that is, a drive gear 2 and a driven gear 3, and movable side plates 6 and 6 that are in contact with both side surfaces 2 a and 3 a of the gears 2 and 3 are provided.
  • the driving gear 2 and the driven gear 3 are well-known gears in which a plurality of tooth bodies are provided at predetermined intervals along the outer peripheral surface.
  • the drive shaft 4 is integrally extended from the center of the drive gear 2 in the rotational axis direction
  • the driven shaft 5 is integrally extended from the driven gear 3 in the rotational axis direction.
  • the drive gear 2 and the drive shaft 4 may be configured separately, and the driven gear 3 and the driven shaft 5 may be configured separately.
  • the casing 1 includes a body 11 having the gear housing chamber 11a, a front cover 12 serving as a cover for closing the opening surface of the gear housing chamber 11a, and an opening surface of the gear housing chamber 11a. It is comprised from the rear cover 13 which is a cover.
  • the body 11 is formed with a substantially glasses-like gear housing chamber 11a for housing the gear pair, that is, the driving gear 2 and the driven gear 3 in a meshed state.
  • the body 11 has a suction port X and a discharge port Y which are not shown in FIG. 1 opened at positions facing the meshing portion of the drive gear 2 and the driven gear 3. is there.
  • the front cover 12 is detachably attached to the body 11 with a bolt or the like, for example, and closes the front opening surface of the gear housing chamber 11a, and a bearing hole into which the drive shaft 4 and the driven shaft 5 can be respectively fitted. 12a and 12b are formed.
  • a bush 7 is fitted into the bearing hole 12a near the position where the drive gear 2 is to be inserted, and one end of the drive shaft 4 is inserted into the bush 7 so as to be rotatably supported.
  • a bush 7 is fitted into the bearing hole 12b near the position where the driven gear 3 is to be inserted, and one end of the driven shaft 5 is inserted into the bush 7 so as to be rotatably supported.
  • the rear cover 13 is also detachably attached to the body 11 with a bolt or the like and closes the rear opening surface of the gear housing chamber 11a, and the drive shaft 4 and the driven shaft 5 can be respectively inserted thereinto.
  • Bearing holes 13a and 13b are formed.
  • a bush 7 is fitted in the bearing hole 13a near the position where the drive gear 2 is to be inserted, and the other end of the drive shaft 4 is inserted into the bush 7 so as to be rotatably supported.
  • a bush 7 is also fitted in the bearing hole 13b near the position where the driven gear 3 is to be inserted, and the other end of the driven shaft 5 is inserted into the bush 7 so as to be rotatably supported.
  • the body 11 and the front cover 12 are integrally formed, and the gear storage chamber 11a is closed from the rear by the rear cover 13, or the body 11 and the rear cover 13 are integrally formed and the gear cover chamber 11a is forwarded by the front cover 12.
  • the gear storage chamber 11a is closed from the rear by the rear cover 13, or the body 11 and the rear cover 13 are integrally formed and the gear cover chamber 11a is forwarded by the front cover 12.
  • the movable side plate 6 is disposed at two locations so as to be brought into contact with both side surfaces 2 a and 3 a of the drive gear 2 and the driven gear 3, and the side surfaces 2 a and 3 a of the drive gear 2 and the driven gear 3. It is for sealing each.
  • a high-pressure introduction groove 6x is provided on the outer peripheral edge of the sliding surface 6a of the movable side plate 6 in order to reduce the bearing load.
  • high-pressure hydraulic fluid is introduced from the discharge port Y into the region indicated by the oblique lines in FIG. 2 on the sliding surface 6 a side of the movable side plate 6.
  • a gasket groove 6y is provided in the non-sliding surface 6b of the movable side plate 6, and the gasket 8 is fitted into the gasket groove 6y.
  • the gasket groove 6y includes a high-pressure introduction portion 6y2 that opens toward the outer periphery of the movable side plate 6, and an outer peripheral edge located on the inner side of the outer periphery of the movable side plate 6 and a low-pressure side edge that is a low-pressure side edge of the high-pressure introduction groove 6a. And the surrounding portion 6y1 reaching the lower pressure side.
  • the gasket 8 is mounted in the gasket groove 6y, and divides the pressure balance region into a low pressure side, that is, a suction port X side and a high pressure side, that is, a discharge port Y side.
  • a region indicated by diagonal lines in FIG. 3 is a high-pressure side region.
  • the gasket 8 includes a gasket body 81 attached to the circumferential portion 6y1 of the gasket groove 6y, and a closing portion 82 for closing the high pressure introduction portion 6y2 of the gasket groove 6y. Yes.
  • the low-pressure end edge of the gasket 8 reaches the low-pressure side further than the low-pressure end edge 6x1 of the high-pressure introduction groove 6x.
  • the gear pump P is connected between the suction port X and the discharge port Y.
  • a difference between high and low pressure occurs, and the toothed body (not shown) of the drive gear 2 and the driven gear 3 gradually separates from each other, the inner space of the body 11, that is, the suction port X side becomes a low pressure region, and the toothed bodies gradually mesh with each other.
  • the space inside the body 11 on the side to be operated, that is, the discharge port Y side becomes a high pressure region.
  • the hydraulic fluid introduced from the suction port X is confined in a volume space closed between the tooth tips of the drive gear 2 and the driven gear 3 and the inner periphery of the casing 1 and guided to the discharge port Y to be discharged.
  • the pump is operated.
  • a liquid reservoir hole 6z which is a recess for forming a liquid film is provided at a switching portion from the low pressure side to the high pressure side on the sliding surface 6a of the movable side plate 6. More specifically, when one tooth tip 2b of the tooth of the gear 2 reaches the low-pressure side edge 8x of the gasket 8, one tooth tip 2b of the gear tooth is formed from a portion facing the tooth 8b.
  • a plurality of reservoir holes 6z which are the recesses for forming a liquid film, are formed on the part facing the tooth, that is, the part marked with light ink in FIG. Provided.
  • the liquid reservoir hole 6z is a recess having a bottom and does not communicate with the low pressure side and the high pressure side. In the present embodiment, a large number of the reservoir holes 6z are randomly arranged in the portion.
  • the gear 2 is indicated by an imaginary line. Although only the drive gear 2 side is shown in the figure, the liquid reservoir hole 6z is similarly provided on the driven gear 3 side.
  • the hydraulic fluid in the tooth gap on the sliding surface 6a side is low pressure, whereas the hydraulic fluid on the non-sliding surface 6b side is higher pressure.
  • the liquid reservoir hole 6z is formed at a corresponding portion of the sliding surface 6a, and a part of the hydraulic fluid guided from the low pressure side is guided into the liquid reservoir hole 6z.
  • a liquid film is formed by the working liquid in the liquid reservoir hole 6z.
  • the hydraulic fluid film is provided on the sliding surface 6a side in the switching portion from the low pressure side to the high pressure side regardless of the pressure difference between the sliding surface 6a side and the non-sliding surface 6b side in the portion. Can be generated. Therefore, it is possible to suppress the occurrence of the liquid film breakage at the site. Then, by suppressing the occurrence of abnormal wear due to the liquid film breakage, the movable side plate 6 is pressed toward the gears 2 and 3 with an appropriate force using the hydraulic pressure regardless of the number of teeth and the shape of the teeth. Can be designed as needed.
  • the liquid introduction groove 6m is a bottomed groove that communicates the low pressure side and the high pressure side.
  • the liquid introduction groove 6 m extends in the circumferential direction around the axis of the drive shaft 4 or the driven shaft 5. Both the width and the depth of the liquid introduction groove 6m are several ⁇ m.
  • the gear 2 is indicated by an imaginary line.
  • the liquid introduction groove 6m is similarly provided on the driven gear 3 side.
  • the width of the liquid introduction groove 6m is drawn larger than the actual, and only three liquid introduction grooves 6m are drawn. A large number of liquid introduction grooves 6m are provided at intervals of several ⁇ m to several tens of ⁇ m.
  • the hydraulic fluid in the tooth gap on the sliding surface 6a side is low pressure, whereas the hydraulic fluid on the non-sliding surface 6b side is higher pressure.
  • the liquid introduction groove 6m is formed at the corresponding location, and a small amount of hydraulic fluid flows through the liquid introduction groove 6m from the high pressure side to the low pressure side. Then, a liquid film is formed by the working fluid flowing through the liquid introduction groove 6m.
  • the sliding portion from the low pressure side to the high pressure side is slid regardless of the pressure difference between the sliding surface 6a side and the non-sliding surface 6b side at that portion.
  • a working fluid film can be generated on the moving surface 6a side. Therefore, it is possible to suppress the occurrence of the liquid film breakage at the site. Then, by suppressing the occurrence of abnormal wear due to the liquid film breakage, the movable side plate 6 is pressed toward the gears 2 and 3 with an appropriate force using the hydraulic pressure regardless of the number of teeth and the shape of the teeth. Can be designed as needed.
  • the occurrence of a liquid film breakage between the gears 2 and 3 and the movable side plate 6 can be suppressed regardless of processing errors in the casing 1 and the movable side plate 6.
  • Productivity can also be increased.
  • the present invention is not limited to the first and second embodiments described above.
  • the liquid reservoir hole that is the recess for forming the liquid film is formed in a circular shape, but the shape of the liquid reservoir hole may be arbitrarily set, for example, a polygonal shape.
  • the reservoir holes are randomly arranged, but the arrangement of the reservoir holes may be arbitrarily set.
  • the number and depth of the reservoir holes and the size of the opening of the reservoir holes may be arbitrarily set.
  • the hydraulic pressure is utilized regardless of the number of teeth and the shape of the teeth.
  • the movable side plate can be designed to be pressed against the gear with an appropriate force.

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

Abstract

L'invention concerne une pompe à engrenages, comportant : un boîtier ayant, en son sein, une chambre de stockage d'engrenages destinée à stocker une paire d'engrenages ; une plaque latérale mobile ayant une rainure d'entrée haute pression dans une région côté haute pression d'une surface coulissante, qui est la surface d'un côté qui repose entre le boîtier et les engrenages et qui fait face aux engrenages ; et un joint qui est prévu sur une surface non coulissante, qui est la surface du côté opposé au côté faisant face aux engrenages de la plaque latérale mobile et qui sépare l'espace entre la surface non coulissante et le boîtier en un côté haute pression et un côté basse pression ; une concavité formant membrane liquide étant prévue dans la région où le côté basse pression passe au côté haute pression dans la surface coulissante de la plaque latérale mobile, afin de supprimer la rupture de membrane liquide entre les engrenages et la plaque latérale mobile et l'usure anormale qui se produit lors d'une telle rupture.
PCT/JP2015/063741 2015-05-13 2015-05-13 Pompe à engrenages WO2016181520A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2015/063741 WO2016181520A1 (fr) 2015-05-13 2015-05-13 Pompe à engrenages
JP2017517536A JP6350744B2 (ja) 2015-05-13 2015-05-13 歯車ポンプ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/063741 WO2016181520A1 (fr) 2015-05-13 2015-05-13 Pompe à engrenages

Publications (1)

Publication Number Publication Date
WO2016181520A1 true WO2016181520A1 (fr) 2016-11-17

Family

ID=57248951

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/063741 WO2016181520A1 (fr) 2015-05-13 2015-05-13 Pompe à engrenages

Country Status (2)

Country Link
JP (1) JP6350744B2 (fr)
WO (1) WO2016181520A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018114919A1 (fr) * 2016-12-21 2018-06-28 Robert Bosch Gmbh Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue
JP2021063455A (ja) * 2019-10-11 2021-04-22 ダイキン工業株式会社 歯車ポンプ又は歯車モータ

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001099071A (ja) * 1999-10-01 2001-04-10 Koyo Seiko Co Ltd ギヤポンプ
US20050058566A1 (en) * 2003-09-11 2005-03-17 Christensen Matthew Peter Gear motor start up control
JP2007239501A (ja) * 2006-03-06 2007-09-20 Toyota Industries Corp ギヤポンプ
JP2012077686A (ja) * 2010-10-01 2012-04-19 Shimadzu Corp 歯車ポンプ又はモータ

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1465021A (en) * 1974-05-07 1977-02-16 Bosch Gmbh Robert Externally-meshing gear pump or gear motor
JPS53114604U (fr) * 1977-02-22 1978-09-12
JPS5797197U (fr) * 1980-12-05 1982-06-15

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001099071A (ja) * 1999-10-01 2001-04-10 Koyo Seiko Co Ltd ギヤポンプ
US20050058566A1 (en) * 2003-09-11 2005-03-17 Christensen Matthew Peter Gear motor start up control
JP2007239501A (ja) * 2006-03-06 2007-09-20 Toyota Industries Corp ギヤポンプ
JP2012077686A (ja) * 2010-10-01 2012-04-19 Shimadzu Corp 歯車ポンプ又はモータ

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018114919A1 (fr) * 2016-12-21 2018-06-28 Robert Bosch Gmbh Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue
JP2021063455A (ja) * 2019-10-11 2021-04-22 ダイキン工業株式会社 歯車ポンプ又は歯車モータ

Also Published As

Publication number Publication date
JPWO2016181520A1 (ja) 2017-10-26
JP6350744B2 (ja) 2018-07-04

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