WO2013186839A1 - Moteur ou pompe à engrenages - Google Patents

Moteur ou pompe à engrenages Download PDF

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Publication number
WO2013186839A1
WO2013186839A1 PCT/JP2012/064937 JP2012064937W WO2013186839A1 WO 2013186839 A1 WO2013186839 A1 WO 2013186839A1 JP 2012064937 W JP2012064937 W JP 2012064937W WO 2013186839 A1 WO2013186839 A1 WO 2013186839A1
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WO
WIPO (PCT)
Prior art keywords
gear
hydraulic
driven
helical gear
pressure
Prior art date
Application number
PCT/JP2012/064937
Other languages
English (en)
Japanese (ja)
Inventor
信雄 向井
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 JP2014520825A priority Critical patent/JP6119748B2/ja
Priority to PCT/JP2012/064937 priority patent/WO2013186839A1/fr
Priority to TW102120463A priority patent/TW201350681A/zh
Publication of WO2013186839A1 publication Critical patent/WO2013186839A1/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
    • F04C2/16—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 helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the present invention relates to a gear pump or a motor provided with an external gear pair composed of a drive gear and a driven gear each utilizing helical gears that mesh with each other, and a casing having a gear storage chamber for storing the external gear pair therein. .
  • a gear pump or a motor including an external gear pair that includes a drive gear and a driven gear that mesh with each other and a casing that internally includes a gear storage chamber that stores the external gear pair has been widely used.
  • the spur gear in which teeth parallel to the axis are formed around the drive gear and driven gear of such a gear pump or motor is the mainstream.
  • a spur gear is used for the drive gear and the driven gear, there are the following problems. Specifically, when the teeth of the drive gear and the teeth of the driven gear mesh with each other, they mesh simultaneously over the entire tooth width. Further, when the meshing between the teeth of the drive gear and the teeth of the driven gear is terminated, the meshing is simultaneously terminated over the entire tooth width. This can cause noise and vibration.
  • a contrivance has been proposed in which helical gears are used as the drive gear and the driven gear (see, for example, Patent Document 1).
  • Such a gear pump or motor has the following configuration, for example. That is, as shown in FIG. 2, an external gear pair X1 composed of a driving side helical gear X6 and a driven side helical gear X7, and a gear storage chamber X2a for storing the external gear pair X1 are internally provided.
  • a casing X2 having a bearing for housing a drive shaft X8 for supporting the helical gear X6 on the driving side and a driven shaft X9 for supporting the driven helical gear X7 on the driving side is housed in the casing X2.
  • a rear-side bearing case X3a and a front-side bearing case X3b that serve as a pair of side plates that are in contact with both side surfaces X6a, X6b, X7a, and X7b of the helical gears X6 and X7, respectively.
  • the hydraulic shafts X41a and X41b have hydraulic chambers X41a and X41b, and the drive shaft X8 and the driven shaft X9 are anti-thrusted by the hydraulic pressure introduced into the hydraulic chambers X41a and X41b.
  • the casing X2 includes a cylindrical body X23 having the gear housing chamber X2a, a front cover X22 attached to the front side of the body X23, and a rear cover X24 attached to the rear side of the body X23.
  • a rear bearing case X3b that pivotally supports the front end side of the driven shaft X9.
  • the bearing case X3a on the rear side receives a large surface pressure due to the thrust load.
  • the balance pistons X43a and X43b of the hydraulic mechanism X4 are arranged on the rear end side of the drive shaft X8 and the driven shaft X9. Are brought into contact with each other and balanced by liquid pressure. As a result, the balance pistons X43a and X43b can apply a pressing force proportional to the fluid pressure against the thrust load.
  • the hydraulic mechanism X4 is provided only for the purpose of reducing and balancing the thrust, when the operating conditions fluctuate, the driving side is the helical gear X6 and the driven side is the helical gear X7.
  • the thrust load received by the cylinder may be uneven and unstable.
  • the bearing cases X3a and X3b are made of a material with high surface pressure strength at a high cost, and by pressure balance using a so-called three-shaped gasket X31, that is, a three-shaped gasket X31. Performance is achieved by forming a hydraulically sealed region inside the rear side and pushing the rear side bearing case X3a strongly against the rear side surfaces X6a and X7a of the driving side helical gear X6 and the driven side helical gear X7 for balancing. It was necessary to maintain.
  • the present invention pays attention to the above points, and can eliminate the restriction that the costly side plate having a high surface pressure strength must be adopted, thereby increasing the degree of design freedom for reducing the component cost. It is an intended object to provide a gear pump or motor that can be used.
  • the gear pump or motor according to the present invention has an external gear pair composed of a driving side helical gear and a driven side helical gear meshing with each other, and a gear storage chamber for storing the external gear pair, and the drive.
  • a casing having a drive shaft for supporting a helical gear on the side and a bearing for housing a driven shaft for supporting the driven helical gear, and a helical gear housed in the casing.
  • a pair of side plates that make contact with both side surfaces of the gear a hydraulic mechanism that has a hydraulic chamber and presses the drive shaft and the driven shaft in the anti-thrust direction by the hydraulic pressure introduced into the hydraulic chamber;
  • the hydraulic pressure mechanism includes a high-pressure hydraulic fluid introduction path that guides hydraulic fluid from the high-pressure side to the hydraulic pressure chamber.
  • the drive shaft and the driven shaft are set in the anti-thrust direction at a value exceeding the maximum value of the varying thrust.
  • Said liquid to press Characterized in that it sets the pressing force of the mechanism.
  • the drive shaft and the driven shaft are pressed in the anti-thrust direction at a value exceeding the maximum value of the varying thrust by the hydraulic mechanism, so the side plate disposed on the thrust direction side is
  • the driving side is not affected by the thrust load from the helical gear and the driven side is not affected by the thrust load from the helical gear. Therefore, the side plate arranged on the thrust direction side can be made of a material having low surface pressure strength. Since both the helical gear on the driving side and the helical gear on the driven side are always pressed in the anti-thrust direction, the driving side on the side of the helical gear and the driven side on the side of the helical gear due to pressure fluctuations. Problems associated with misalignment can also be solved.
  • a gear pump or a motor that can eliminate the restriction that a costly side plate having a high surface pressure strength must be adopted and can increase the degree of freedom in designing to reduce the component cost. Can be provided.
  • the gear pump P ⁇ b> 1 accommodates an external gear pair 1 including a driving-side helical gear 6 and a driven-side helical gear 7 that mesh with each other, and the external gear pair 1.
  • a casing 2 having a gear housing chamber 2a therein and a bearing for housing the drive shaft 8 that supports the helical gear 6 on the driving side and the driven shaft 9 that supports the helical gear 7 on the driven side.
  • a rear plate 3a and a front plate 3b which are housed in the casing 2 and make a pair respectively contacting the both side surfaces 6a, 6b, 7a, 7b of the helical gears 6, 7;
  • a hydraulic mechanism 4 having pressure chambers 41a and 41b and pressing the drive shaft 8 and the driven shaft 9 in the anti-thrust direction by the hydraulic pressure introduced into the hydraulic chambers 41a and 41b;
  • the hydraulic fluid is guided to the pressure chambers 41a and 41b from the high pressure side. Comprising a pressure hydraulic fluid introducing passage 5.
  • the driving-side helical gear 6 and the driven-side helical gear 7 constituting the external gear pair 1 are helical gears that are well known as those used in this type of gear pump.
  • the teeth on the driving side of the helical gear 6 and the teeth on the driven side of the helical gear 7 are operated as a gear pump in a state where they are engaged with each other.
  • the helical gear 6 receives a thrust load going backward
  • the driven gear 7 receives a thrust load going forward.
  • the helical gear 6 on the driving side and the helical gear 7 on the driven side receive thrust loads directed rearward by the hydraulic pressure while operating as a gear pump.
  • the driving side is different in the helical gear 6 and the driven side is different in the helical gear 7.
  • the thrust load is applied toward the rear.
  • the drive side is provided with the helical gear 6 and the drive shaft 8 integrally.
  • the drive shaft 8 extends from the center of the helical gear 6 on the drive side in the rotational axis direction.
  • One end of the drive shaft 8 extends to the outside of the casing 2.
  • the driven side is provided integrally with the helical gear 7 and the driven shaft 9.
  • the driven shaft 9 extends from the center of the driven helical gear 7 in the direction of the rotational axis.
  • the casing 2 includes a casing body 21 having a gear housing chamber 2a that opens forward, and a front cover 22 that is mounted on the front side of the casing body 21.
  • the casing main body 21 has a substantially eyeglass-shaped gear housing chamber 2a in which the external gear pair 1, that is, the driving-side helical gear 6 and the driven-side helical gear 7 are housed in an engaged state, and the gear housing chamber 2a.
  • the body 23 includes a bearing 25 that supports the rear end sides of the drive shaft 8 and the driven shaft 9 behind the gear housing chamber 2a.
  • Each bearing 25 is provided with a bearing hole 25x into which the rear end side of the drive shaft 8 and the driven shaft 9 can be respectively fitted, and is slidable on the drive shaft 8 and the driven shaft 9 provided on the inner periphery of the bearing hole 25x. And a bush 25y that pivotally supports the shaft.
  • the front cover 22 is detachably attached to the casing body 21 with bolts or the like, and closes the opening surface of the gear housing chamber 2a.
  • the front cover 22 includes a bearing 26 that pivotally supports the front end sides of the drive shaft 8 and the driven shaft 9.
  • Each bearing 26 is provided with a bearing hole 26x in which the front end sides of the drive shaft 8 and the driven shaft 9 can be respectively fitted, and an inner periphery of the bearing hole 26x so that the drive shaft 8 and the driven shaft 9 can slide.
  • a supporting bush 26y is provided.
  • the front end of the drive shaft 8 passes through the bearing hole 26x and protrudes to the outside of the casing 2.
  • the driving side is provided with the rear side plate 3 a attached to the rear side surface 6 a of the helical gear 6 and the driven side helical gear 7.
  • This rear side plate 3a has a thin plate shape substantially the same as that used in a spur gear type gear pump.
  • the rear surface of the rear side plate 3 a is brought into contact with the stepped end surface 21 a of the casing body 21 through a three-shaped gasket 31.
  • the hydraulic pressure sealing region formed inside the three-shaped gasket 31 is set narrower than that of the conventional one.
  • the driving side is provided with a front side plate 3b attached to the front side surface 6b of the helical gear 6 and the driven side helical surface 7b.
  • the front side plate 3b is made of a material having a relatively high surface pressure strength, and has a thin plate shape.
  • the front surface of the front plate 3 b is in contact with the inner surface 22 a of the front cover 22 via the gasket 32.
  • the material of the front side plate 3b is different from the material of the rear side plate 3a.
  • the hydraulic mechanism 4 includes a pair of hydraulic chambers 41a and 41b formed inside the rear cover 24 so as to correspond to the drive shaft 8 and the driven shaft 9, respectively, and these hydraulic chambers 41a and 41b are connected to the casing body 21.
  • a pair of cylinder bores 42a and 42b communicating with each other, and a pair of balance pistons 43a and 43b slidably fitted in the cylinder bores 42a and 42b, respectively. 43b are brought into contact with the corresponding end surfaces of the drive shaft 8 and the driven shaft 9.
  • the diameters of the balance pistons 43a and 43b in other words, the diameters of the cylinder bores 42a and 42b in which the balance pistons 43a and 43b are fitted exceed the maximum value of the fluctuating thrust.
  • the drive shaft is on the drive shaft 8 side in the anti-thrust direction with a force F1 of P ⁇ A1. It is pressed by the balance piston 43a.
  • the cylinder bore 42a on the drive shaft 8 side is disconnected so that the pressing force F1 becomes 10.
  • the area A1 is set.
  • the driven shaft 9 When the pressure of the hydraulic fluid is P and the cross-sectional area of the cylinder bore 43b on the driven shaft 9 side is A2, the driven shaft 9 is pressed by the balance piston in the anti-thrust direction with a force F2 of P ⁇ A2.
  • the cylinder bore 42b on the driven shaft 9 side is disconnected so that the pressing force F2 becomes 5.
  • the area A2 is set.
  • the high-pressure hydraulic fluid introduction path 5 is for guiding the hydraulic fluid from the high-pressure side to the hydraulic chambers 41 a and 41 b of the hydraulic mechanism 4 and is formed in the casing body 21.
  • the hydraulic fluid introduced from the hydraulic fluid suction port is confined in a volume space that is closed between the tooth tip of the helical gear 6 on the driving side and the helical gear 7 on the driven side and the gear housing chamber 2a.
  • a pumping action is performed so as to lead to the hydraulic fluid discharge port 2b and discharge.
  • the gear pump P1 introduces high-pressure hydraulic fluid from the hydraulic fluid discharge port 2b, thereby taking out rotational torque from the drive shaft 8 and driving an external load, and at the same time, operating the hydraulic fluid at low pressure in the operation. It goes without saying that it can also function as a gear motor that performs the motor action of discharging from the liquid suction port.
  • the diameters of the cylinder bores 42a and 42b that house the balance pistons 43a and 43b exceed the maximum value of the fluctuating thrust. Since the shaft 8 and the driven shaft 9 are set to values capable of pressing in the anti-thrust direction, the rear side plate 3a is not affected by the thrust. Therefore, the rear side plate 3a can be configured by using a material having a low surface pressure strength which is substantially the same as that used in the spur gear type gear pump. Further, since the front side plate 3b receives a pressing force from the balance pistons 43a and 43b, the front side plate 3b needs to be made of a material having a sufficient surface pressure strength.
  • the front side plate 3b is made of a thin plate.
  • Can do That is, it is possible to eliminate the restriction that a material having a high cost and high surface pressure strength must be used for the side plates 3a and 3b, and it is possible to increase the degree of design freedom for reducing the component cost.
  • a bearing case having a bearing for viewing the drive shaft and the driven shaft can be omitted, and the thrust can be received by the thin plate-like rear side plate 31 and front side plate 32, thereby reducing the number of parts and manufacturing cost. Can be reduced.
  • both the helical gear 6 on the driving side and the helical gear 7 on the driven side are always pressed forward, that is, in the direction opposite to the last force, so that the driving side helical gear 6 and the driven gear due to pressure fluctuations.
  • the problem that the hydraulic fluid leaks from the side surfaces 6a, 6b, 7a and 7b of the gears 6 and 7 due to the displacement of the side surfaces 6a, 6b, 7a and 7b of the helical gear 7 can be solved. .
  • the substantially eyeglass-shaped gear housing chamber 2a that accommodates the external gear pair 1 in an engaged state therein, and the hydraulic fluid inlet and the hydraulic fluid outlet that communicate the gear housing chamber 2a with the outside. Since the cylindrical body 23 provided with 2b and the rear cover 24 for closing the rear end of the body 23 are integrally formed as the body main body 21, the body 23 is different from the one formed separately. From this point, it is possible to eliminate the problem that the hydraulic fluid leaks from the joint portion between the rear cover 24 and the rear cover 24, and the volume performance is lowered.
  • the body is integrally formed with a body including a gear storage chamber that stores the external gear pair and a rear cover that closes the rear end of the body.
  • a gear storage chamber that stores the external gear pair
  • a rear cover that closes the rear end of the body.
  • the rear side plate and the front side plate are made of different materials.
  • the rear side plate and the front side plate may be made of the same material.

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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)
  • Hydraulic Motors (AREA)

Abstract

L'invention concerne un moteur ou une pompe à engrenages comprenant : une paire d'engrenages s'engrenant extérieurement (1) qui est composée d'un engrenage hélicoïdal menant (6) et d'un engrenage hélicoïdal mené (7) qui s'engrènent l'un avec l'autre ; un carter (2) qui comprend à l'intérieur de celui-ci une chambre de logement d'engrenages (2a) permettant de loger la paire d'engrenages s'engrenant extérieurement (1) et qui comprend des paliers (25, 26) permettant de recevoir un arbre menant (8) qui supporte l'engrenage hélicoïdal menant (6) de manière rotative et recevant également un arbre mené (9) qui supporte l'engrenage hélicoïdal mené (7) de manière rotative ; une paire de plaques latérales (31, 32) qui sont logées à l'intérieur du carter (2) et qui sont chacune disposées en contact avec des surfaces latérales (6a, 7a, 6b, 7b) de chacun des engrenages hélicoïdaux (6, 7) de la paire d'engrenages s'engrenant extérieurement (1) ; un mécanisme hydraulique (4) qui comprend des chambres hydrauliques (41a, 41b) et qui, au moyen d'une pression hydraulique introduite dans les chambres hydrauliques (41a, 41b), presse l'arbre menant (8) et l'arbre mené (9) dans la direction opposée à la direction d'action d'une poussée axiale ; et un passage d'introduction de fluide hydraulique à haute pression (5) qui introduit un fluide hydraulique depuis le côté haute pression dans les chambres hydrauliques (41a, 41b) du mécanisme hydraulique (4). La pression de pressage générée par le mécanisme hydraulique (4) est définie de sorte que l'arbre menant (8) et l'arbre mené (9) sont pressés à une valeur supérieure à la valeur maximale d'une poussée axiale variable, l'arbre menant (8) et l'arbre mené (9) étant pressés dans la direction opposée à la direction d'action de la poussée axiale.
PCT/JP2012/064937 2012-06-11 2012-06-11 Moteur ou pompe à engrenages WO2013186839A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2014520825A JP6119748B2 (ja) 2012-06-11 2012-06-11 歯車ポンプ又はモータ
PCT/JP2012/064937 WO2013186839A1 (fr) 2012-06-11 2012-06-11 Moteur ou pompe à engrenages
TW102120463A TW201350681A (zh) 2012-06-11 2013-06-10 齒輪泵及馬達

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/064937 WO2013186839A1 (fr) 2012-06-11 2012-06-11 Moteur ou pompe à engrenages

Publications (1)

Publication Number Publication Date
WO2013186839A1 true WO2013186839A1 (fr) 2013-12-19

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PCT/JP2012/064937 WO2013186839A1 (fr) 2012-06-11 2012-06-11 Moteur ou pompe à engrenages

Country Status (3)

Country Link
JP (1) JP6119748B2 (fr)
TW (1) TW201350681A (fr)
WO (1) WO2013186839A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5654717B1 (ja) * 2014-03-20 2015-01-14 住友精密工業株式会社 液圧装置
WO2016052570A1 (fr) * 2014-09-30 2016-04-07 ダイキン工業株式会社 Pompe ou moteur à engrenages

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015181908A1 (fr) * 2014-05-28 2015-12-03 株式会社 島津製作所 Pompe ou moteur à engrenages
KR102009908B1 (ko) * 2018-05-15 2019-08-14 김범열 헬리컬 기어펌프

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS542407Y1 (fr) * 1973-07-12 1979-02-01
JPS59213962A (ja) * 1983-05-20 1984-12-03 Hokuetsu Kogyo Co Ltd ロ−タリ・コンプレツサ
JPH0213185U (fr) * 1988-06-30 1990-01-26
JPH04228892A (ja) * 1990-06-30 1992-08-18 Kobe Steel Ltd 油冷式スクリュ圧縮機

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO20010540A1 (it) * 2001-09-07 2003-03-07 Mario Antonio Morselli Perfezionamenti in una pompa volumetrica rotativa
JP2003254259A (ja) * 2002-03-04 2003-09-10 Ebara Corp ギヤポンプ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS542407Y1 (fr) * 1973-07-12 1979-02-01
JPS59213962A (ja) * 1983-05-20 1984-12-03 Hokuetsu Kogyo Co Ltd ロ−タリ・コンプレツサ
JPH0213185U (fr) * 1988-06-30 1990-01-26
JPH04228892A (ja) * 1990-06-30 1992-08-18 Kobe Steel Ltd 油冷式スクリュ圧縮機

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5654717B1 (ja) * 2014-03-20 2015-01-14 住友精密工業株式会社 液圧装置
WO2015140986A1 (fr) * 2014-03-20 2015-09-24 住友精密工業株式会社 Dispositif hydraulique
WO2016052570A1 (fr) * 2014-09-30 2016-04-07 ダイキン工業株式会社 Pompe ou moteur à engrenages
JP2016070210A (ja) * 2014-09-30 2016-05-09 ダイキン工業株式会社 歯車ポンプ又は歯車モータ
US20170298934A1 (en) * 2014-09-30 2017-10-19 Daikin Industries, Ltd. Gear pump and gear motor
EP3203083A4 (fr) * 2014-09-30 2018-03-28 Daikin Industries, Ltd. Pompe ou moteur à engrenages
US10267309B2 (en) 2014-09-30 2019-04-23 Daikin Industries, Ltd. Gear pump and gear motor

Also Published As

Publication number Publication date
TW201350681A (zh) 2013-12-16
JP6119748B2 (ja) 2017-04-26
JPWO2013186839A1 (ja) 2016-02-01

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