WO2023243665A1 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
WO2023243665A1
WO2023243665A1 PCT/JP2023/022105 JP2023022105W WO2023243665A1 WO 2023243665 A1 WO2023243665 A1 WO 2023243665A1 JP 2023022105 W JP2023022105 W JP 2023022105W WO 2023243665 A1 WO2023243665 A1 WO 2023243665A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring gear
oil passage
transmission oil
pressure
teeth
Prior art date
Application number
PCT/JP2023/022105
Other languages
English (en)
Japanese (ja)
Inventor
夏氷 石
孝明 大西
博昭 竹田
Original Assignee
住友精密工業株式会社
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 住友精密工業株式会社 filed Critical 住友精密工業株式会社
Priority to CN202380011294.5A priority Critical patent/CN117597515A/zh
Publication of WO2023243665A1 publication Critical patent/WO2023243665A1/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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member

Definitions

  • Patent Document 1 describes an internal gear pump (1).
  • This internal gear pump (1) has a separating element (7) (a so-called crescent).
  • the tooth tips of the internal gear (2) and the pinion (3) each abut against the separation member (7).
  • the separating member (7) also has an intermediate space (17) between the inner part (13) and the outer part (14).
  • the intermediate space (17) communicates with the pressurized region (9) of the internal gear pump (1).
  • the inner part (13) and the outer part (14) have a penetration (19).
  • the penetration part (19) radially penetrates each of the inner part (13) and the outer part (14), and extends the intermediate part (17) into the space between the teeth of the pinion (3) and the internal gear (2). communicate with.
  • the intermediate space (17) is at the same pressure as the pressurized area (9), so that through the penetration (19), between the teeth of the pinion (3) and the internal gear (2)
  • the pressure in the space increases.
  • the high pressure in the space between the teeth suppresses sudden pressure changes at the pump discharge and suppresses the noise of the internal gear pump (1).
  • the technology disclosed herein achieves both noise suppression of an internal gear pump and suppression of a decrease in pump efficiency.
  • the internal gear pump (1) described in Patent Document 1 has a structure in which a crescent moves.
  • internal gear pumps are known which have a non-movable crescent.
  • the space between the teeth of the ring gear is a space sandwiched between adjacent teeth of the ring gear.
  • the pressure in the space between the pinion gear teeth is high even without a pressure transmission oil path. Also on the pinion gear side, rapid pressure changes at the discharge port are suppressed.
  • the pressure transmission oil passage promotes leakage flow of the internal gear pump, but the pressure transmission oil passage is formed only in the area on the ring gear side and not in the area on the pinion gear side. Increase in leakage flow from the internal gear pump is suppressed. Therefore, a decrease in pump efficiency is suppressed.
  • the internal gear pump described above achieves both noise suppression and reduction in pump efficiency.
  • the housing has a sliding surface on which the outer peripheral surface of the ring gear slides
  • the internal gear pump includes a high-pressure oil supply section that supplies high-pressure hydraulic oil between the outer peripheral surface and the sliding surface through an inlet opening to the sliding surface,
  • the introduction port may be located on the opposite side of the crescent across the ring gear.
  • the high-pressure oil supply section supplies high-pressure hydraulic oil between the outer peripheral surface of the ring gear and the sliding surface of the housing.
  • the supplied high-pressure hydraulic oil pushes the ring gear toward the ring gear rotation axis. Since the introduction port is located on the opposite side of the crescent across the ring gear, the internal teeth of the ring gear are pressed against the second arcuate wall of the crescent. Leakage of hydraulic oil from between the internal teeth and the second arcuate wall is suppressed.
  • the high pressure oil supply increases the pumping efficiency of the internal gear pump.
  • the internal teeth of the ring gear are pressed against the second circular arc wall of the crescent, which increases pump efficiency while suppressing the pressure increase in the space between the teeth of the ring gear due to leakage flow from the discharge port.
  • the low pressure in the space between the ring gear teeth increases the noise of the internal gear pump.
  • the internal gear pump described above has a pressure transmission oil passage formed in the housing in the region on the ring gear side.
  • the pressure transmission oil passage increases the pressure in the space between the teeth of the ring gear.
  • the combination of the high-pressure oil supply section and the pressure transmission oil passage on the ring gear side achieves both a high level of noise suppression of the internal gear pump and suppression of reduction in pump efficiency.
  • the housing has a first support surface and a second support surface that respectively support two side surfaces of the ring gear that are orthogonal to the rotation axis,
  • the discharge port is formed on each of the first support surface and the second support surface,
  • the pressure transmission oil passage is formed to be recessed from the first support surface, the second support surface, or the first support surface and the second support surface, The pressure transmission oil passage may overlap a space between teeth of the ring gear when viewed in the direction of the rotation axis.
  • the pressure transmission oil passage formed in the first support surface and/or the second support surface overlaps with the space between the teeth of the ring gear when viewed in the direction of the rotation axis, so Hydraulic oil can be supplied to the space.
  • Hydraulic oil can be supplied to the space.
  • the pressure in the space between the teeth of the ring gear increases.
  • the cross section of the pressure transmission oil passage formed on the first support surface and/or the second support surface may be triangular.
  • the cross section of the pressure transmission oil passage formed on the first support surface and/or the second support surface may be quadrangular.
  • the pressure transmission oil passage may be a groove formed in the first support surface and/or the second support surface.
  • the pressure transmission oil passage may be linear.
  • the pressure transmission oil passage may be curved.
  • the pressure transmission oil passage may be formed so as to be recessed from the second arcuate wall of the crescent.
  • the pressure transmission oil passage may be formed by cutting out the surface of the crescent.
  • the pressure transmission oil passage formed in the second arcuate wall of the crescent communicates with the space between the teeth of the ring gear.
  • the pressure transmission oil passage can supply hydraulic oil from the discharge port to the space between the teeth of the ring gear. The pressure in the space between the teeth of the ring gear increases.
  • the depth of the pressure transmission oil passage may become gradually shallower as it moves away from the discharge port.
  • the depth of the pressure transmission oil passage may be a constant depth.
  • the width of the pressure transmission oil passage may be gradually narrowed away from the discharge port.
  • the width of the pressure transmission oil passage may be a constant width.
  • the tip of the pressure transmission oil passage is formed at the crescent, which extends from the edge of the discharge port at an angle ⁇ 1 or more corresponding to the tooth width of the ring gear, with the rotation axis of the ring gear as the center, and extends from the discharge port to the suction port. It may be located within a range of angle ⁇ 2 or less to an intermediate position.
  • a pressure transmission oil path with an appropriate length can suppress both the noise of the internal gear pump and the reduction in pump efficiency.
  • the pressure transmission oil passage is too short. That is, a pressure transmission oil passage that is too short cannot increase the pressure in the space between the teeth of the ring gear before the space is opened to the discharge port.
  • the internal gear pump described above can both suppress noise and suppress a decrease in pump efficiency.
  • FIG. 1 is an exploded view of an internal gear pump.
  • FIG. 2 is a cross-sectional view of the internal gear pump.
  • FIG. 3 illustrates a pressure transmission oil passage.
  • FIG. 4 shows a modification of the pressure transmission oil passage.
  • FIG. 5 shows a modification of the pressure transmission oil passage.
  • FIG. 1 and 2 illustrate an internal gear pump 1.
  • the internal gear pump 1 includes a shaft 2, a pinion gear 3, a ring gear 4, a gear housing 5, and a front cover 6.
  • the gear housing 5 and the front cover 6 constitute a housing 10 of the internal gear pump 1.
  • FIG. 1 is an exploded view in which the front cover 6 is removed from the gear housing 5.
  • the pinion gear 3 is integrally formed at an intermediate position of the first shaft 21.
  • the pinion gear 3 and the shaft 2 are coaxial.
  • the pinion gear 3 rotates together with the shaft 2.
  • the pinion gear 3 has external teeth 31.
  • the ring gear 4 meshes with the pinion gear 3.
  • the ring gear 4 is arranged eccentrically with respect to the shaft 2.
  • C1 in FIG. 1 is the rotation axis of the pinion gear 3
  • C2 is the rotation axis of the ring gear 4.
  • Internal teeth 41 are formed on the inner peripheral surface of the ring gear 4.
  • a portion of the external teeth 31 of the pinion gear 3 meshes with a portion of the internal teeth 41 of the ring gear 4 in the region on the right side of the paper.
  • the gear housing 5 accommodates the pinion gear 3 and ring gear 4.
  • the gear housing 5 has an inner hole 53 formed therein. The end of the first shaft 21 is located within the inner bore 53.
  • a support hole 62 through which the shaft 2 passes is formed through the front cover 6.
  • the shaft 2 is rotatably supported by the front cover 6 and the gear housing 5 via a bearing 63 and a bearing member 64.
  • the opening of the support hole 62 is closed by a sealing member 621.
  • a discharge port 12 is also formed in the front cover 6 and the gear housing 5.
  • the discharge port 12 is a port that discharges hydraulic oil from the space 50 inside the housing 10.
  • the outlet of the discharge port 12 is open to the outer peripheral surface of the gear housing 5, as shown in FIG. Note that the direction of the inlet of the suction port 11 and the direction of the outlet of the discharge port 12 may be different directions as illustrated in FIG. 2, or may be the same direction although not shown. .
  • the inlet of the discharge port 12 opens on the second support surface 61 of the front cover 6 and the first support surface 52 of the gear housing 5, respectively. As shown in FIG. 1, the inlet of the discharge port 12 also extends in the circumferential direction along the rotational direction of the shaft 2 on the opposite side of the shaft 2 from the suction port 11.
  • the crescent 54 extends in the circumferential direction over a predetermined angular range along the rotational direction of the shaft 2. As shown in FIG. 1, the crescent 54 has a crescent shape when viewed in the axial direction of the shaft 2.
  • the crescent 54 has two arc walls, a first arc wall 541 and a second arc wall 542, and the first arc wall 541 and the second arc wall 542 are respectively attached to the first support surface 52 of the gear housing 5. It is erected.
  • the internal gear pump 1 includes a high-pressure oil supply section 8.
  • the high-pressure oil supply section 8 supplies high-pressure hydraulic oil between the outer peripheral surface 42 of the ring gear 4 and the sliding surface 51 of the gear housing 5. Note that the high-pressure oil supply section 8 is illustrated only in FIG. 1.
  • the high-pressure oil supply unit 8 uses high-pressure hydraulic oil to push and move the ring gear 4 from the outer periphery of the third region toward the rotation axis C2. Since the tooth tips of the ring gear 4 are pressed against the second arcuate wall 542 of the crescent 54, leakage of hydraulic oil from the high pressure side to the low pressure side within the housing 10 is suppressed.
  • the high-pressure oil supply section 8 has an inlet 81 that opens to the sliding surface 51 and a supply path 82 that connects the discharge port 12 and the inlet 81.
  • the introduction port 81 is located in the third region, as shown in FIG. More specifically, the introduction port 81 faces the crescent 54 in the radial direction with the ring gear 4 interposed therebetween.
  • the inlet 81 introduces a portion of the high-pressure hydraulic oil discharged from the discharge port 12 into the housing 10 .
  • the introduction port 81 is preferably located at a position facing the crescent 54.
  • the inlet 81 has a third region that is divided into a low-pressure side region and a high-pressure side region. In the region, it is preferably located in a region on the high pressure side.
  • the pressure transmission oil passage 91 is a groove formed in the second support surface 61. As shown in FIG. 3, the cross-sectional shape of the pressure transmission oil passage 91 is triangular. Note that the cross-sectional shape of the pressure transmission oil passage 91 is not limited to a triangle. The shape of the cross section may be, for example, a quadrangle.
  • the pressure transmission oil passage 91 is formed in the housing only in the area on the ring gear 4 side, and no pressure transmission oil passage is formed in the area on the pinion gear 3 side. Both noise suppression of the internal gear pump 1 and improvement of pump efficiency are achieved.
  • the pressure transmission oil passage 91 has the function of increasing the pressure in the space between the teeth of the ring gear 4 before the space communicates with the discharge port 12. If the pressure transmission oil passage 91 is too short, it is difficult to increase the pressure in the space between the teeth of the ring gear 4 before the space communicates with the discharge port 12. There is a minimum length of the pressure transmission oil passage 91 for the pressure transmission oil passage 91 to perform its function.
  • the intermediate position of the crescent 54 is the intermediate position in the circumferential direction of the crescent 54 that extends in the circumferential direction from the discharge port 12 to the suction port 11. Since the pressure transmission oil passage 91 is not too long, the pressure in the space between the teeth of the ring gear 4 can be sufficiently increased, and an increase in leakage flow can be suppressed.
  • the pressure transmission oil passage 91 is formed on the second support surface 61 of the front cover 6.
  • the pressure transmission oil passage 91 may be formed to be recessed from the first support surface 52 of the gear housing 5.
  • the pressure transmission oil passage 91 may be formed on each of the second support surface 61 of the front cover 6 and the first support surface 52 of the gear housing 5.
  • the pressure transmission oil passage 92 extends in an arc shape along the curve of the second arc wall 542 of the crescent 54. When viewed in the direction of the rotation axis C2 of the ring gear 4, the pressure transmission oil passage 92 overlaps the space between the teeth of the ring gear 4. The pressure transmission oil passage 92 communicates with the space between the teeth of the ring gear 4. Since the pressure in the space between the teeth of the ring gear 4 increases in the third region, when the space is opened to the discharge port 12, the pressure difference between the pressure in the discharge port 12 and the pressure in the space between the teeth is small. . The noise of the internal gear pump 1 is suppressed.
  • FIG. 5 is a perspective view of the internal gear pump 1 with the front cover 6 removed. This internal gear pump 1 has a pressure transmission oil passage 93 formed in the crescent 54.
  • the pressure transmission oil passage 93 is formed at the upper end of the second arcuate wall 542 of the crescent 54.
  • the pressure transmission oil passage 93 is formed by cutting out the surface of the crescent 54. Note that the upper end here is the end of the crescent 54 that stands up from the first support surface 52 of the gear housing 5 on the opposite side to the first support surface 52 .
  • the upper end of the second arcuate wall 542 is the end that comes into contact with the second support surface 61 of the front cover 6 .
  • the pressure transmission oil passage 93 extends from the high-pressure side end of the crescent 54 (that is, the left end in FIG. 5) to an intermediate position of the crescent 54.
  • the pressure transmission oil passage 93 communicates with the discharge port 12 that opens into the second support surface 61 of the front cover 6 .
  • the length of the pressure transmission oil passage 93 can be set arbitrarily within the above-mentioned range of ⁇ 1 or more and ⁇ 2 or less.
  • the pressure transmission oil passage 93 has a width/depth that gradually becomes narrower/shallower as it moves away from the discharge port 12.
  • the width/depth of the pressure transmission oil passage 93 may be constant.
  • the pressure transmission oil passage 93 formed in the crescent 54 also communicates the space between the teeth of the ring gear 4 and the discharge port 12. Since the pressure in the space between the teeth of the ring gear 4 increases in the third region, when the space is opened to the discharge port 12, the pressure difference between the pressure in the discharge port 12 and the pressure in the space between the teeth is small. . Since pressure fluctuations are suppressed, the noise of the internal gear pump 1 is suppressed.
  • pressure transmission oil passage formed in the crescent 54 is not limited to being formed at the upper end of the crescent 54.
  • the pressure transmission oil passage may be formed at an intermediate position in the vertical direction on the second arcuate wall 542 of the crescent 54.
  • a pressure transmission oil passage may be formed at the lower end of the crescent 54.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une pompe à engrenages internes (1) qui comprend un pignon d'engrenage (3), une couronne (4), un boîtier (10), et un croissant (54) ayant une première paroi arquée (541) avec laquelle des dents externes (31) viennent en contact, et une seconde paroi arquée (542) avec laquelle des dents internes (41) viennent en contact, la première paroi arquée et la seconde paroi arquée étant toutes deux des parois fixes qui ne se déplacent pas vers les dents externes ou les dents internes ; un passage d'huile de transmission de pression (91) s'étendant à partir d'un orifice d'évacuation est formé à l'intérieur du boîtier, dans uniquement une région latérale de couronne entre une région latérale de pignon d'engrenage et la région latérale de couronne, qui prennent en sandwich le croissant ; et le passage d'huile de transmission de pression fournit une communication entre l'orifice d'évacuation et un espace entre les dents de la couronne.
PCT/JP2023/022105 2022-06-16 2023-06-14 Pompe à engrenages internes WO2023243665A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202380011294.5A CN117597515A (zh) 2022-06-16 2023-06-14 内啮合齿轮泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022097648A JP2023183867A (ja) 2022-06-16 2022-06-16 内接ギヤポンプ
JP2022-097648 2022-06-16

Publications (1)

Publication Number Publication Date
WO2023243665A1 true WO2023243665A1 (fr) 2023-12-21

Family

ID=89191402

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2023/022105 WO2023243665A1 (fr) 2022-06-16 2023-06-14 Pompe à engrenages internes

Country Status (3)

Country Link
JP (1) JP2023183867A (fr)
CN (1) CN117597515A (fr)
WO (1) WO2023243665A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1553014A1 (de) * 1963-03-04 1969-08-21 Otto Eckerle Einrichtung an Pumpen zur Verminderung der Geraeuschentwicklung
JPH04203373A (ja) * 1990-11-29 1992-07-23 Shimadzu Corp 内接歯車ポンプ又はモータ
JPH11229802A (ja) * 1997-12-03 1999-08-24 Luk Getriebe Syst Gmbh ハイドロリック式の歯車機械

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1553014A1 (de) * 1963-03-04 1969-08-21 Otto Eckerle Einrichtung an Pumpen zur Verminderung der Geraeuschentwicklung
JPH04203373A (ja) * 1990-11-29 1992-07-23 Shimadzu Corp 内接歯車ポンプ又はモータ
JPH11229802A (ja) * 1997-12-03 1999-08-24 Luk Getriebe Syst Gmbh ハイドロリック式の歯車機械

Also Published As

Publication number Publication date
JP2023183867A (ja) 2023-12-28
CN117597515A (zh) 2024-02-23

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