WO2010095505A1 - Pompe à engrenage intérieur - Google Patents

Pompe à engrenage intérieur Download PDF

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Publication number
WO2010095505A1
WO2010095505A1 PCT/JP2010/051351 JP2010051351W WO2010095505A1 WO 2010095505 A1 WO2010095505 A1 WO 2010095505A1 JP 2010051351 W JP2010051351 W JP 2010051351W WO 2010095505 A1 WO2010095505 A1 WO 2010095505A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
housing
peripheral surface
outer gear
oil groove
Prior art date
Application number
PCT/JP2010/051351
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English (en)
Japanese (ja)
Inventor
正一 八木
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
Publication of WO2010095505A1 publication Critical patent/WO2010095505A1/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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • 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
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C15/0088—Lubrication
    • 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
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber

Definitions

  • the present invention relates to an internal gear pump used for pressurizing hydraulic oil for driving an actuator such as a cylinder.
  • FIGS. 6 (a) and 6 (b) are widely used for pressurizing hydraulic oil to drive various actuators such as cylinders.
  • the structure of this internal gear pump is described in detail in Patent Documents 1 and 2, for example.
  • the basic structure of the internal gear pump will be described with reference to FIGS. 6 (a) and 6 (b).
  • 6A is a longitudinal sectional view of the shaft
  • FIG. 6B is a transverse sectional view of the shaft, and is a view taken along the line U-U in FIG. 6A.
  • This pump has an inner gear 3 and an outer gear 4 combined in the housing 1.
  • the inner gear 3 is an external gear, and is rotationally driven by a rotating shaft 2 that penetrates the center of the housing.
  • the outer gear 4 is an annular internal gear that is rotatably accommodated in the housing 1, and is eccentrically disposed outside the inner gear 3, thereby meshing with the inner gear 3 in a part in the circumferential direction.
  • an arcuate space is formed between the tooth surfaces.
  • an arcuate partition piece 5 called a crescent is provided integrally with the housing 1.
  • a suction port 6 is provided on the upstream side in the rotation direction of the partition piece 5, and a discharge port 7 is provided on the downstream side in the rotation direction.
  • the suction port 6 and the discharge port 7 are opened on one inner surface of the gear housing portion in the housing 1 so as to face each other between the gears 3 and 4 from the side.
  • Concave portions 8 and 9 corresponding to the suction port 6 and the discharge port 7 are formed on the other inner surface.
  • the outer gear 4 When the drive shaft 2 is driven by a motor (not shown) and the inner gear 3 rotates, the outer gear 4 also rotates synchronously at a fixed position. Due to the eccentricity of the outer gear 4, the hydraulic oil is sucked in between the gears 3 and 4 from the suction port 6 on the upstream side in the rotational direction, divided into the inner peripheral side and the outer peripheral side of the partition piece 5, and the discharge port on the downstream side in the rotational direction 7 is discharged. That is, the working oil is sucked from the suction port 6 by gradually separating the teeth of the two gears 3 and 4 on the upstream side in the rotational direction of the partition piece 5, and the two gears 3 and 4 on the upstream side in the rotational direction of the partition piece 5. As the distance between the teeth gradually approaches, the hydraulic oil is pressurized and discharged from the discharge port 7.
  • FIG. 6B shows a circumferential distribution of the radial pressure generated between the outer peripheral surface 4a of the rotating outer gear 4 and the inner peripheral surface 1a of the gear housing portion in the housing 1.
  • the lubrication in the internal gear pump is such that part of the sucked hydraulic oil passes through minute gaps between the gears 3 and 4 and the inner side surfaces 1b and 1b on both sides of the gear housing portion in the housing 1, and part of the housing is in the housing. 1 and the rotating shaft 2, the remainder is performed by entering between the outer peripheral surface 4 a of the outer gear 4 and the inner peripheral surface 1 a of the gear housing portion in the housing 1. Less hydraulic oil enters between the inner peripheral surface 1a of the housing 1 and particularly in the vicinity of the discharge region where the radial pressure is high. For these reasons, oil shortage is likely to occur at the sliding portion of the outer gear 4, and seizure is likely to occur on the outer peripheral surface 4 a of the outer gear 4.
  • the suction port 6 is extended between the outer peripheral surface 4a of the outer gear 4 and the inner peripheral surface 1a of the gear housing portion in the housing 1. Increasing the amount of hydraulic oil supplied during this period is being carried out.
  • the oil passage with a valve that guides the hydraulic oil pressurized in the discharge region between the outer peripheral surface 4a of the outer gear 4 and the inner peripheral surface 1a of the housing 1 is provided in the housing. 1 is performed.
  • An object of the present invention is to provide an internal gear pump that can stably and economically prevent seizure of the outer peripheral surface of the outer gear even when operation and stop are frequently repeated.
  • the present inventors have planned to clarify the detailed cause of seizure of the outer peripheral surface of the outer gear, and the pressure acting on the outer gear includes the tendency of pressure rise at the start of operation.
  • Each part was investigated.
  • there is a difference in oil pressure on both sides of the outer gear the difference being large in the vicinity of the discharge region and large during low-speed rotation at the start of operation, and pulsation in one of the oil pressures on both sides in the vicinity of the discharge region.
  • the follow-up performance of the hydraulic pressure is poor, especially in the vicinity of the discharge area on the outer peripheral side of the outer gear during low-speed rotation at the start of operation.
  • the present inventor believes that if these phenomena can be mitigated, seizure of the outer peripheral surface of the outer gear can be reduced, and as a technique for this, an oil groove in the direction of the rotation axis is provided on the inner peripheral surface of the gear housing portion in the housing, We planned to balance the pressure by connecting both sides, and investigated in detail the relationship between the oil groove formation position and the effect in the vicinity of the discharge area. As a result, it has become clear that it is effective to form at the downstream part in the rotation direction of the discharge region, and further, it is effective to form at the upstream part in the rotation direction of the discharge region.
  • the internal gear pump of the present invention has been completed on the basis of such knowledge, and is rotatably accommodated in the housing together with the inner gear to be rotated and the inner gear so as to mesh with a part of the inner gear.
  • the outer gear arranged in the center and the arc-shaped partition piece provided between the two gears located in the non-engagement region of both gears, and located on the upstream side of the partition piece, the suction port on the inner surface of the housing
  • the outer gear is disposed on the downstream side of the discharge region of the inner peripheral surface of the housing where the outer peripheral surface of the outer gear slides. Oil grooves are provided to allow communication between the both side surfaces.
  • another oil groove for communicating the both side surfaces of the outer gear is also provided at the upstream side of the discharge area of the inner peripheral surface of the housing where the outer peripheral surface of the outer gear is in sliding contact.
  • Any oil groove is preferably configured to communicate with the discharge region via a recess provided on the inner surface of the gear housing portion in the housing.
  • an oil groove that communicates both side surfaces of the outer gear is provided on the inner peripheral surface of the housing in the vicinity of the discharge region where the outer gear receives strong pressure, so that the rotation speed increase period at the start of operation
  • the pressure balance on both sides of the outer gear is balanced and the amount of oil supplied to the outer peripheral side of the outer gear is increased, so that the outer gear is smoothly rotated and lubricated, and seizure of the outer peripheral surface of the outer gear is prevented.
  • this oil groove on the downstream side of the discharge area on the inner peripheral surface of the housing, the follow-up performance of the oil pressure on the closing side of the discharge area is improved and the pulsation is improved when the rotational speed is increased at the start of operation. Is prevented. If this oil groove is provided also in the upstream portion of the discharge area on the inner peripheral surface of the housing, the follow-up performance of the oil pressure on the outer peripheral side of the discharge area is improved when the rotational speed is increased at the start of operation. Both lead to smooth rotation of the outer gear and contribute to improvement of seizure resistance.
  • an oil groove is provided on the inner peripheral surface of the housing to connect the both side surfaces of the outer gear. Since the pressure balance on both sides of the outer gear is balanced and the amount of oil supplied to the outer peripheral side of the outer gear increases, rotation and lubrication of the outer gear can be facilitated and seizure resistance of the outer peripheral surface of the outer gear can be improved. Can do.
  • FIG. 5 is a longitudinal sectional view of an internal gear pump showing an embodiment of the present invention, and corresponds to a view taken along line SS in FIG. 3.
  • FIG. 5 is a longitudinal sectional view of the internal gear pump, corresponding to the TT line arrow diagram in FIG. 3. It is a side view of the housing main body in the internal gear pump. It is the graph which showed the pressure fluctuation of the outer gear both sides in the X point position and Y point position in FIG. 3 about the case where there is no oil groove, and the case where it exists in a discharge zone downstream part.
  • FIG. 3 is a graph showing pressure fluctuations at point A, point B, and point C in FIG.
  • the internal gear pump of the present embodiment is located in a housing 10 that houses a gear unit, a rotary shaft 20 that penetrates the center of the housing 10, and an outer side of the rotary shaft 20.
  • An inner gear 30 and an outer gear 40 accommodated in the housing 10 are provided.
  • the housing 10 includes a main body 10A that houses the inner gear 30 and the outer gear 40, and a cover 10B that closes an opening of the main body 10A.
  • the main body 10A is provided with an eccentric circular gear housing portion 11 into which the outer gear 40 is rotatably fitted.
  • a shaft hole through which the rotary shaft 20 is rotatably passed is provided at the center of the main body 10A, and a similar shaft hole is also provided at the center of the cover 10B.
  • the inner gear 30 is an external gear and is concentrically connected to the rotary shaft 20 in the gear housing portion 11 of the main body 10A.
  • the outer gear 40 is an internal gear that is rotatably accommodated in the gear accommodating portion 11 that is eccentric with respect to the rotating shaft 20, and meshes with the inner gear 30 in a part of the circumferential direction.
  • An arcuate partitioning piece 12 called a crescent is integrally provided with the main body 10A on the opposite meshing side opposite to the meshing side.
  • the partition piece 12 is disposed between the inner gear 30 and the outer gear 40, and the upstream side in the rotation direction is the suction area IN and the downstream side is the discharge area OUT.
  • the suction area IN exists in an arc shape along the rotation direction, and the height gradually increases from the upstream side to the downstream side in the rotation direction.
  • the discharge area OUT also exists along the rotation direction, and the height gradually decreases from the upstream side to the downstream side in the rotation direction.
  • the cover 10B of the housing 10 is provided with an arcuate suction port 13 and the main body 10A is provided with an arcuate recess 14 so as to face the suction area IN from the side.
  • the main body 10A of the housing 10 is provided with an arc-shaped discharge port 15 and the cover 10B is provided with an arc-shaped recess 16 so as to face the discharge area OUT from the side.
  • the first oil groove 17 a is a U-shaped groove having a cross-sectional arc located at the downstream portion in the rotation direction of the discharge region OUT, and an end portion on the main body side is one inner surface of the gear housing portion 11 (of the gear housing portion 11. It communicates with the downstream end in the rotational direction of the discharge port 15 via a connecting circular recess 18a provided on the bottom surface.
  • the end of the oil groove 17a on the cover side of the arc-shaped recess 16 corresponding to the discharge port 15 is connected via a circular recess 18b for connection provided on the other inner surface (the surface of the cover 10B) of the gear housing portion 11. It communicates with the downstream end portion in the rotational direction.
  • the second oil groove 17b is a U-shaped groove having an arc-shaped cross section located in the upstream portion in the rotation direction of the discharge area OUT, and the end on the main body side is one inner side surface of the gear housing portion 11 (the gear housing portion 12). It communicates with the upstream end in the rotational direction of the discharge port 15 via a connecting circular recess 19a provided on the bottom surface.
  • the end of the oil groove 17b on the cover side of the arc-shaped recess 16 corresponding to the discharge port 15 is connected to a circular recess 19b for connection provided on the other inner surface (the surface of the cover 10B) of the gear housing portion 11. It communicates with the upstream end in the rotational direction.
  • the rotary shaft 20 is rotationally driven by a motor (not shown). Accordingly, hydraulic oil is sucked between the inner gear 30 and the outer gear 40 in the gear housing portion 11 from the arc-shaped suction port 13 provided on the cover 10B side corresponding to the suction area IN in the housing 10. It is.
  • the hydraulic oil sucked into the gear housing portion 11 is divided into an inner peripheral side and an outer peripheral side of the partition piece 12, and is discharged from an arc-shaped discharge port 14 provided on the main body 10A side corresponding to the discharge region OUT.
  • the working oil is sucked by the gradual separation between the teeth of the inner gear 30 and the outer gear 40, and the position on the downstream side in the rotation direction of the partition piece 12.
  • the hydraulic oil is pressurized as the teeth between the inner gear 30 and the outer gear 40 gradually approach each other.
  • a part of the hydraulic oil sucked into the housing 10 passes through a minute gap between both side surfaces of the outer gear 40 and both inner side surfaces of the gear housing portion 11, a part is toward the rotation center side, and the rest is the outer periphery. Invade each side.
  • the former is lubrication between the housing 10 and the rotary shaft 20, more specifically, a sleeve-like bearing member 50 fitted and fixed to the shaft hole in each central portion of the main body 10A and the cover 10B of the housing 10. , 50 and the outer peripheral surface of the rotary shaft 20, and the latter lubrication of the sliding portion between the outer peripheral surface 41 of the outer gear 40 and the inner peripheral surface 11 a of the gear housing 11. Used respectively.
  • the discharge port 15 exists only on one side (the side of the main body 10A) of the discharge area OUT in the housing 10. That is, the discharge area OUT is open on one side (the main body 10A side) and closed on the opposite side (the cover 10B side). Further, the radial hydraulic pressure between the outer peripheral surface 41 of the outer gear 40 and the inner peripheral surface 11a of the gear housing portion 11 with which the outer gear 40 is in sliding contact is maximized in the discharge region OUT (see FIG. 6B). For these reasons, in the discharge area OUT, the outer gear 40 receives a strong pressure in the lateral direction (rotational axis direction) from the cover 10B side that is the closing side toward the main body 10A that is the opening side. Needless to say, it causes seizure of the gear 40.
  • oil grooves 17a and 17b in the rotation axis direction are provided on the inner peripheral surface 11a on the outer peripheral side of the discharge region OUT in the gear housing portion 11.
  • the first oil groove 17a is in the downstream portion of the discharge area OUT, and communicates with the discharge port 15 and the arc-shaped recess 16 of the discharge area OUT via the connecting circular recesses 18a and 18b on both sides.
  • the second oil groove 17b is in the upstream portion of the discharge region OUT and communicates with the discharge port 15 and the arc-shaped recess 16 in the discharge region OUT via the circular recesses 19a and 19b for connection on both sides.
  • the main body side which is the open side is lower in pressure at the X side and the Y point than the cover side which is the closed side.
  • the followability to the increase in the rotational speed at the start of operation is poor, and a relatively large pulsation is seen at the point X on the upstream side in the rotational direction [FIG. a)].
  • the first oil groove 17a is also provided.
  • the seizure resistance equivalent to that of the case of only was exhibited.
  • the specifications of the internal gear pump used for the seizure resistance test are as follows.
  • the internal gear pump used for the investigations in FIGS. 4A and 4B is of the same type.
  • the results shown in FIGS. 4 (a) and 4 (b) are pressure changes at various points when the discharge pressure is suddenly changed from unloading to on-loading. went.
  • the depth of the oil grooves 17a, 17b and the circular recesses 18a, 18b, 19a, 19b is too shallow to secure a sufficient volume for pressure oil propagation. Within the range, both were set to 2.0 mm in the test.
  • the oil grooves 17a and 17b are U-grooves, they may be concave grooves and their cross-sectional shapes are not limited.
  • the circular recesses 18a, 18b, 19a, 19b for connection need not be circular, and may be straight grooves.
  • SYMBOLS 10 Housing 10A Main body 10B Cover 11 Gear accommodating part 11a Inner peripheral surface 12 Partition piece (Crescent) DESCRIPTION OF SYMBOLS 13 Suction port 14,16 Arc-shaped recessed part 15 Discharge port 17a, 17b Oil groove 18a, 18b, 19a, 19b Circular recessed part for connection 20 Rotating shaft 30 Inner gear 40 Outer gear 50 Bearing member

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

Abstract

L'invention concerne une pompe à engrenage intérieur présentant une excellente résistance au grippage. Un engrenage intérieur (30) entraîné par un arbre tournant (20) et un engrenage extérieur (40) sont logés dans un boîtier (10). L'engrenage extérieur (40) faisant fonction de roue à denture intérieure est excentrique par rapport à l'arbre tournant (20) et la partie circonférentielle de l'engrenage extérieur (40) engrène partiellement avec l'engrenage intérieur (30) faisant fonction de roue à denture extérieure. Un élément de partition en arc est installé du côté opposé à l'engrènement. Le côté amont de l'élément de partition dans le sens de rotation est défini comme une zone d'admission et le côté aval de l'élément de partition dans le sens de rotation est défini comme une zone de refoulement. La surface périphérique extérieure de l'engrenage extérieur (40) est en contact de glissement avec la surface périphérique intérieure d'une partie de logement d'engrenage à l'intérieur du boîtier (10). Des rainures (17a, 17b) d'huile sont aménagées le long de l'arbre tournant dans la surface périphérique intérieure de la partie de logement d'engrenage, de telle sorte que les faces latérales opposées de l'engrenage extérieur (20) soient en communication l'une avec l'autre. La première rainure (17a) d'huile est disposée dans la partie aval de la zone de refoulement et la deuxième rainure (17b) d'huile est disposée dans la partie amont de la zone de refoulement.
PCT/JP2010/051351 2009-02-20 2010-02-01 Pompe à engrenage intérieur WO2010095505A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-037350 2009-02-20
JP2009037350A JP2010190161A (ja) 2009-02-20 2009-02-20 内接ギヤポンプ

Publications (1)

Publication Number Publication Date
WO2010095505A1 true WO2010095505A1 (fr) 2010-08-26

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113217587A (zh) * 2021-06-02 2021-08-06 田应雄 变径齿轮无级变速器
WO2022018023A1 (fr) * 2020-07-24 2022-01-27 Eckerle Technologies GmbH Machine à fluide à engrenage interne
WO2022018022A1 (fr) * 2020-07-24 2022-01-27 Eckerle Technologies GmbH Machine à fluide à engrenage interne

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101230044B1 (ko) 2011-10-07 2013-02-05 주식회사 코아비스 지로터 펌프
US10480507B2 (en) * 2016-09-01 2019-11-19 GM Global Technology Operations LLC Gerotor assembly having an oil groove

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5491706U (fr) * 1977-12-13 1979-06-28
JPH0317188U (fr) * 1989-06-28 1991-02-20
JP2000355274A (ja) * 1998-10-06 2000-12-26 Denso Corp 回転式ポンプ及び回転式ポンプを備えたブレーキ装置
JP2007023975A (ja) * 2005-07-20 2007-02-01 Equos Research Co Ltd ギヤ式のオイルポンプ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5491706U (fr) * 1977-12-13 1979-06-28
JPH0317188U (fr) * 1989-06-28 1991-02-20
JP2000355274A (ja) * 1998-10-06 2000-12-26 Denso Corp 回転式ポンプ及び回転式ポンプを備えたブレーキ装置
JP2007023975A (ja) * 2005-07-20 2007-02-01 Equos Research Co Ltd ギヤ式のオイルポンプ

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022018023A1 (fr) * 2020-07-24 2022-01-27 Eckerle Technologies GmbH Machine à fluide à engrenage interne
WO2022018022A1 (fr) * 2020-07-24 2022-01-27 Eckerle Technologies GmbH Machine à fluide à engrenage interne
CN116209830A (zh) * 2020-07-24 2023-06-02 艾可勒科技公司 内齿轮流体机械
US11971033B2 (en) 2020-07-24 2024-04-30 Eckerle Technologies GmbH Internal gear fluid machine
CN113217587A (zh) * 2021-06-02 2021-08-06 田应雄 变径齿轮无级变速器

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