WO2016121291A1 - Pompe à engrenages et son procédé de fabrication - Google Patents

Pompe à engrenages et son procédé de fabrication Download PDF

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Publication number
WO2016121291A1
WO2016121291A1 PCT/JP2015/086533 JP2015086533W WO2016121291A1 WO 2016121291 A1 WO2016121291 A1 WO 2016121291A1 JP 2015086533 W JP2015086533 W JP 2015086533W WO 2016121291 A1 WO2016121291 A1 WO 2016121291A1
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WO
WIPO (PCT)
Prior art keywords
tooth
teeth
inner rotor
gear pump
clearance
Prior art date
Application number
PCT/JP2015/086533
Other languages
English (en)
Japanese (ja)
Inventor
雅幸 木村
雅士 服部
光博 武田
Original Assignee
アイシン機工株式会社
アイシン・エィ・ダブリュ株式会社
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 アイシン機工株式会社, アイシン・エィ・ダブリュ株式会社 filed Critical アイシン機工株式会社
Priority to US15/543,624 priority Critical patent/US20170370359A1/en
Priority to JP2016571829A priority patent/JP6343355B2/ja
Priority to CN201580074754.4A priority patent/CN107208627B/zh
Priority to DE112015006082.0T priority patent/DE112015006082T5/de
Publication of WO2016121291A1 publication Critical patent/WO2016121291A1/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
    • F04C2/102—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 the two members rotating simultaneously around their respective axes
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • 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
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor

Definitions

  • the present disclosure relates to a gear pump including an inner rotor having a plurality of external teeth and an outer rotor having a plurality of internal teeth and arranged to be eccentric with respect to the inner rotor, and a method for manufacturing the same.
  • a gear pump As a gear pump, one of the pump chambers defined by the external teeth of the external gear and the internal teeth of the internal gear communicates with a pump chamber (interdental chamber) whose volume is increased by the rotation of both gears.
  • a pump chamber internal chamber
  • One having a suction port and two discharge ports communicating with a pump chamber whose volume is reduced by the rotation of both gears is known (for example, see Patent Document 1).
  • This gear pump has a minimum clearance of 0.020 mm or more between the external teeth and the internal teeth located on the partition wall that divides the two discharge ports in a state where the external gear and the internal gear are pressed in opposite directions in the radial direction. And it is designed to be 0.110 mm or less.
  • the pump chamber communicating with one discharge port on the high pressure side and the other on the low pressure side It would be possible to improve the volumetric efficiency of the pump by reducing the leakage of hydraulic oil to the pump chamber communicating with the discharge port.
  • the minimum clearance between the external teeth and the internal teeth located on the partition wall is reduced, cavitation occurs when fluid flows into the pump chamber communicating with the suction port, thereby reducing volumetric efficiency. There is a risk of noise or vibration.
  • the main object of the present disclosure is to provide a gear pump that can suppress the occurrence of cavitation while improving volumetric efficiency, and a method for manufacturing the same.
  • a gear pump of the present disclosure includes an inner rotor having a plurality of external teeth, an outer rotor having a plurality of internal teeth larger than the external teeth of the inner rotor and arranged to be eccentric with respect to the inner rotor,
  • the gear pump including a plurality of interdental chambers defined by two adjacent external teeth and two adjacent internal teeth, the teeth whose volume increases as the inner rotor and the outer rotor rotate.
  • One suction port that communicates with the interchamber, and a first and a second that are partitioned by a partition wall and are independent of each other, and communicate with the interdental chamber that decreases in volume as the inner rotor and the outer rotor rotate.
  • the volume change amount when the inner rotor is rotated by a unit angle and communicating with the suction port is maximum.
  • the minimum clearance between the external teeth and the internal teeth defining the interdental chamber is defined as a suction side clearance, and the first and second discharge ports when the volume change amount per unit angle becomes maximum.
  • the minimum clearance between the external teeth and the internal teeth that define an interdental chamber that at least partially overlaps the partition wall is defined as a discharge side clearance
  • the suction side clearance is more than the discharge side clearance. Is also large.
  • the inner rotor communicates with the suction port and has a minimum clearance between the external teeth and the internal teeth that define the interdental space that maximizes the volume change when the inner rotor rotates by a unit angle.
  • the clearance is formed so as to be larger than the minimum clearance between the external teeth and the internal teeth that define the interdental chamber that at least partially overlaps the partition wall.
  • the flow of fluid between the first and second discharge ports is regulated to improve volumetric efficiency.
  • FIG. 1 is a schematic configuration diagram illustrating a gear pump 1 according to an embodiment of the present disclosure.
  • a gear pump 1 shown in the figure is configured as an oil pump mounted on a vehicle (not shown), for example, and sucks hydraulic oil (ATF) stored in an oil pan and pumps it to a hydraulic control device (both not shown).
  • the gear pump 1 is defined by, for example, a pump housing (both not shown) constituted by a pump body fixed to a transmission case of an automatic transmission and a pump cover fastened to the pump body, and the pump housing.
  • An inner rotor (drive gear) 2 and an outer rotor (driven gear) 3 that are rotatably arranged in a gear housing chamber (not shown).
  • the gear pump 1 may be configured as an in-vehicle pump (for example, an engine oil pump) other than an oil pump that pumps hydraulic oil for transmission, and may be applied to uses other than the in-vehicle pump.
  • the inner rotor 2 is fixed to a rotary shaft 4 connected to a crankshaft (both not shown) of an engine mounted on a vehicle, and is rotationally driven by power applied to the rotary shaft 4.
  • a plurality of (for example, 11 teeth in this embodiment) external teeth 20 are formed on the outer periphery of the inner rotor 2.
  • the number of internal teeth 30 that is one more than the total number of external teeth 20 of the inner rotor 2 (for example, 12 teeth in this embodiment) is formed.
  • the outer rotor 3 is rotatable in the gear housing chamber with a plurality of inner teeth 30 positioned on the lower side in FIG.
  • a plurality of interdental chambers (pump chambers) 5 are formed between the inner rotor 2 and the outer rotor 3 by two adjacent external teeth 20 and two adjacent internal teeth 30.
  • the outer rotor 3 has a part of the plurality of inner teeth 30 meshed with a part of the plurality of outer teeth 20.
  • the inner rotor 2 and the outer rotor 3 are rotated, in the rear region in the rotation direction of the both (see the thick arrow in FIG. 1), that is, mainly in the right half region in FIG.
  • the volume of each interdental chamber 5 increases (interdental chamber 5 expands).
  • the inner rotor 2 and the outer rotor 3 rotate, in the front region in the rotation direction of the inner rotor 2 or the like, that is, mainly the left half region in FIG.
  • the volume of the chamber 5 decreases (the interdental chamber 5 contracts).
  • the pump housing (not shown) of the gear pump 1 increases in volume as the inner rotor 2 and the outer rotor 3 among the plurality of interdental chambers 5 defined by the external teeth 20 and the internal teeth 30 rotate.
  • the volume decreases with the rotation of the suction port 6 extending in a substantially arc shape so as to communicate (oppose) with the interdental chamber 5 and the inner rotor 2 and the outer rotor 3 of the plurality of interdental chambers 5 respectively.
  • a first discharge port 7 and a second discharge port 8 extending in a substantially arc shape so as to communicate (oppose) with the interdental chamber 5 are formed.
  • the first and second discharge ports 7 and 8 are partitioned by a partition wall 9 and are independent of each other.
  • the first discharge port 7 located on the rear side in the rotation direction of the inner rotor 2 or the like is a low pressure port
  • the second discharge port 8 located on the front side in the rotation direction is a high pressure port.
  • the 1st and 2nd discharge ports 7 and 8 may be connected to a mutually different oil path, and may be connected to a common oil path.
  • the suction port 6, the first and second discharge ports 7, 8 may be formed on both sides (both the pump body and the pump cover) in the axial direction of the inner rotor 2 and the outer rotor 3,
  • the outer rotor 3 may be formed on one side (one of the pump body and the pump cover) in the axial direction.
  • the suction port 6 may be formed on one side in the axial direction of the inner rotor 2 or the like, and the first and second discharge ports 7 and 8 are formed on the other side in the axial direction of the inner rotor 2 or the like.
  • the first discharge port 7 may be formed on one side in the axial direction of the inner rotor 2 or the like
  • the second discharge port 8 may be formed on the other side in the axial direction of the inner rotor 2 or the like.
  • FIG. 2 is a schematic diagram showing a procedure for creating the inner teeth 30 of the outer rotor 3 included in the gear pump 1.
  • the tooth profile (outline) of the outer rotor 3 defined by the plurality of inner teeth 30 is a diameter 2 ⁇ e + t with the rotation center 2c of the inner rotor 2 being the center of the rotation center 3c of the outer rotor 3.
  • a plurality of tooth profile lines (inner rotors) obtained by rotating the inner rotor 2 by the rotation angle ⁇ / N when the rotation center 2c revolves by the predetermined angle ⁇ . 2 contours (refer to the two-dot chain line in FIG. 3).
  • t indicates that the rotation center 2 c of the inner rotor 2, the rotation center 3 c of the outer rotor 3, the top portion 21 t of the tooth tip portion 21 of the external tooth 20, and the top portion of the tooth tip portion of the internal tooth 30 are aligned.
  • the clearance (tip clearance) between the top 21t and the top of the internal tooth 30 is, for example, a value of about 0.03 to 0.07 mm.
  • the tooth profile (outline) of the outer rotor 3 may be the envelope itself or may be determined to be located outside the envelope.
  • the inner teeth of the outer rotor 3 may be created using a gear cutting tool having substantially the same shape as the inner rotor 2.
  • FIG. 3 is a schematic configuration diagram showing the external teeth 20 of the inner rotor 2
  • FIG. 4 is a schematic diagram showing a procedure for creating the external teeth 20.
  • each external tooth 20 of the inner rotor 2 includes a convexly curved tooth tip portion 21, a concave curved tooth bottom portion 22, and the rotational direction of the inner rotor 2 relative to the tooth tip portion 21 ( The first intermediate portion 23 located between the tooth tip portion 21 and the tooth bottom portion 22 on the front side in the thick arrow in FIG. 3, and the tooth on the rear side in the rotational direction of the inner rotor 2 relative to the tooth tip portion 21.
  • a second intermediate portion 24 located between the tip portion 21 and the tooth bottom portion 22 is included.
  • the external teeth 20 are formed asymmetrically with respect to a tooth profile center line Lc passing through the top portion 21t located on the outermost radial direction of the tooth tip portion 21 and the rotation center 2c of the inner rotor 2.
  • the tooth tip portion 21 has a trochoidal coefficient obtained by dividing the radius rde of the first drawing point by the radius re of the abduction circle Co, which is larger than 1 (for example, about 1.2). Value)
  • a convex curved surface is formed by an epitrochoid curve.
  • the epitrochoid curve forming the tooth tip portion 21 maintains the radius rde of the first drawing point at the first value Rde (constant value) and has an abduction circle Co having a radius re smaller than the first value Rde. Is rolled without slipping while circumscribing the base circle BCt having the rotation center 2c of the inner rotor 2 and the center O in common.
  • the tooth bottom portion 22 is formed in a concave curved surface by a hypotrochoidal curve having a trochoid coefficient larger than 1 obtained by dividing the radius rdh of the second drawing point by the radius rh of the inversion circle Ci.
  • the hypotrochoid curve forming the tooth bottom portion 22 is the same as the epitrochoid curve forming the tooth tip portion 21 and the basic circle BCt.
  • the radius rdh of the second drawing point is set to the first value. It is obtained by rolling an inversion circle Ci having a radius Rh smaller than the second value Rdh while keeping the value Rdh (constant value) 2 without slipping while inscribed in the basic circle BCt.
  • the tooth bottom portion 22 is a front side in the rotational direction from the tooth profile center line Lc by a half ( ⁇ / 2) of an angle ⁇ (360 ° / the number of teeth of the external teeth 20) corresponding to one tooth of the external teeth 20.
  • the first tooth bottom portion 22a located on the front side in the rotation direction of the inner rotor 2 with respect to the tooth tip portion 21 and the tooth tip portion 21 with respect to the intersection portion 22x with the line segment Le rotated rearward. It is divided into a second tooth bottom portion 22b located on the rear side in the rotation direction of the inner rotor 2.
  • a range between the two intersecting portions 22 x sandwiching the tooth profile center line Lc is a range corresponding to one tooth of the external teeth 20.
  • the second tooth bottom portion 22 b is continuous with the rear first tooth bottom portion 22 a in the rotation direction of the inner rotor 2.
  • the radius rde of the first drawing point for drawing the epitrochoid curve forming the tooth tip portion 21, that is, the first value Rde, and the hypotrochoid curve forming the tooth bottom portion 22 are drawn.
  • the radius rdh of the second drawing point that is, the second value Rdh is set to the same value Rd.
  • the first intermediate portion 23 is formed between the tooth tip portion 21 and the first tooth bottom portion 22 a of the tooth bottom portion 22, and is located on the tooth tip portion 21 side. And an inner intermediate portion 23i located on the first tooth bottom portion 22a side.
  • the outer intermediate portion 23o is such that the tangent at the front end 21f in the rotational direction of the inner rotor 2 of the tooth tip portion 21 is the same as the tangent of the epitrochoidal curve at the end 21f. It is formed by a defined involute curve. Thereby, the tip part 21 and the outer side intermediate part 23o can be smoothly continued in the edge part 21f.
  • the inner intermediate portion 23i is smoothly continuous with the first tooth bottom portion 22a at the rear end portion 22r in the rotation direction of the inner rotor 2 of the first tooth bottom portion 22a and is a boundary portion 23x with the outer intermediate portion 23o.
  • the outer intermediate portion 23o is formed by a smooth curve (for example, an arc) that is smoothly continuous. As shown in the drawing, the curve forming the inner intermediate portion 23i may be selected to be as short as possible than the involute curve forming the outer intermediate portion 23o.
  • the first intermediate portion 23 is formed by an involute curve (see Japanese Patent Application Laid-Open No. 2014-181620) obtained by using a basic circle having a center O in common with the basic circle BCt of the epitrochoid curve and the hypotrochoid curve. May be.
  • the diameter of the base circle of the involute curve forming the first intermediate portion 23 is “Rbi”
  • the diameter of the base circle BCt of the epitrochoid curve forming the tooth tip portion 21 and the hypotrochoid curve forming the tooth bottom portion 22 is set. Is set to “Rbt”
  • the diameters Rbt and Rbi may be selected so as to satisfy the relationship Rbi ⁇ Rbt.
  • the first intermediate portion 23 may include a relay surface formed by a smooth curve (for example, an arc) on the inner side (front side) and the outer side (rear side) of the portion formed by the involute curve.
  • the second intermediate portion 24 is formed between the tooth tip portion 21 and the second tooth bottom portion 22 b of the tooth bottom portion 22, and has teeth more than the intersection portion 24 x with the basic circle BCt.
  • intersection part 24x are included.
  • the gear pump 1 in order to improve the volumetric efficiency by regulating the flow of the hydraulic oil between the first and second discharge ports 7 and 8, the gear pump 1 It is necessary to make the minimum value of the clearance between the external teeth 20 and the internal teeth 30 overlapping with the partition wall 9 as small as possible when viewed from the axial direction of 1.
  • the external teeth 20 and the internal teeth 30 It is necessary to increase the minimum value of the clearance to allow the hydraulic oil to flow between the interdental chambers 5 adjacent to each other, thereby reducing the flow velocity of the hydraulic oil flowing from the suction port 6. Therefore, the inventors have determined the minimum clearance between the external teeth 20 and the internal teeth 30 between the first and second discharge ports 7 and 8 and the clearance between the external teeth 20 and the internal teeth 30 on the suction port 6 side. We conducted intensive research to optimize the minimum value.
  • volume change amount per unit angle hereinafter referred to as “volume change”. It has come to focus on "rate ⁇ V").
  • the internal pressure greatly decreases when the volume change rate ⁇ V becomes the maximum, and from the suction port 6 due to the decrease in the internal pressure. Cavitation tends to occur when hydraulic fluid flows at a high flow rate.
  • the minimum value of the clearance between the external teeth 20 and the internal teeth 30 that define the interdental chamber 5 that communicates with the intake port 6 and has the maximum volume change rate ⁇ V (hereinafter referred to as “intake side clearance” as appropriate). The smaller the amount, the lower the amount of pressure in the interdental chamber 5 (negative pressure) becomes larger when the volume change rate ⁇ V becomes maximum.
  • the plurality of external teeth 20 of the inner rotor 2 are in the ideal center state, and the minimum clearance (the clearance between the external teeth 20 and the internal teeth 30 that overlap the partition wall 9 when the volume change rate ⁇ V amount becomes maximum (
  • the suction side clearance is appropriately asymmetrical with respect to the tooth profile center line Lc so as to be larger than the “discharge side clearance”.
  • the rotation center c of the inner rotor 2 coincides with the rotation center of the rotation shaft 4 fixed to the inner rotor 2, and the rotation center c of the outer rotor 3 and the outer rotor 3 are accommodated.
  • the state where the center of the gear housing chamber matches.
  • the length of the curve forming the first intermediate portion 23 that is, the length from the end portion 21f of the tooth tip portion 21 to the end portion 22r of the first tooth bottom portion 22a.
  • the length is determined to be longer than the length of the curve forming the second intermediate portion 24, that is, the length from the end portion 21r of the tooth tip portion 21 to the end portion 22f of the second tooth bottom portion 22b.
  • the length of the hypotrochoid curve forming the first tooth bottom portion 22a that is, the length from the end 22r of the first tooth bottom portion 22a to the intersecting portion 22x is the length of the hypotrochoid curve forming the second tooth bottom portion 22b.
  • the length of the curve forming the first intermediate portion 23 is made longer than the length of the curve forming the second intermediate portion 24, and the length of the hypotrochoid curve forming the first tooth bottom portion 22a is set to the first length.
  • the end portion 21r on the rear side in the rotational direction of the epitrochoid curve forming the tooth tip portion 21 is made the second tooth bottom portion as shown in FIG. 22b, and the end portion 21f on the front side in the rotational direction of the epitrochoid curve can be moved outward in the radial direction of the inner rotor 2.
  • interdental chamber 5 connected to the 1st and 2nd discharge ports 7 and 8 by making the end part 21r on the back side in the rotation direction of the epitrochoid curve forming the tooth tip part 21 closer to the second tooth bottom part 22b.
  • the minimum value of the clearance between the outer teeth 20 and the inner teeth 30 that define the above can be reduced as a whole.
  • the minimum clearance between the teeth 20 and the internal teeth 30 can be increased as a whole.
  • the interdental chamber 5 that has reached the top dead center is positioned on the rear side in the rotation direction of the inner rotor 2. While any one external tooth 20 is in contact with the corresponding internal tooth 30, the external tooth 20 located on the one rear side in the rotation direction of the inner rotor 2 is located with respect to any one external tooth 20.
  • a plurality of external teeth 20 of the inner rotor 2 are formed so as to contact the corresponding internal teeth 30.
  • the position where the tooth tip apex 21t of the external tooth 20 and the tooth top apex of the internal tooth 30 face each other in a straight line through the top dead center (refer to the position between the suction port 6 and the first discharge port 7 in FIG. 7). While one of the outer teeth 20 closest to () is in contact with the corresponding inner tooth 30, the outer teeth 30 are positioned one rear side in the rotational direction of the inner rotor 2 with respect to any one of the outer teeth 30. The external teeth 20 come into contact with the corresponding internal teeth 30.
  • the “top dead center” is a position where the volume of the interdental chamber 5 that increases with the rotation of the inner rotor 2 or the like is maximized (position between the suction port 6 and the first discharge port 7 in FIG. 1).
  • the “decentered state from the ideal center state” means a deviation between the rotation center c of the inner rotor 2 and the rotation center of the rotation shaft 4 and a deviation between the rotation center c of the outer rotor 3 and the center of the gear housing chamber. A state in which at least one of them has occurred.
  • FIG. 5 illustrates the relationship between the rotation angle ⁇ around the rotation center 2 c of the inner rotor 2 in the gear pump 1 and the minimum value of the clearance between the outer teeth 20 and the inner teeth 30, and
  • FIG. 6 illustrates the rotation center of the inner rotor 2.
  • the relationship between the rotation angle ⁇ around 2c and the volume V and volume change rate ⁇ V of one interdental chamber 5 is illustrated.
  • the rotation angle ⁇ around the rotation center 2c of the inner rotor 2 is a rotation angle around the rotation center 2c of the line portion connecting the bottommost portion (deepest portion) of the tooth bottom portion 22 of the external tooth 20 and the rotation center 2c. 7 is measured counterclockwise in FIG. 7 when the state where the bottom of the bottom 22 of the external tooth 20 is located directly below the center of rotation 2c of the inner rotor 2 is 0 °.
  • a range A in FIG. 5 indicates a range in which the bottom part of the bottom part 22 of the external tooth 20 overlaps the partition wall 9.
  • the volume change rate ⁇ V shown in FIG. 6 is a change amount of the volume V when the rotation angle ⁇ changes (increases) by, for example, 5 °.
  • the minimum clearance CLd between the external teeth 20d and the internal teeth 30d overlapping the partition wall 9 is the discharge side clearance.
  • the minimum clearance CLi (suction side clearance) between the external teeth 20i and the internal teeth 30i is the minimum clearance CLd between the external teeth 20d and the internal teeth 30d overlapping the partition wall 9 (FIG. 5). 5 to 9 to 10 times as large as the value in the range A).
  • the minimum clearance shown in FIG. 5 is a design value (analysis value) in an ideal center state, and the minimum clearance between the external teeth 20 and the internal teeth 30 in the gear pump 1 as a product is a manufacturing tolerance or the like. Varies depending on In this regard, according to experiments and analysis by the present inventors, if the suction side clearance (CLi) in the product is at least three times or more than the discharge side clearance (CLd), the external teeth 20 overlapping the partition wall 9 are obtained. It has been confirmed that the minimum value of the clearance in the interdental chamber 5 where the volume change rate ⁇ V is maximized can be made sufficiently large in practice, while the minimum value of the clearance between the teeth 30 and the internal teeth 30 is sufficiently small in practice. Yes.
  • the gear pump 1 is one rear side in the rotational direction of any one of the external teeth 20.
  • the external teeth 20 positioned in the inner rotor 2 are configured to come into contact with the corresponding internal teeth 30.
  • the suction side clearance (CLi) is set. The upper limit of will be determined.
  • the gear pump 1 when the volume change rate ⁇ V of the interdental chamber 5m shown in FIG. 7 is maximized, the pair of external teeth 20d and internal teeth 30d overlap with the partition wall 9. Therefore, the external teeth 20d and internal teeth
  • the minimum clearance CLd with respect to 30d is set as the discharge-side clearance, but is not necessarily limited thereto. That is, the gear pump 1 may be configured such that the two sets of external teeth 20 and internal teeth 30 overlap the partition wall 9 when the volume change rate ⁇ V of the interdental chamber 5m is maximized. Of the minimum clearances of the outer teeth 20 and the inner teeth 30 in the set, the smaller one may be used as the discharge side clearance.
  • the discharge-side clearance is defined by the external teeth 20 and the internal teeth that define the interdental chamber 5 that at least partially overlaps the partition wall between the first and second discharge ports 7 and 8 when the volume change rate ⁇ V becomes maximum.
  • the minimum clearance with the teeth 30 may be set.
  • any one of the external teeth 20 closest to the top dead center is in contact with the corresponding internal tooth 30.
  • the external tooth 30 at the top dead center in the ideal rotation state in order to bring the external tooth 20 positioned one rear side in the rotational direction from any one of the external teeth 20 into contact with the corresponding internal tooth 30, the external tooth 30 at the top dead center in the ideal rotation state.
  • the tip clearance CLx (see FIG. 7) between the outer teeth 30 and the inner teeth 20 is set to the driving tooth surface of the outer teeth 30 located one rear side in the rotational direction with respect to the outer teeth 30 on the top dead center and the corresponding inner teeth 30.
  • the clearance with the driven tooth surface be equal to or greater than the minimum value CLy (see FIG. 7) in the ideal center state.
  • the tip clearance CLx between the outer teeth 30 and the inner teeth 20 at the top dead center in the ideal center state is preferably set to 200 ⁇ m or less.
  • the lower limit value of the tip clearance CLx in the ideal center state may be set to 5 ⁇ m or more in consideration of manufacturing tolerances.
  • Each external tooth 20 of the inner rotor 2 is asymmetrical so that the minimum value of the clearance in the interdental chamber 5 where the rate ⁇ V is maximum is increased.
  • the tooth tip portion 21 of each external tooth 20 of the inner rotor 2 is formed by a portion other than the loop portion of the epitrochoid curve having a trochoid coefficient larger than 1
  • the tooth bottom portion 22 is formed by the epitrochoid.
  • the curve and the base circle BCt are made common and formed by a portion other than the hypotrochoid curve loop in which the trochoid coefficient is larger than 1.
  • the shape of the tooth tip portion 21 and the tooth bottom portion 22 is determined using one basic circle BCt, and the outer diameter of the basic circle BCt, that is, the outer diameter of the inner rotor 2 is reduced. It is possible to easily increase the tooth height while maintaining it.
  • the first intermediate portion 23 positioned on the front side of the tooth tip portion 21 in the rotation direction of the inner rotor 2 is formed by an involute curve.
  • the outer teeth 20 of the inner rotor 2 and the inner teeth 30 of the outer rotor 3 can be meshed more smoothly and the rotational speed ratio between the inner rotor 2 and the outer rotor 3 can be made constant.
  • the first intermediate unit 23 is an involute curve such as an n-order function (where “n” is an integer of 1 or more), an arc, an arbitrary polynomial, a trigonometric function, a relaxation curve, and a combination thereof. Needless to say, it may be formed by other curves.
  • the range from the intersection 24x with the basic circle BCt of the second intermediate portion 24 to the end 21r of the tooth tip 21 changes to the basic circle BCt while changing the radius of the drawing point of the abduction circle Co. It is formed by a first curve obtained by rolling the circumscribed circle Co that circumscribes it without slipping. Further, the range from the intersection 24x of the second intermediate portion 24 with the basic circle BCt to the end 22f of the second tooth bottom portion 22b is inscribed in the basic circle BCt while changing the radius of the drawing point of the inversion circle Ci. It is formed by a second curve obtained by rolling the inward circle Ci without slipping.
  • the second intermediate portion smoothly connecting the tooth tip portion 21 and the second tooth bottom portion 22b while bringing the rear end portion 21r of the tooth tip portion 21 in the rotation direction of the inner rotor as close as possible to the second tooth bottom portion 22b.
  • the part 24 can be configured.
  • the second intermediate portion 24 is also an involute curve such as an n-order function (where “n” is an integer equal to or greater than 1), an arc, an arbitrary polynomial, a trigonometric function, a relaxation curve, and a combination thereof. Needless to say, it may be formed by other curves.
  • the gear pump according to the present disclosure has an inner rotor having a plurality of external teeth, a plurality of internal teeth that are larger than the external teeth of the inner rotor, and is arranged to be eccentric with respect to the inner rotor. And a plurality of interdental chambers defined by the two adjacent external teeth and the two adjacent internal teeth, with the rotation of the inner rotor and the outer rotor.
  • One suction port that communicates with the interdental chamber that increases in volume, and the interdental chamber that is partitioned by a partition wall and independent from each other, and the volume decreases as the inner rotor and the outer rotor rotate.
  • the minimum clearance between the external teeth and the internal teeth that defines the interdental chamber that maximizes the volume change amount is defined as the suction side clearance, and the volume change amount per unit angle is maximized when the volume change amount is maximized.
  • the suction side clearance when the minimum clearance between the external teeth and the internal teeth that define an interdental chamber that at least partially overlaps the partition wall between the first and second discharge ports is the discharge side clearance. Is larger than the discharge-side clearance.
  • This gear pump has one suction port and first and second discharge ports that are partitioned by a partition wall and independent from each other.
  • the flow of fluid between the first and second discharge ports is reduced by further reducing the minimum clearance between the external teeth and the internal teeth that overlap the partition between the first and second discharge ports.
  • the minimum clearance between the external teeth and the internal teeth is reduced from the viewpoint of suppressing the occurrence of cavitation due to the inflow (suction) of fluid from the suction port. It needs to be bigger.
  • the internal pressure greatly decreases when the volume change per unit angle becomes maximum. Cavitation is likely to occur due to the flow of fluid from the suction port at a high flow rate due to the decrease in the pressure.
  • the minimum clearance between the external teeth and the internal teeth that define the interdental space that maximizes the volume change amount when the inner rotor rotates by a unit angle while communicating with the suction port, that is, the suction side clearance is small. As the amount of decrease in the pressure in the interdental chamber (negative pressure) increases, the volume change amount per unit angle becomes maximum.
  • the inner rotor of this gear pump has an external tooth and an internal tooth that define an interdental space that at least partially overlaps the partition wall when the suction side clearance has a maximum volume change per unit angle.
  • the clearance is formed to be larger than the minimum value, that is, the discharge-side clearance.
  • the volume is determined based on the minimum clearance between the external teeth and the internal teeth that define the interdental chamber that at least partially overlaps the partition wall.
  • the plurality of external teeth may be formed asymmetrically with respect to the tooth profile center line. Thereby, the suction side clearance can be easily made larger than the discharge side clearance.
  • the tooth profile center line may be a straight line connecting the top of the tooth tip and the rotation center of the inner rotor.
  • the suction side clearance may be at least three times the discharge side clearance.
  • the minimum clearance between the external teeth and the internal teeth overlapping the partition wall can be reduced.
  • the minimum value of the clearance in the interdental chamber where the volume change amount is maximized can be made sufficiently large in practice while being sufficiently small in practice. Thereby, it becomes possible to satisfactorily suppress the occurrence of cavitation in the interdental chamber communicating with the suction port while further improving the volumetric efficiency.
  • the tip clearance between the external teeth and the internal teeth when any one of the external teeth and the corresponding tooth tops of the internal teeth are positioned in a straight line is greater than that of any one of the external teeth.
  • the clearance may be equal to or greater than the minimum value of the clearance between the driving tooth surface of the external tooth positioned on the rear side in the rotation direction of the inner rotor and the driven tooth surface of the internal tooth corresponding thereto.
  • the tip clearance between any one of the outer teeth and the corresponding inner teeth may be 200 ⁇ m or less. Thereby, it is possible to suppress the increase in the discharge-side clearance and to regulate the fluid flow between the first and second discharge ports and to improve the volume efficiency.
  • each of the outer teeth of the inner rotor is a tooth tip formed by an epitrochoid curve obtained by rolling an outer rotation circle having a radius smaller than the drawing point radius without slipping while circumscribing the base circle.
  • a second tooth bottom portion continuous with the first tooth bottom portion on the rear side in the rotation direction, and an arbitrary curve, and the tooth tip portion and the first tooth bottom.
  • a first intermediate portion located between the first tip portion and the second root portion, and a first intermediate portion located between the first tip portion and the second bottom portion.
  • the length of the curve forming the intermediate portion may be longer than the length of the curve forming the second intermediate portion.
  • the minimum value of the clearance between the external teeth and the internal teeth that overlap the partition wall is made smaller, while the minimum clearance value in the interdental chamber that maximizes the volume change amount is reduced. It becomes possible to make it larger. That is, by making the length of the curve forming the first intermediate portion longer than the length of the curve forming the second intermediate portion, the end portion on the rear side in the rotation direction of the epitrochoid curve forming the tooth tip portion is The two tooth bottoms can be brought closer to each other, and the end portion on the front side in the rotational direction of the epitrochoid curve can be moved outward in the radial direction of the inner rotor.
  • the external teeth and internal teeth that overlap the partition wall It is possible to reduce the cavitation in the interdental chamber satisfactorily by making the minimum clearance value smaller and sufficiently increasing the minimum clearance value in the interdental chamber where the volume change is maximum.
  • one basic circle is used by increasing the radius of the epitrochoid curve and hypotrochoid curve while keeping the radius of the abduction circle and adduction circle (the radius of the basic circle / the number of teeth) small.
  • the shape of the tip portion and the bottom portion of the tooth can be determined, and the tooth height of the outer teeth can be easily increased while keeping the outer diameter of the basic circle, that is, the outer diameter of the inner rotor small.
  • the first intermediate part may be formed by at least an involute curve.
  • the range from the intersection of the second intermediate portion with the basic circle to the boundary with the tooth tip portion is the outer circumference circumscribing the basic circle while changing the radius of the drawing point of the abduction circle. It may be formed by a first curve obtained by rolling a rolling circle without slipping, and the range from the intersection of the second intermediate part with the basic circle to the boundary with the second tooth bottom is It may be formed by a second curve obtained by rolling the inversion circle inscribed in the basic circle without slipping while changing the radius of the drawing point of the inversion circle. Accordingly, the second intermediate portion that smoothly connects the tooth tip portion and the second tooth bottom portion while making the rear end portion of the tooth tip portion in the rotation direction of the inner rotor as close as possible to the second tooth bottom portion is configured. Is possible.
  • the tooth profile of the outer rotor defined by the plurality of inner teeth has an eccentricity amount of the rotation center of the outer rotor with respect to the rotation center of the inner rotor as “e”, and the rotation center of the inner rotor and the outer rotor Clearance between the tooth tip of the external tooth and the tooth tip of the internal tooth when the rotation center of the rotor, the top of the tooth tip of the external tooth and the top of the tooth tip of the internal tooth are positioned on a straight line Is set to “t”, the rotation center of the inner rotor is revolved by a predetermined angle on the circumference of the diameter 2 ⁇ e + t centering on the rotation center of the outer rotor, and the rotation center of the inner rotor is When revolving by an angle, the inner rotor is drawn with respect to a plurality of tooth profile lines obtained by rotating the inner rotor by the rotation angle corresponding to the predetermined angle and the number of teeth of the inner rotor. It may be determined based on ⁇ .
  • a manufacturing method of a gear pump includes an inner rotor having a plurality of external teeth, and an outer rotor having a plurality of inner teeth larger than the outer teeth of the inner rotor and arranged eccentric to the inner rotor.
  • a suction port that communicates with the chamber, and a first and a second that are partitioned by a partition wall and are independent of each other, and communicate with the interdental chamber that decreases in volume as the inner rotor and the outer rotor rotate.
  • a method for manufacturing a gear pump comprising a discharge port, wherein the inner rotor rotates at a unit angle while communicating with the suction port.
  • the minimum clearance between the external teeth and the internal teeth that define the interdental chamber where the amount of change is the maximum is the suction side clearance, and the first change when the volume change amount per unit angle is the maximum.
  • the suction side clearance is A step of forming the inner rotor so as to be larger than the discharge-side clearance;
  • the flow of fluid between the first and second discharge ports is restricted to improve the volumetric efficiency, and the occurrence of cavitation in the interdental chamber communicating with the suction port is suppressed. It becomes possible.
  • the invention of the present disclosure can be used in the gear pump manufacturing industry.

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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

Plusieurs dents externes (20) d'un rotor interne (2) sont formées de sorte que le jeu côté admission (CLi) soit supérieur au jeu côté refoulement (CLd), le jeu côté admission correspondant à la valeur minimale de jeu (CLi) entre des dents externes (20i) et des dents internes (30i) délimitant une chambre inter-dents (5) qui est en communication avec un orifice d'admission (6) et va présenter la variation en volume la plus importante lorsque le rotor interne (2) tourne d'un angle unitaire, et le jeu côté refoulement (CLd) correspond à la valeur minimale de jeu (CLd) entre des dents externes (20d) et des dents internes (30d) délimitant une chambre inter-dents (5) chevauchant au moins partiellement une paroi de séparation (9) entre des premier et second orifices (7, 8) de refoulement lorsque la variation en volume par angle unitaire est la plus importante.
PCT/JP2015/086533 2015-01-30 2015-12-28 Pompe à engrenages et son procédé de fabrication WO2016121291A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US15/543,624 US20170370359A1 (en) 2015-01-30 2015-12-28 Gear pump and manufacturing method of the same
JP2016571829A JP6343355B2 (ja) 2015-01-30 2015-12-28 ギヤポンプおよびその製造方法
CN201580074754.4A CN107208627B (zh) 2015-01-30 2015-12-28 齿轮泵及其制造方法
DE112015006082.0T DE112015006082T5 (de) 2015-01-30 2015-12-28 Zahnradpumpe und Herstellungsverfahren der Zahnradpumpe

Applications Claiming Priority (2)

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JP2015-017762 2015-01-30
JP2015017762 2015-01-30

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JP (1) JP6343355B2 (fr)
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WO (1) WO2016121291A1 (fr)

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WO2017043478A1 (fr) * 2015-09-07 2017-03-16 アイシン・エィ・ダブリュ株式会社 Pompe à engrenages
KR102425555B1 (ko) * 2021-03-31 2022-07-27 창원대학교 산학협력단 로터리 로브 펌프용 로터

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DE102017214897B4 (de) * 2017-08-25 2019-03-21 Kocks Technik Gmbh & Co Kg Anstellbares Walzgerüst für das Walzen von stabförmigem Walzgut mit einer asymmetrischen Verzahnung zwischen den Exzenterbuchsen sowie Exzenterbuchse mit asymmetrischer Verzahnung
CN109373167B (zh) * 2018-12-19 2020-06-09 自贡市川力科技股份有限公司 一种双出油道结构的机油泵
CN112628137B (zh) * 2020-11-20 2023-05-02 中国航发哈尔滨东安发动机有限公司 一种高容积效率摆线齿轮泵及提高容积效率的方法
US11549507B2 (en) 2021-06-11 2023-01-10 Genesis Advanced Technology Inc. Hypotrochoid positive-displacement machine
US11965509B2 (en) 2022-02-28 2024-04-23 Genesis Advanced Technology Inc. Energy transfer machine for corrosive fluids

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JP5469875B2 (ja) * 2009-02-10 2014-04-16 豊興工業株式会社 内接歯車ポンプ
JP2015094252A (ja) * 2013-11-11 2015-05-18 豊興工業株式会社 内接歯車ポンプ

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JP2008128041A (ja) * 2006-11-17 2008-06-05 Sumitomo Denko Shoketsu Gokin Kk 内接歯車式ポンプ
JP5469875B2 (ja) * 2009-02-10 2014-04-16 豊興工業株式会社 内接歯車ポンプ
JP2015094252A (ja) * 2013-11-11 2015-05-18 豊興工業株式会社 内接歯車ポンプ

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WO2017043478A1 (fr) * 2015-09-07 2017-03-16 アイシン・エィ・ダブリュ株式会社 Pompe à engrenages
KR102425555B1 (ko) * 2021-03-31 2022-07-27 창원대학교 산학협력단 로터리 로브 펌프용 로터

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CN107208627B (zh) 2019-06-28
CN107208627A (zh) 2017-09-26
DE112015006082T5 (de) 2017-10-12
US20170370359A1 (en) 2017-12-28
JP6343355B2 (ja) 2018-06-13

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