WO2017043478A1 - ギヤポンプ - Google Patents

ギヤポンプ Download PDF

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Publication number
WO2017043478A1
WO2017043478A1 PCT/JP2016/076157 JP2016076157W WO2017043478A1 WO 2017043478 A1 WO2017043478 A1 WO 2017043478A1 JP 2016076157 W JP2016076157 W JP 2016076157W WO 2017043478 A1 WO2017043478 A1 WO 2017043478A1
Authority
WO
WIPO (PCT)
Prior art keywords
inner rotor
gear pump
discharge port
interdental chamber
teeth
Prior art date
Application number
PCT/JP2016/076157
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
雅士 服部
光博 武田
雅幸 木村
Original Assignee
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・エィ・ダブリュ株式会社 filed Critical アイシン・エィ・ダブリュ株式会社
Priority to CN201680050919.9A priority Critical patent/CN107923390B/zh
Priority to DE112016002336.7T priority patent/DE112016002336T8/de
Priority to US15/574,220 priority patent/US20180172000A1/en
Publication of WO2017043478A1 publication Critical patent/WO2017043478A1/ja

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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
    • F04C2/082—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
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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.
  • a gear pump including an inner rotor having n external teeth, an outer rotor having n + 1 internal teeth meshing with the external teeth, and a casing in which a suction port and a discharge port are formed is known.
  • the first angle formed by the first straight line connecting the rotation center of the inner rotor and the tooth tip of the external tooth and the second straight line connecting the rotation center and the meshing portion of the external tooth is the rotation center and the external tooth. It is set to 1.4 times or more and 1.8 times or less of the second angle formed by the third straight line connecting the tooth bottom and the second straight line.
  • the width along the rotation direction of the meshing portion of the external teeth is equal to the distance between the rear end in the rotation direction of both rotors of the suction port and the front end in the rotation direction of the discharge port, that is, the partition width of the port. .
  • Patent Document 1 by setting the first angle to be 1.4 times or more and 1.8 times or less of the second angle, both rotors of a plurality of cells (interdental chambers) mesh with each other from the outer teeth. It is described that it is possible to prevent the occurrence of so-called fluid confinement, in which the minimum volume cell located at the meshing position where the rotational driving force is transmitted to the teeth is sealed.
  • the gap between the case and both rotors (the gap in the axial direction of the gear pump) with respect to a cell whose volume is minimized by discharging fluid to the discharge port. It is difficult to completely suppress the inflow of fluid. Therefore, in the gear pump of Patent Document 1, cavitation occurs due to the fluid flowing at high speed from the gap between the case and both rotors into the interdental chamber that does not communicate with the discharge port and communicates with the suction port. There is a fear.
  • the main object of the invention of the present disclosure is to provide a gear pump that can satisfactorily suppress the occurrence of cavitation in the interdental chamber that does not communicate with the discharge port and communicates with the suction port.
  • the gear pump of the present disclosure has a suction port, a discharge port, 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 eccentric with respect to the inner rotor. And a plurality of interdental chambers defined by the plurality of external teeth and the plurality of internal teeth, the discharge port is configured to rotate the inner rotor and the outer rotor.
  • the interdental chamber communicated with the interdental chamber, the volume of which decreases along with the discharge port, and communicated with the suction port while the volume of the interdental chamber decreased, and communicated with the discharge port.
  • the volume of the interdental chamber that is no longer increased increases after at least a part of the interdental chamber communicates with the suction port.
  • the interdental chamber that has stopped communicating with the discharge port communicates with the suction port while the volume of the interdental chamber decreases as the inner and outer rotors rotate.
  • the volume of the interdental chamber that is no longer in communication with the discharge port decreases with the rotation of the inner rotor or the like, so that fluid is discharged from the interdental chamber to the suction port.
  • the volume of the interdental chamber that is no longer in communication with the discharge port increases after the interdental chamber communicates with the suction port. That is, the volume of the interdental chamber that is no longer in communication with the discharge port is minimized after the interdental chamber communicates with the suction port.
  • the fluid flowing into the suction port from the interdental chamber that is no longer in communication with the discharge port causes fluid to flow into the interdental chamber from the gap between the inner rotor and the outer rotor and the member that accommodates both (axial gap). Inflow at high speed can be well controlled. Therefore, in this gear pump, it is possible to satisfactorily suppress the occurrence of cavitation in the interdental chamber that does not communicate with the discharge port and communicates with the suction port.
  • 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 configured so that any one or a plurality of inner teeth 30 located on the lower side in FIG.
  • a plurality of interdental chambers (pump chambers) 5 are basically 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 is formed with a suction port 6, a first discharge port 7, and a second discharge port 8 each extending in a substantially arc shape.
  • the suction port 6 communicates with the interdental chamber 5 whose volume increases as the inner rotor 2 and the outer rotor 3 rotate among the interdental chambers 5 defined by the external teeth 20 and the internal teeth 30 ( opposite.
  • the first and second discharge ports 7 and 8 are separated by a partition wall 9 and are independent from each other, and the teeth whose volumes decrease as the inner rotor 2 and the outer rotor 3 of the plurality of interdental chambers 5 rotate. It communicates (opposites) with the inter-chamber 5 respectively.
  • 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 configuration diagram showing the external teeth 20 of the inner rotor 2
  • FIG. 3 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 (a portion other than the loop portion).
  • 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 root portion 22 is an intermediate formed by a hypotrochoid curve (a portion other than the loop portion) 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. Part and two rising parts formed by a curve such as an arc.
  • the hypotrochoid curve forming the middle portion of the tooth bottom portion 22 shares the epitrochoid curve forming the tooth tip portion 21 with the basic circle BCt, and as shown in FIG.
  • the radius of the second drawing point It is obtained by keeping rdh at the second value Rdh (constant value) and rolling the inversion circle Ci having a radius rh smaller than the second value Rdh without slipping while inscribed in the basic circle BCt. .
  • 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 two rising parts of the tooth bottom part 22 extend from the intermediate part toward the corresponding first or second intermediate part 23, 24 so as to be smoothly connected to the intermediate part formed by the hypotrochoid curve.
  • the rear rising portion in the rotation direction of the inner rotor 2 is formed so as to smoothly continue to the first intermediate portion 23 at the front end portion 23f of the first intermediate portion 23 in the rotation direction.
  • the front rising portion in the second rotational direction is formed so as to be smoothly continuous with the second intermediate portion 24 at the rear end 24r of the second intermediate portion 24 in the rotational direction.
  • the tooth bottom portion 22 is frontward 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.
  • an intersection 22x with the line segment Le rotated to the rear side is included.
  • 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 first intermediate portion 23 is formed between the tooth tip portion 21 and the front tooth bottom portion 22 of the tooth tip portion 21 in the rotation direction of the inner rotor 2.
  • the first intermediate portion 23 is determined such that the tangent at the front end 21f in the rotation direction of the tooth tip 21 is common to the tangent of the epitrochoidal curve at the end 21f. Formed by an involute curve. Thereby, the tip part 21 and the 1st intermediate part 23 can be smoothly continued in the edge part 21f.
  • the length of the involute curve forming the first intermediate portion 23, that is, the length from the end portion 21 f of the tooth tip portion 21 to the end portion 23 f of the first intermediate portion 23 is the same as that of the second intermediate portion 24.
  • the length of the curve to be formed that is, the length from the end portion 21r of the tooth tip portion 21 to the end portion 24r of the second intermediate portion 24 is determined.
  • the second intermediate portion 24 is formed between the tooth tip portion 21 and the rear tooth bottom portion 22 of the tooth tip portion 21 in the rotation direction of the inner rotor 2.
  • the second intermediate portion 24 includes an outer intermediate portion 24o located on the tooth tip portion 21 side with respect to the intersection portion 24x with the basic circle BCt, and an inner intermediate portion 24i located on the tooth bottom portion 22 side with respect to the intersection portion 24x. Including. In the present embodiment, the range from the outer intermediate portion 24o, that is, the intersecting portion 24x to the rear end portion (boundary) 21r in the rotation direction of the inner rotor 2 of the tooth tip portion 21, as shown in FIG.
  • FIG. 4 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 the rotation center 2c of the inner rotor 2Z based on the inner rotor 2 and the rotation center 3c of the outer rotor 3. Obtained by rotating the inner rotor 2Z by a rotation angle ⁇ / N when the rotation center 2c revolves by a predetermined angle ⁇ . It is determined based on the envelope drawn with respect to a plurality of tooth profile lines (the outline of the inner rotor 2, see the two-dot chain line in FIG. 3).
  • t indicates that the rotation center 2c of the inner rotor 2Z, the rotation center 3c of the outer rotor 3, the top part 21t of the tooth tip part 21 of the external tooth 20 and the top part of the tooth tip part 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 inner rotor 2Z for defining the tooth profile of the outer rotor 3 corresponds to a structure in which the tooth bottom portion 22 of the inner rotor 2 is replaced with a tooth bottom portion 22z indicated by a two-dot chain line in FIGS. 2 and 3, the tooth bottom portion 22z is the end of the second intermediate portion 24 formed by the same hypotrochoidal curve (portion other than the loop portion) that forms the intermediate portion of the tooth bottom portion 22, as shown in FIGS.
  • a portion from the portion 24r to the boundary portion 22y shown in FIGS. 2 and 3 and a portion from the boundary portion 22y formed by a smooth curve (for example, an arc) to the end portion 23f of the first intermediate portion 23 are included.
  • 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 2Z.
  • the inner rotor 2 (specifications of the external teeth 20), the outer rotor 3, the suction port 6, the first and second discharge ports 7, 8 are not connected to the second discharge port 8.
  • the chamber 5x (see FIG. 1) communicates with the suction port 6 while the volume of the interdental chamber 5x is decreasing, and after the communication between at least a part of the interdental chamber 5x and the suction port 6, the volume of the interdental chamber 5x Is configured to increase.
  • the top dead center (a position where the top of the tooth tip 21 of the external tooth 20 and the top of the tooth tip of the internal tooth 30 face each other in a straight line) is closest.
  • the external tooth 20 located on the back side in the rotation direction of any one of the external teeth 20 is in contact with the corresponding internal tooth 30.
  • the plurality of external teeth 20 of the inner rotor 2 are formed.
  • the occurrence of cavitation in the interdental chamber 5 (5x) is satisfactorily suppressed.
  • the behavior of the inner rotor 2 and the outer rotor 3 during operation of the gear pump 1 can be stabilized to reduce vibration and noise.
  • FIG. 8 is a diagram illustrating the rotation angle ⁇ around the rotation center 2c of the inner rotor 2 and the interdental teeth that do not communicate with the second discharge port 8. It is a graph which illustrates the relationship with the volume V of the chamber 5x.
  • the rotation angle ⁇ 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 certain external tooth 20 and the rotation center 2c. Measurement is performed counterclockwise in FIG. 1 with 0 ° being the state in which the bottom of the bottom portion 22 of the external tooth 20 is located directly below the center of rotation 2c.
  • each interdental chamber 5 communicating with the second discharge port 8 decreases as the inner rotor 2 and the outer rotor 3 rotate. Then, when the rotation angle ⁇ of the inner rotor 2 becomes the first angle ⁇ 1 (see FIG. 8), the rotation direction that defines the interdental chamber 5x communicating with the second discharge port 8, as shown in FIG.
  • the meshing portion E of the rear external teeth 20 and the internal teeth 30 overlaps the peripheral edge 8e of the second discharge port 8 when viewed from the axial direction of the inner rotor 2, so that the interdental chamber 5x and the second discharge port 8 communicate with each other. Will be refused.
  • the inner rotor 2 is more than the outer teeth 20 including the meshing portion E.
  • the tooth surface (the tooth bottom portion 22 or the second intermediate portion 24) of the outer tooth 20 on the immediately preceding side in the rotational direction is slightly different from the peripheral edge 6e of the suction port 6 when viewed from the axial direction of the inner rotor 2. get over.
  • the interdental chamber 5x communicates with the suction port 6 almost at the same time as it does not communicate with the second discharge port 8.
  • the volume V of the interdental chamber 5x increases with the rotation of the inner rotor 2 and the outer rotor 3, as shown in FIG. Will further decrease. Further, the communication area between the interdental chamber 5x and the suction port 6 as seen from the axial direction of the inner rotor 2 gradually increases as the inner rotor 2 and the outer rotor 3 rotate as shown in FIG. Further, in the present embodiment, when the rotation angle ⁇ of the inner rotor 2 becomes the second angle ⁇ 2 (see FIG. 8), the entire interdental chamber 5x communicates with the suction port 6 as shown in FIGS. (The entire interdental chamber 5x overlaps the suction port 6 when viewed from the axial direction), and the volume V of the interdental chamber 5x becomes the minimum value Vmin.
  • the tooth bottom portion 22 between the two external teeth 20 defining the interdental chamber 5x is formed in the axial direction of the inner rotor 2 as shown in FIG.
  • the suction port 6 does not protrude toward the rotation center 2c and is close to (substantially contacts) the inner peripheral edge 6ie.
  • the volume V of the interdental chamber 5x increases as the inner rotor 2 and the outer rotor 3 rotate as shown in FIG.
  • the hydraulic oil is sucked into the interdental chamber 5x from the suction port 6.
  • the interdental chamber 5 x that is no longer communicated with the second discharge port 8 is reduced while the volume V of the interdental chamber 5 x decreases as the inner rotor 2 and the outer rotor 3 rotate. It communicates with the suction port 6.
  • the volume V of the interdental chamber 5x that is no longer in communication with the second discharge port 8 decreases with the rotation of the inner rotor 2 or the like, so that the hydraulic oil remaining in the interdental chamber 5x is sucked. It is discharged to port 6.
  • the volume V of the interdental chamber 5x that has stopped communicating with the second discharge port 8 begins to increase after the interdental chamber 5x has completely communicated with the suction port 6. That is, the volume V of the interdental chamber 5x that is no longer communicated with the second discharge port 8 becomes the minimum value Vmin after the interdental chamber 5x is completely communicated with the suction port 6.
  • the interdental chamber 5 x whose volume V decreases with the rotation of the inner rotor 2 and the outer rotor 3 is a meshing portion between the external teeth 20 and the internal teeth 30 that define the interdental chamber 5 x.
  • the E overlaps with the peripheral edge 8e of the second discharge port 8 when viewed from the axial direction of the inner rotor 2, the E is not communicated with the second discharge port 8.
  • the meshing portion E overlaps the peripheral edge 8 e of the second discharge port 8 as viewed from the axial direction of the inner rotor 2
  • the rotational direction of the inner rotor 2 is greater than the external teeth 20 including the meshing portion E.
  • the interdental chamber 5x whose volume V decreases with the rotation of the inner rotor 2 or the like is communicated with the suction port 6 immediately after it stops communicating with the second discharge port 8, and the hydraulic oil in the interdental chamber 5x Can flow out to the suction port 6. Therefore, with respect to the interdental chamber 5x that is no longer in communication with the second discharge port 8, a narrow interdental chamber 5x is formed from the gap between the inner rotor 2 and the outer rotor 3 and at least one of the pump body and the pump housing. It is possible to very well regulate the flow of hydraulic oil (leakage oil) at high speed.
  • the volume V of the interdental chamber 5 x that has stopped communicating with the second discharge port 8 starts to increase after the entire interdental chamber 5 x communicates with the suction port 6.
  • the intermediate portion formed by the hypotrochoidal curve of each tooth bottom portion 22 of the inner rotor 2 is offset to the center O (rotation center 2c) side from the basic circle BCt, and the tooth The bottom 22 is deeper than that originally corresponding to the inner teeth 30 of the outer rotor 3.
  • the tooth bottom portion 22 between the two external teeth 20 that defines the interdental chamber 5x that is no longer in communication with the second discharge port 8 has a minimum volume V of the interdental chamber 5x.
  • the communication area can be increased. Accordingly, it is possible to suppress the occurrence of cavitation accompanying the suction of the hydraulic oil into the interdental chamber 5x by suppressing the increase in the flow velocity of the hydraulic oil flowing from the suction port 6 into the interdental chamber 5x.
  • the 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 of the inner rotor 2 is formed by a portion other than the hypotrochoid curve loop in which the epitrochoid curve and the basic circle BCt are made common and 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 of the external teeth 20 while keeping it.
  • the end portion on the rear side in the rotation direction of the suction port 6 is brought closer to the end portion on the front side in the rotation direction of the second discharge port 8, so that the interdental chamber 5 x that is no longer in communication with the second discharge port 8 can be easily filled. It is possible to communicate with the suction port 6 while V is decreasing.
  • the tooth tip portion 21 ( The end portion 21r on the rear side in the rotation direction of the epitrochoid curve) can be brought closer to the bottom portion 22, and the end portion 21f on the front side in the rotation direction of the tooth tip portion 21 can be moved outward in the radial direction of the inner rotor 2.
  • 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 second intermediate section 24 is also an involute curve such as an n-order function (where “n” is an integer greater than or equal to 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 1 may have a single discharge port.
  • each external tooth 20 of the inner rotor 2 may be formed symmetrically with respect to the tooth profile center line Lc.
  • the interdental chamber 5x communicates with the suction port 6 at a timing such that the interdental chamber 5x does not communicate with the suction port 6 while the interdental chamber 5x communicates with the second discharge port 8.
  • the timing may be slightly later than the timing at which communication with the discharge port 8 stops. That is, both timings do not necessarily have to coincide completely.
  • the inner rotor 2, the second discharge port 8, and the input port 6 have a meshing portion E between the external teeth 20 and the internal teeth 30 that define the interdental chamber 5 x.
  • the interdental chamber 5x may be formed so as to communicate with the suction port 6 before it overlaps the peripheral edge 8e of the inner rotor 2 when viewed from the axial direction.
  • the timing at which the interdental chamber 5x communicates with the suction port 6 is compared with the timing at which the interdental chamber 5x does not communicate with the second discharge port 8 within a range that does not significantly affect the discharge pressure from the second discharge port 8. May be slightly faster.
  • the interdental chamber 5x whose volume decreases with the rotation of the inner rotor 2 or the like, is communicated with the suction port 6 before it stops communicating with the second discharge port 8, and an appropriate amount of operation in the interdental chamber 5x is achieved. Oil can flow out to the second discharge port 8 and the suction port 6.
  • the gear pump (1) of the present disclosure includes the suction port (6), the discharge port (7, 8), the inner rotor (2) having a plurality of external teeth (20), and the inner rotor.
  • the discharge port (7, 8) is connected to the inner rotor (2).
  • the volume of the interdental chamber (5x) communicated with the inlet port (6) and no longer communicated with the discharge port (8) is such that at least a part of the interdental chamber (5x) is connected to the suction port (6). It is characterized by an increase after communication.
  • the interdental chamber that has stopped communicating with the discharge port communicates with the suction port while the volume of the interdental chamber decreases as the inner and outer rotors rotate.
  • the volume of the interdental chamber that is no longer in communication with the discharge port decreases with the rotation of the inner rotor or the like, so that fluid is discharged from the interdental chamber to the suction port.
  • the volume of the interdental chamber that is no longer in communication with the discharge port increases after the interdental chamber communicates with the suction port. That is, the volume of the interdental chamber that is no longer in communication with the discharge port is minimized after the interdental chamber communicates with the suction port.
  • the fluid flowing into the suction port from the interdental chamber that is no longer in communication with the discharge port causes fluid to flow into the interdental chamber from the gap between the inner rotor and the outer rotor and the member that accommodates both (axial gap). Inflow at high speed can be well controlled. Therefore, in this gear pump, it is possible to satisfactorily suppress the occurrence of cavitation in the interdental chamber that does not communicate with the discharge port and communicates with the suction port.
  • the volume (V) of the interdental chamber (5x) that has stopped communicating with the discharge port (6) starts to increase after the entire interdental chamber (5x) communicates with the suction port (6). Also good.
  • the communication area between the interdental chamber and the suction port when the fluid begins to flow from the suction port in response to an increase in volume with respect to the interdental chamber that is no longer in communication with the discharge port is suppressed. can do.
  • an increase in the flow rate of the fluid flowing from the suction port into the interdental chamber can be suppressed, and the occurrence of cavitation associated with the suction of the fluid into the interdental chamber can be satisfactorily suppressed.
  • the inner rotor (2) has a tooth bottom portion (22) defining the interdental chamber (5x) that is no longer in communication with the discharge port (8), and the volume (V) of the interdental chamber (5x) ), When viewed from the axial direction of the inner rotor (2), it does not protrude from the inner peripheral edge (6ie) of the suction port (6) to the rotation center (2c) side of the inner rotor (2). You may form so that it may adjoin to this inner periphery (6ie).
  • the minimum volume of the interdental chamber that is, the interdental chamber and the suction port when fluid starts to flow from the suction port in response to the increase in volume with respect to the interdental chamber that is no longer communicated with the discharge port.
  • the communication area can be increased.
  • an increase in the flow velocity of the fluid flowing from the suction port into the interdental chamber can be suppressed, and the occurrence of cavitation accompanying the suction of the fluid into the interdental chamber can be suppressed extremely well.
  • the bottom of the teeth of the inner rotor is placed inside the suction port when the interdental chamber volume reaches a minimum value.
  • the minimum volume (communication area) of the interdental chamber that is brought close to the periphery and no longer communicates with the discharge port can be increased more appropriately.
  • the interdental chamber (5x) in which the volume (V) decreases, the external teeth (20) and the internal teeth (30) that define the interdental chamber (5x). (E) is formed so as to communicate with the suction port (6) after overlapping the peripheral edge (8e) of the discharge port (8) when viewed from the (2) axial direction of the inner rotor. May be.
  • the interdental chamber whose volume decreases with the rotation of the inner rotor or the like is communicated with the suction port almost simultaneously with the discharge port, and the fluid in the interdental chamber flows out to the suction port. Can do. Therefore, it is possible to very well regulate the flow of fluid from the gap between the inner rotor and the outer rotor and the member that accommodates both into the interdental chamber that is no longer in communication with the discharge port.
  • the interdental chamber (5x) in which the volume (V) decreases is defined by the external teeth (20) and the internal teeth (30) that define the interdental chamber (5x).
  • (E) is formed so as to communicate with the suction port (6) before overlapping the peripheral edge (8e) of the discharge port (8) when viewed from the (2) axial direction of the inner rotor. Also good.
  • the interdental chamber whose volume decreases with the rotation of the inner rotor or the like is communicated with the suction port before it is not communicated with the discharge port, and an appropriate amount of fluid in the interdental chamber is transferred to the discharge port and the suction port. Can be drained. As a result, it is possible to keep the pressure of the fluid in the interdental chamber from rising more than necessary, and to suppress the occurrence of vibration due to the increase in the pressure of the fluid in the interdental chamber.
  • each of the external teeth (20) of the inner rotor (2) causes the outer circle (Co) having a radius (re) smaller than the radius (rde) of the drawing point to circumscribe the basic circle (BCt).
  • the tooth tip part (21) formed by the epitrochoid curve obtained by rolling without slipping may be included. That is, by keeping the radius of the abduction circle (the radius of the base circle / the number of teeth) small while increasing the drawing point radius of the epitrochoid curve, the outer diameter of the basic circle, that is, the outer diameter of the inner rotor is kept small. It is possible to easily increase the height of the external teeth.
  • each of the outer teeth (20) of the inner rotor (2) is formed by an arbitrary curve, and the inner rotor (2) more than the tooth tip portion (21) and the tooth tip portion (21).
  • a second intermediate portion (24) positioned between the tooth bottom portion (22) positioned on the rear side in the rotational direction of the inner rotor (2) relative to (21), and the first intermediate portion ( The length of the curve forming 23) may be longer than the length of the curve forming the second intermediate part (24).
  • the epitrochoid curve forming the tooth tip portion The rear end portion in the rotation direction can be brought closer to the tooth bottom portion, and the front end portion in the rotation direction of the epitrochoid curve can be brought closer to the outer side in the radial direction of the inner rotor. Then, by bringing the end of the epitrochoid curve forming the tooth tip portion on the rear side in the rotational direction closer to the tooth bottom portion, the minimum clearance between the external teeth and the internal teeth defining the interdental space communicating with the discharge port The value can be reduced as a whole.
  • the first intermediate part (23) may be formed by at least an involute curve.
  • the discharge port is separated from the first discharge port (7) by a first discharge port (7) and a partition wall (9), and the inner rotor (2) is separated from the first discharge port (7).
  • a second discharge port (8) arranged on the front side in the rotation direction.
  • the invention of the present disclosure can be used in the gear pump manufacturing industry.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
PCT/JP2016/076157 2015-09-07 2016-09-06 ギヤポンプ WO2017043478A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201680050919.9A CN107923390B (zh) 2015-09-07 2016-09-06 齿轮泵
DE112016002336.7T DE112016002336T8 (de) 2015-09-07 2016-09-06 Zahnradpumpe
US15/574,220 US20180172000A1 (en) 2015-09-07 2016-09-06 Gear pump

Applications Claiming Priority (2)

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JP2015175874A JP6599181B2 (ja) 2015-09-07 2015-09-07 ギヤポンプ
JP2015-175874 2015-09-07

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JP (1) JP6599181B2 (zh)
CN (1) CN107923390B (zh)
DE (1) DE112016002336T8 (zh)
WO (1) WO2017043478A1 (zh)

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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
CN109944792A (zh) * 2019-04-30 2019-06-28 哈尔滨理工大学 一种双压双向齿轮泵
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
DE102022130861A1 (de) 2022-11-22 2024-05-23 Klaus Stühmeier Fördereinrichtung für flüssiges oder gasförmiges Medium

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JP2005048767A (ja) * 2003-07-17 2005-02-24 Yamada Seisakusho Co Ltd トロコイド型オイルポンプ
JP2007064122A (ja) * 2005-08-31 2007-03-15 Mitsubishi Materials Pmg Corp 内接型ギヤポンプ
JP2009185644A (ja) * 2008-02-05 2009-08-20 Hitachi Ltd オイルポンプ
US20100215537A1 (en) * 2005-06-22 2010-08-26 Peter Lit Ming Chang Gear Pump With Improved Inlet Port
WO2016121291A1 (ja) * 2015-01-30 2016-08-04 アイシン機工株式会社 ギヤポンプおよびその製造方法

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JP2006214286A (ja) * 2005-02-01 2006-08-17 Aisin Seiki Co Ltd オイルポンプ
JP2006233771A (ja) * 2005-02-22 2006-09-07 Mitsubishi Materials Pmg Corp ポンプロータ
CN101832264B (zh) * 2005-09-22 2011-12-28 爱信精机株式会社 油泵转子
WO2014034717A1 (ja) * 2012-08-28 2014-03-06 アイシン・エィ・ダブリュ株式会社 ギヤポンプ
JP6080635B2 (ja) * 2013-03-19 2017-02-15 アイシン機工株式会社 ギヤポンプおよびインナーロータの製造方法

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JP2005048767A (ja) * 2003-07-17 2005-02-24 Yamada Seisakusho Co Ltd トロコイド型オイルポンプ
US20100215537A1 (en) * 2005-06-22 2010-08-26 Peter Lit Ming Chang Gear Pump With Improved Inlet Port
JP2007064122A (ja) * 2005-08-31 2007-03-15 Mitsubishi Materials Pmg Corp 内接型ギヤポンプ
JP2009185644A (ja) * 2008-02-05 2009-08-20 Hitachi Ltd オイルポンプ
WO2016121291A1 (ja) * 2015-01-30 2016-08-04 アイシン機工株式会社 ギヤポンプおよびその製造方法

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DE112016002336T8 (de) 2018-04-05
JP6599181B2 (ja) 2019-10-30
US20180172000A1 (en) 2018-06-21
CN107923390B (zh) 2019-05-07
CN107923390A (zh) 2018-04-17
DE112016002336T5 (de) 2018-02-15
JP2017053240A (ja) 2017-03-16

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