WO2022137706A1 - Structure de palier pour engrenage dans une pompe à engrenages externes - Google Patents

Structure de palier pour engrenage dans une pompe à engrenages externes Download PDF

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Publication number
WO2022137706A1
WO2022137706A1 PCT/JP2021/036031 JP2021036031W WO2022137706A1 WO 2022137706 A1 WO2022137706 A1 WO 2022137706A1 JP 2021036031 W JP2021036031 W JP 2021036031W WO 2022137706 A1 WO2022137706 A1 WO 2022137706A1
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WO
WIPO (PCT)
Prior art keywords
gear
bush
pump
leaf spring
pressure
Prior art date
Application number
PCT/JP2021/036031
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English (en)
Japanese (ja)
Inventor
真裕 谷田
健治 高宮
康由 梅木
亮宏 嶋村
Original Assignee
株式会社Ihi
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社Ihi filed Critical 株式会社Ihi
Priority to JP2022571064A priority Critical patent/JPWO2022137706A1/ja
Publication of WO2022137706A1 publication Critical patent/WO2022137706A1/fr
Priority to US18/164,884 priority patent/US20230184247A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0028—Internal leakage control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the present disclosure relates to a gear bearing structure [a structure a bearing for a gear in an external gear pump] of an external gear pump that sends out fluid by a pair of gears.
  • Japanese Patent Application Laid-Open No. 2000-145661 discloses an external gear pump.
  • the circumscribed gear pump includes a pair of driving gears and driven gears in the pump body. Gear teeth are formed on the outer circumferences of the drive gear and the driven gear.
  • the drive gear and the driven gear are sandwiched by side plates from both sides in the axial direction in a state of being meshed with each other.
  • a suction chamber [inlet chamber] for sucking fluid is formed on one side of the meshed portion [mesh portion] of the drive gear and the driven gear, and a discharge chamber [outlet chamber] for discharging the fluid is formed on the other side of the meshed portion. Will be done.
  • the drive gear and the driven gear start to mesh on the discharge chamber side and disengage on the suction chamber side. Fluid enters between the disengaged gear teeth, and as the gear teeth rotate, the fluid is held between the gear teeth and the inner surface of the pump body and sent to the discharge chamber along the circumferential direction [delivered]. ..
  • Each rotating shaft of the drive gear and the driven gear is supported by a fluid bearing.
  • a lubricating liquid film is formed by a fluid sent by a gear pump between the inner peripheral surface of each bushing that supports the rotating shaft and the outer peripheral surface of the rotating shaft. Further, the side surface of the gear is in sliding contact with the end surface of the bush.
  • An object of the present disclosure is to provide a gear bearing structure of a circumscribed gear pump capable of suppressing fluid leakage and discharging a fluid with stable accuracy.
  • the gear bearing structure of the external gear pump according to the present disclosure is formed on one side of the meshing portion of the drive gear and the driven gear rotatably housed inside the pump body of the external gear pump and the drive gear and the driven gear.
  • the bush is provided with an annular leaf spring arranged between the pump body and the bush and urging the bush toward at least one side surface of the drive gear or the driven gear.
  • the annular leaf spring may be a wave washer that undulates in the circumferential direction.
  • the gear bearing structure may further include a flow path for introducing a fluid from the discharge chamber at a position where the annular leaf spring is arranged.
  • FIG. 2 is a sectional view taken along line II-II in FIG.
  • FIG. 3 is a cross-sectional view taken along the line III-III in FIG.
  • It is sectional drawing of the external gear pump provided with the gear bearing structure which concerns on 2nd Embodiment (the figure corresponding to FIG. 1).
  • the circumscribed gear pump P provided with the gear bearing structure according to the first embodiment is used as a pump for sending liquid fuel to the engine.
  • the circumscribed gear pump P is also simply referred to as a gear pump P
  • the liquid fuel is also simply referred to as a fuel.
  • this fuel is also used as a lubricating liquid [lubricating liquid] that lubricates each part of the gear pump P.
  • the lubricating liquid is also referred to as lubricating oil [lubricating oil]. That is, in this embodiment, the fuel and the lubricating oil are the same.
  • both the terms fuel and lubricating oil will be used depending on the content of the explanation.
  • the gear pump P includes a pair of gears G in the pump body B.
  • the pump body B is composed of a main body B1, a side plate B2, a mid plate B3, and an end plate B4.
  • a gear storage chamber 1 for accommodating a pair of gears G in a meshed state is formed inside the main body B1.
  • the gear storage chamber 1 has an 8-shaped cross section perpendicular to the rotation axis [rotational axes] O of the gear G.
  • the gear G will be described in detail later, but a plurality of gear teeth are formed on the outer circumference of each gear G.
  • the tip of the gear tooth is in sliding contact with the inner peripheral surface of the gear storage chamber 1 via the lubricating liquid film.
  • a suction chamber 2I for sucking fuel from the outside is formed on one side of the constriction portion of the gear storage chamber 1, that is, a meshing portion of the gear G, and a discharge chamber 2O for discharging fuel on the other side. Is formed.
  • the gear pump P is a positive displacement pump, and the pressure PH in the discharge chamber 2O is higher than the pressure PL in the suction chamber 2I (PL ⁇ PH) due to the flow path resistance on the discharge chamber 2O side.
  • each rotation shaft [rotational shaft] GS of the gear G are rotatably held by the side plate B2 and the mid plate B3 via a cylindrical bush F described later.
  • the bush F will be described in detail later, but each bush F is a fluid bearing using a lubricating liquid film formed between the inner peripheral surface 100 (see FIGS. 4 and 5) and the outer peripheral surface of the rotary shaft GS. To configure.
  • This fluid bearing is also a plain bearing.
  • a ring-shaped end plate B4 is fixed to the outer surface of the mid plate B3. From the center of the end plate B4, one rotation shaft GS of the pair of gears G, that is, the rotation shaft GS1 of the first gear G1 extends to the outside.
  • the first gear G1 which is one of the pair of gears G, is a drive gear that is rotated by external power.
  • a spline is formed at the end of the rotary shaft GS1 of the first gear G1 (see FIG. 7), and the first gear G1 is connected to the drive source via the spline.
  • the first gear G1 and the second gear G2 rotate in opposite directions as shown by the arrows in FIG.
  • the gear profiles of the first gear G1 and the second gear G2, such as the shape and number of gear teeth, are the same.
  • the fuel in the suction chamber 2I is carried along the circumferential direction, that is, along the inner peripheral surface of the gear storage chamber 1, while being held between the gear teeth of the first gear G1 and the second gear G2. It is exposed and sent to the discharge chamber 2O.
  • the rotation shaft GS1 of the first gear G1 is a solid cylinder, and is integrally [monolithically] formed with the first gear G1 so as to penetrate the first gear G1.
  • An oil seal S is provided between the rotating shaft GS1 and the side plate B2 to allow the rotating shaft GS1 to rotate and prevent the lubricating oil from leaking.
  • An oil seal S is also provided between the rotary shaft GS1 and the mid plate B3 to prevent the lubricating oil from leaking while allowing the rotary shaft GS1 to rotate.
  • the rotation shaft GS2 of the second gear G2 is a hollow cylinder and is integrally formed with the second gear G2 so as to penetrate the second gear G2. Both ends of the rotation shaft GS2 are held by the side plate B2 and the mid plate B3 via the bush F, respectively.
  • the lubricating oil can flow through the inside of the rotary shaft GS2.
  • the portion of the rotation shaft GS1 of the first gear G1 on the mid plate B3 side is held by the first bush F11, and the portion on the side plate B2 side thereof is held by the second bush F12.
  • the portion of the rotating shaft GS2 of the second gear G2 on the mid plate B3 side is held by the first bush F21, and the portion of the side plate B2 side thereof is held by the second bush F22.
  • the first bush F11 of the first gear G1 and the first bush F21 of the second gear G2 of the present embodiment are rotating shafts at the center of the first gear G1 and the second gear G2. It is configured symmetrically with respect to a plane of symmetry parallel to the rotation axis O of the GS.
  • first bush F11 of the first gear G1 and the first bush F21 of the second gear G2 are the low-pressure side recess [low-pressure depressed portion] 101 and the high-pressure side recess [high-pressure depressed portion] 102a, which will be described later.
  • the shape is slightly different.
  • the symmetrically configured first bushes F11 and F21 will be described below with reference to the first bushes F11 shown in FIGS. 4 and 5.
  • the first bush F11 has a cylindrical shape, and a step portion is formed on the outer peripheral surface thereof.
  • a ring-shaped second surface P2 is formed on the step portion. That is, a large diameter portion and a small diameter portion are formed on the first bush F11 with the second surface P2 as a boundary, and the outer diameter of the large diameter portion is equal to the gear outer diameter of the first gear G1 (FIG. 2). reference).
  • a lubrication groove 103 is formed on the outer peripheral surface of the large-diameter portion to facilitate the sliding of the rotating shaft GS in the axial direction.
  • a part of the large diameter portion of the first bush F11 on the outer peripheral surface is formed as a contact plane 104.
  • the first bushes F11 and F21 are arranged on the mid plate B3 side in the gear storage chamber 1 in a state where the contact plane 104 is in contact with the contact plane 104 of the first bush F21 of the second gear G2. Therefore, the first bushes F11 and F21 are non-rotatably stored in the gear storage chamber 1.
  • the plane including the contact plane 104 is the above-mentioned symmetrical plane of the first bushes F11 and F21.
  • the inner diameter of the inner peripheral surface 100 of the first bush F11 is substantially equal to the outer diameter of the rotating shaft GS1 of the first gear G1, and a lubricating liquid film is formed between the inner peripheral surface 100 and the rotating shaft GS1. That is, the inner peripheral surface 100 is in sliding contact with the outer peripheral surface of the rotating shaft GS1 via the lubricating liquid film.
  • the second surface P2 is a plane perpendicular to the rotation axis O1 of the rotation axis GS1, and is the first surface P1 (see FIG. 6) of the circular protrusion 6 (see FIG. 1) of the mid plate B3. Facing.
  • An annular leaf spring [ring plate spring] 4 is interposed between the second surface P2 and the first surface P1 (see FIG. 4).
  • the annular leaf spring 4 of the present embodiment is a wave washer [wave washer] formed of a metal having a spring property.
  • the annular leaf spring 4 is arranged between the second surface P2 and the first surface P1 in a compressed state, that is, between the pump body B and the first bush F11, and the first bush F11 is placed on the side surface of the first gear G1. We are urging towards.
  • the rotary shaft GS1 is inserted into the central hole of the annular leaf spring 4.
  • the annular leaf spring 4 of the present embodiment is a wave washer that undulates in four cycles in the circumferential direction, and comes into contact with each of the first surface P1 and the second surface P2 at four points.
  • contact with each of the first surface P1 and the second surface P2 at three or more points. Is desirable.
  • the width of the annular leaf spring 4 is set according to the position where the width of the second surface P2 is the narrowest. Specifically, since the width of the second surface P2 is the narrowest at the center of the above-mentioned contact plane 104, the width of the annular leaf spring 4 is set to be substantially the same as this width, more specifically, slightly narrower. Has been done.
  • the first bush F11 has a third surface P3 facing the first gear G1.
  • the third surface P3 is also a plane perpendicular to the rotation axis O1 of the rotation shaft GS1, and is in sliding contact with the side surface of the first gear G1 via the lubricating liquid film.
  • a low pressure side recess 101 is formed from the third surface P3 to the outer peripheral surface and the portion of the contact plane 104 on the suction chamber 2I side.
  • the curved concave inner surface of the low pressure side recess 101 is a part of the suction chamber 2I.
  • a high-pressure side recess 102a is formed from the third surface P3 to the outer peripheral surface and the portion of the contact plane 104 on the discharge chamber 2O side.
  • the curved concave inner surface of the high-pressure side recess 102a is the inner surface of the discharge chamber 2O.
  • a tapered portion 102b extends from the high-pressure side recess 102a along the circumferential direction.
  • the tapered portion 102b forms a tapered surface between the third surface P3 and the outer peripheral surface.
  • the first bush F11 has a fourth surface P4 facing the mid plate B3.
  • the fourth surface P4 is also a plane perpendicular to the rotation axis O1 of the rotation axis GS1.
  • the pressure regions [pressure ranges] formed in the circumferential direction of the pair of gears G will be described with reference to FIG.
  • the pressure PH in the discharge chamber 2O is higher than the pressure PL in the suction chamber 2I (PL ⁇ PH). Therefore, a low pressure region [low-pressure range] L is formed along the inner circumference of the gear storage chamber 1 corresponding to the outer circumferences of the first gear G1 and the second gear G2 facing the suction chamber 2I.
  • This low pressure region L corresponds to the above-mentioned low pressure side recess 101.
  • a high pressure range [high-pressure range] H is formed along the inner circumference of the gear storage chamber 1 corresponding to the outer circumferences of the first gear G1 and the second gear G2 facing the discharge chamber 2O.
  • This high pressure region H corresponds to the above-mentioned high pressure side recess 102a.
  • the high-pressure side recess 102a is enlarged in the circumferential direction by the tapered portion 102b. Therefore, the high pressure region H is expanded to the tapered portion 102b.
  • the fuel is stored between the gear teeth of the gear G and carried in the circumferential direction.
  • the fuel pressure between the gear teeth is low if it is in the low pressure region L, and high if it is in the high pressure region H.
  • a pressure transition region [pressure transition range] T is formed in which the fuel pressure gradually shifts from low pressure to high pressure via the lubricating liquid film of the sliding portion.
  • the pressure transition region T can also be referred to as a pressure pressure region [pressure rising range].
  • the low pressure region L, the pressure transition region T, and the high pressure region H are partitioned corresponding to the outer periphery of the gear G.
  • a through groove 107 is formed on the inner peripheral surface 100 of the first bush F11.
  • the through groove 107 is located in the high pressure region H (see FIG. 3) described above.
  • the through groove 107 is formed in parallel with the rotation axis O1 of the rotation axis GS1 over the entire length from one end to the other end of the inner peripheral surface 100.
  • the inner surface of the through groove 107 is formed as a concave curved surface.
  • One end of the through groove 107 on the fourth surface P4 side communicates with the low-pressure lubricating oil of the suction chamber 2I through the inside of the mid plate B3.
  • the lubricating oil in the through groove 107 forms a lubricating liquid film between the inner peripheral surface 100 of the first bush F11 and the outer peripheral surface of the rotating shaft GS1.
  • the lubricating oil forming the lubricating liquid film is discharged from the end portion on the low pressure side on the fourth surface P4 side by the through groove 107, and the sliding surfaces are cooled by the circulation of the lubricating oil.
  • the second surface P2 of the first bush F11 or F21 faces the first surface P1 of the mid plate B3.
  • the first surface P1 is also a plane perpendicular to the rotation axis O of the rotation axis GS.
  • the first surface P1 is formed as an end surface of the circular convex portion 6 of the mid plate B3.
  • the circular protrusion 6 projects from the surface of the mid plate B3 facing the main body B1.
  • a first storage hole H1 for accommodating the end portion of the first bush F11 and a second storage hole H2 for accommodating the end portion of the first bush F21 are formed on the first surface P1 of the circular convex portion 6, a first storage hole H1 for accommodating the end portion of the first bush F11 and a second storage hole H2 for accommodating the end portion of the first bush F21 are formed. ..
  • the first storage hole H1 is a through hole having a step on the inner peripheral surface, and the rotation shaft GS1 of the first gear G1 penetrates the through hole.
  • the first storage hole H1 stores the small diameter portion of the first bush F11. Therefore, the second surface P2, which is the boundary between the small diameter portion and the large diameter portion of the first bush F11, faces the first surface P1. Similarly, the second storage hole H2 stores the small diameter portion of the first bush F21. Therefore, the second surface P2, which is the boundary between the small diameter portion and the large diameter portion of the first bush F21, also faces the first surface P1.
  • the above-mentioned compressed annular leaf spring 4 abuts on the first surface P1 and the second surface P2 and urges the first bushes F11 and F21 in a direction to separate them from the first surface P1.
  • FIG. 6 also shows a high-pressure supply passage [high-pressure supply passage] 5 for supplying high-pressure lubricating oil between the second surface P2 and the first surface P1.
  • the high-voltage supply path 5 will be described in detail later, but the open end [open end] 5c, which is the outlet end [outlet end] of the high-voltage supply path 5 of the present embodiment, is branched into a T shape, and one tip is the first.
  • One bush F11 faces the second surface P2, and the other tip faces the second surface P2 of the first bush F21. That is, the open end 5c faces the second surface P2 of both the first bush F11 and the first bush F21.
  • the high-pressure lubricating oil supplied between the first surface P1 and the second surface P2 urges the first bushes F11 and F21 together with the annular leaf spring 4.
  • the first bush F11 or F21 arranged on the mid plate B3 side has been described above.
  • the second bush F12 or F22 arranged on the side plate B2 side is partially different from the first bush F11 or F21.
  • the annular leaf spring 4 is not arranged at the position of the second surface P2 of the second bush F12 or F22.
  • the second bush F12 has a shape substantially symmetrical to the first bush F11 with respect to the first gear G1
  • the second bush F22 has a shape substantially symmetrical to the first bush F21 with respect to the second gear G2. have.
  • the lubricating oil in the through groove 107 forms a lubricating liquid film between the inner peripheral surface 100 of the first bush F21 and the outer peripheral surface of the rotating shaft GS1.
  • the lubricating oil forming the lubricating liquid film is discharged from the end portion on the low pressure side on the fourth surface P4 side by the through groove 107, and the lubricating oil circulates to cool the lubricating sliding surface.
  • the fourth surface P4 of the second bush F22 facing the side plate B2 and the fourth surface P4 of the first bush F21 facing the mid plate B3 communicate with each other via the inside of the rotation shaft GS2 of the second gear G2. There is.
  • the second bushes F12 and F22 are housed on the side plate B2 side of the gear storage chamber 1.
  • the first bushes F11 and F21 are urged in the direction away from the first surface P1 [in a direction away from the first surface P1] (left side in FIG. 1). That is, the first bushes F11 and F21 are urged toward the pair of gears G. Since the second surface P2 of the second bushes F12 and F22 abuts on the step portion of the main body B1, the position of the rotation axis GS in the rotation axis O direction is determined.
  • the pair of gears G are pushed by the urged first bushes F11 and F21, and are in sliding contact with the third surface P3 of the second bushes F12 and F22 on their side surfaces via the lubricating liquid film. As described above, the pair of gears G are in sliding contact with the first bush F11 and the third surface P3 of the F21 urged on the opposite side surfaces thereof via the lubricating liquid film. In this way, the sliding states of the gear G, the first bushes F11 and F21, and the second bushes F12 and F22 are stabilized.
  • the high voltage supply path 5 will be described with reference to FIG. 7.
  • the annular leaf spring 4 is not shown in FIG. 7 for the sake of clarity.
  • a supply port 8 for supplying high-pressure lubricating oil to the high-pressure supply path 5 is provided on the outer surface of the mid plate B3.
  • the supply port 8 is connected to a discharge port [discharge port] 9 for discharging high-pressure fuel in the discharge chamber 2O by a pipe (not shown).
  • the main path 5a of the high-voltage supply path 5 is formed linearly from the supply port 8 toward the slightly outward side of the circular convex portion 6.
  • the main road 5a is formed at a right angle to the rotation axis O of the rotation axis GS.
  • a sub road 5b of the high voltage supply road 5 is connected to the tip of the main road 5a (see also FIG. 6).
  • the secondary path 5b is formed parallel to the rotation axis O of the rotation axis GS, that is, at a right angle to the first surface P1. Then, the above-mentioned T-shaped branched open end 5c is formed at the tip of the secondary road 5b.
  • the high pressure supply path 5 may communicate the open end 5c and the discharge chamber 2O only inside the pump body B.
  • the high pressure supply path 5 is a part of the flow path for introducing the fluid from the discharge chamber 2O at the position where the annular leaf spring 4 is arranged, that is, at the position between the second surface P2 and the first surface P1.
  • the lubricating oil can be maintained at a high pressure over the entire circumference.
  • an annular leaf spring 4 is also interposed between the first surface P1 and the second surface P2, and the minute gap between the first surface P1 and the second surface P2 is high pressure. Functions as a reservoir for lubricating oil. As a result, high-pressure lubricating oil can be stably supplied from the open end 5c between the first surface P1 and the second surface P2.
  • the lubricating oil is applied between the peripheral surface of the gear G and the pump body B, between the side surface of the gear G and the third surface P3, and the outer peripheral surface of the rotary shaft GS and the bush F. It can move through the lubricating liquid film of the above-mentioned sliding portion formed between the inner peripheral surface 100 and the inner peripheral surface 100.
  • high-pressure lubricating oil is supplied between the second surface P2 of the first bushes F11 and F21 and the first surface P1 of the mid plate B3, and the second surface P2 and the first surface are supplied.
  • An annular leaf spring 4 is also interposed between P1 and P1.
  • the lubricating oil pressure and the annular leaf spring 4 urge the first bushes F11 and F21 toward the side surface of the gear G to suppress leakage of the lubricating oil between the side surface of the gear G and the third surface P3. do. As a result, the decrease in efficiency of the gear pump is suppressed. Further, since the leakage of the lubricating oil between the side surface of the gear G and the third surface P3 is suppressed, it is possible to suppress a decrease in the accuracy of the fuel discharge amount.
  • the pressure PH of the lubricating oil in the discharge chamber 2O is used as the lubricating oil pressure for urging the gear G.
  • the annular leaf spring 4 urges the first bushes F11 and F21 toward the side surface of the gear G, so that the side surface of the gear G and the third surface P3 Leakage of lubricating oil between them can be suppressed.
  • the pressure PH in the discharge chamber 2O rises, it seems likely that the leakage of the lubricating oil between the side surface of the gear G and the third surface P3 in the high pressure region H (see FIG. 3) described above is likely to increase.
  • the pressure PH acts between the second surface P2 and the first surface P1
  • the lubricating oil pressure and the urging force of the first bushes F11 and F21 by the annular leaf spring 4 also increase. Therefore, leakage of the lubricating oil between the side surface of the gear G and the third surface P3 can be suppressed as it is.
  • the above-mentioned urging mechanism provided with the annular leaf spring 4 is compared with the following urging mechanism.
  • a plurality of storage holes [accommodation holes] for accommodating coil springs in a compressed state are provided on the second surface P2 along the circumferential direction, and the first bush F11 and the first bush F11 and the plurality of coil springs are provided.
  • the F21 is urged toward the side surface of the gear G.
  • the number of parts increases due to the coil spring.
  • the manufacturing process such as the processing process of the storage hole and the storage process of the coil spring in the storage hole will be increased. Further, the manufacturing process is complicated because the coil spring must be assembled in the storage hole.
  • the manufacture of the gear pump P becomes complicated.
  • the annular leaf spring 4 is naturally positioned when it is inserted into the small diameter portions of the first bushes F11 and F21. Does not occur.
  • the width in the radial direction of the second surface P2 in order to machine the storage hole, the width in the radial direction of the second surface P2 must be widened, that is, the area of the second surface P2 must be widened. Since the pressure PH in the discharge chamber 2O is used for urging the first bushes F11 and F21, this means that the area receiving the pressure PH is widened. Therefore, when the rotation speed of the gear G becomes high and the pressure PH becomes high, there is a concern that the urging force of the first bushes F11 and F21 becomes too high. Excessive urging force of the first bushes F11 and F21 increases the rotational resistance of the gear G, which causes a decrease in pump efficiency and wear of the gear G and the bush F.
  • the configuration of this comparative example may limit the degree of freedom in designing the gear pump P.
  • the degree of freedom in designing the radial width of the second surface P2 is high, and the degree of freedom in designing the gear pump P can be improved. More specifically, it is easy to arbitrarily set the ratio of the area of the second surface P2 on the high pressure side and the area of the fourth surface P4 on the low pressure side, and the degree of freedom in designing the urging force by the lubricating oil pressure can be increased.
  • the annular leaf spring 4 is provided between the fourth surface P4 of the first bush F11 and the bottom surface of the first storage hole H1, and the fourth surface P4 and the second storage hole H2 of the first bush F21. It is provided between the bottom surface (see also FIG. 6).
  • the first storage hole H1 and the second storage hole H2 are formed in the circular convex portion 6 of the mid plate B3.
  • FIG. 9 shows only the first bush F11 among the first bushes F11 and F21, but the portion on the first bush F21 side is also symmetrically configured as in the first embodiment. This will be described below with reference to the first bush F11 shown in FIG.
  • the annular leaf spring 4 of the present embodiment is also a wave washer formed of a metal having a spring property.
  • the annular leaf spring 4 is arranged in a compressed state between the fourth surface P4 and the bottom surface of the first storage hole H1, that is, between the pump body B and the first bush F11, and the first bush F11 is the first gear. It is urging toward the side of G1.
  • the rotary shaft GS1 is inserted into the central hole of the annular leaf spring 4.
  • the annular leaf spring 4 of the present embodiment is also a wave washer in a form of waving in four cycles in the circumferential direction.
  • the width of the annular leaf spring 4 is substantially equal to the width of the fourth surface P4.
  • the pressure PL in the suction chamber 2I is introduced between the fourth surface P4 and the bottom surface of the first storage hole H1, that is, at the position where the annular leaf spring 4 is arranged.
  • the pressure PH in the discharge chamber 2O is introduced between the first surface P1 and the second surface P2. Therefore, the annular leaf spring 4 and the pressure PH urge the first bush F11 toward the side surface of the first gear G1.
  • the annular leaf spring 4 is positioned when it is inserted into the rotary shaft GS1.
  • the first bushes F11 and F21 are urged toward the side surface of the gear G by the lubricating oil pressure and the annular leaf spring 4, and the side surface of the gear G and the first Leakage of lubricating oil between the three sides P3 can be suppressed. As a result, the decrease in efficiency of the gear pump is suppressed. Further, since the leakage of the lubricating oil between the side surface of the gear G and the third surface P3 is suppressed, it is possible to suppress a decrease in the accuracy of the fuel discharge amount. Further, in the present embodiment, the degree of freedom in designing the area of the second surface P2, that is, the degree of freedom in designing the urging forces of the first bushes F11 and F21 due to the lubricating oil pressure is higher than in the first embodiment.
  • the gear bearing structure according to the present disclosure includes a cylindrical bush F that supports the rotating shaft GS.
  • the bush F forms a lubricating liquid film with at least one rotating shaft GS of the drive gear G1 or the driven gear G2.
  • the gear bearing structure according to the present disclosure also includes an annular leaf spring 4 which is arranged between the pump body B and the bush F and urges the bush F toward at least one side surface of the drive gear G1 or the driven gear G2. I have. Therefore, the annular leaf spring 4 suppresses fluid leakage between the bush F and the side surface of the drive gear G1 or the driven gear G2. As a result, it is possible to suppress the leakage of the fluid and discharge the fluid with a stable discharge amount accuracy.
  • the bush F can be stably urged toward the side surface of the drive gear G1 or the driven gear G2. Since the wave washer has a form of waving in the circumferential direction, the bush F can be urged more uniformly over the entire circumference and the bush F can be urged accurately in the direction of the rotation axis GS of the gear G. Therefore, since the third surface P3 of the bush F is uniformly slidably contacted with the side surface of the gear G, fluid leakage can be stably suppressed. As a result, the fluid can be discharged with a more stable discharge amount accuracy.
  • the bush F in the flow path for introducing the fluid from the discharge chamber 2O at the position where the annular leaf spring 4 is arranged, that is, at the position between the first surface P1 and the second surface P2.
  • a high voltage supply path 5 is further provided. Therefore, the bush F can be stably urged toward the side surface of the drive gear G1 or the driven gear G2 by the high pressure PH in the discharge chamber 2O and the annular leaf spring 4. Since the position where the annular leaf spring 4 is arranged, that is, the position between the first surface P1 and the second surface P2 is the reservoir of the supplied fluid, the pressure can be stably applied to the bush F. can.
  • the annular leaf spring 4 secures the bias of the bush F.
  • the bush F is urged by the pressure PH, so that fluid leakage can be stably suppressed even if the rotation speed increases. As a result, the fluid can be discharged with a more stable discharge amount accuracy.
  • the annular leaf spring 4 is a wave washer having a seamless and completely annular shape.
  • the annular leaf spring 4 may be a single-winding wave spring cut in the radial direction.
  • the annular leaf spring 4 may be a C-shape in which the cut ends are separated, or it may be an annular shape in which the cut ends are overlapped.
  • the annular leaf spring 4 may be a disc spring.
  • it may be a disc spring or a disc spring in which a large number of cuts [slots] are formed from one or both of the inner peripheral edge and the outer peripheral edge.
  • the annular leaf spring 4 is preferably provided for both the drive gear and the driven gear, but may be provided for only one of them. The above-mentioned effect can be obtained in the gear provided with the annular leaf spring 4.

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

Abstract

La présente invention concerne une structure d'un palier pour un engrenage dans une pompe à engrenages externes (P) comprenant : un engrenage d'entraînement (G1) et un engrenage entraîné (G2) qui sont logés rotatifs à l'intérieur d'un corps de pompe (B) de la pompe à engrenages externes (P) ; une chambre d'entrée (2I) formée sur un côté d'une partie maille entre l'engrenage d'entraînement (G1) et l'engrenage entraîné (G2) ; une chambre de sortie (2O) formée sur l'autre côté de la partie maille ; une douille cylindrique (F) formant un film de liquide de lubrification dans un espace par rapport à un arbre rotatif (GS) de l'engrenage d'entraînement (G1) et/ou de l'engrenage entraîné (G2) pour supporter l'arbre rotatif (GS) ; et un ressort à plaque annulaire (4) qui est disposé entre le corps de pompe (B) et la douille (F) et qui sollicite la douille (F) vers une surface latérale de l'engrenage d'entraînement (G1) et/ou de l'engrenage entraîné (G2).
PCT/JP2021/036031 2020-12-21 2021-09-30 Structure de palier pour engrenage dans une pompe à engrenages externes WO2022137706A1 (fr)

Priority Applications (2)

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JP2022571064A JPWO2022137706A1 (fr) 2020-12-21 2021-09-30
US18/164,884 US20230184247A1 (en) 2020-12-21 2023-02-06 Bearing structure for gear in external gear pump

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JP2020-211215 2020-12-21
JP2020211215 2020-12-21

Related Child Applications (1)

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US18/164,884 Continuation US20230184247A1 (en) 2020-12-21 2023-02-06 Bearing structure for gear in external gear pump

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5566682A (en) * 1978-11-03 1980-05-20 Bosch Gmbh Robert Gear machine
JP2000130358A (ja) * 1998-10-28 2000-05-12 Toyota Motor Corp 外接ギヤポンプ
CN106050647A (zh) * 2015-04-17 2016-10-26 施瓦本冶金工程汽车有限公司 泵

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5566682A (en) * 1978-11-03 1980-05-20 Bosch Gmbh Robert Gear machine
JP2000130358A (ja) * 1998-10-28 2000-05-12 Toyota Motor Corp 外接ギヤポンプ
CN106050647A (zh) * 2015-04-17 2016-10-26 施瓦本冶金工程汽车有限公司 泵

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JPWO2022137706A1 (fr) 2022-06-30
US20230184247A1 (en) 2023-06-15

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