WO2017169552A1 - Machine rotative hydraulique - Google Patents

Machine rotative hydraulique Download PDF

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Publication number
WO2017169552A1
WO2017169552A1 PCT/JP2017/008898 JP2017008898W WO2017169552A1 WO 2017169552 A1 WO2017169552 A1 WO 2017169552A1 JP 2017008898 W JP2017008898 W JP 2017008898W WO 2017169552 A1 WO2017169552 A1 WO 2017169552A1
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WO
WIPO (PCT)
Prior art keywords
retainer
swash plate
piston
piston rod
rotation
Prior art date
Application number
PCT/JP2017/008898
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English (en)
Japanese (ja)
Other versions
WO2017169552A9 (fr
Inventor
智史 前川
直紀 菅野
啓 森田
Original Assignee
株式会社神戸製鋼所
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
Priority claimed from JP2016249264A external-priority patent/JP6688724B2/ja
Application filed by 株式会社神戸製鋼所 filed Critical 株式会社神戸製鋼所
Priority to US16/084,848 priority Critical patent/US10808686B2/en
Priority to EP17774097.4A priority patent/EP3438451B1/fr
Priority to CN201780018146.0A priority patent/CN108884815B/zh
Publication of WO2017169552A1 publication Critical patent/WO2017169552A1/fr
Publication of WO2017169552A9 publication Critical patent/WO2017169552A9/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons

Definitions

  • the present invention relates to a hydraulic rotating machine that can be used as a hydraulic pump and a hydraulic motor.
  • variable displacement hydraulic rotating machines that can be used as hydraulic pumps or hydraulic motors are known.
  • a hydraulic rotating machine includes a housing, a rotating shaft, a cylinder block, and a plurality of pistons.
  • the rotating shaft is rotatably supported by the housing.
  • the cylinder block includes a plurality of cylinders formed around the central axis of the rotation shaft, and rotates together with the rotation shaft.
  • the pistons are respectively accommodated in a plurality of cylinders of the cylinder block and reciprocate as the cylinder block rotates.
  • the rotating shaft is rotated by the output of a predetermined driving unit, so that the cylinder block rotates together with the rotating shaft, and each piston reciprocates.
  • the hydraulic oil flows into the cylinder of the cylinder block from the predetermined low pressure port, is pressurized by the piston, and is discharged from the predetermined high pressure port.
  • the hydraulic rotating machine when used as a hydraulic motor, the high-pressure hydraulic oil flows into the cylinder of the cylinder block from the high-pressure port, so that the hydraulic fluid that has flowed in acts on the piston. After the reciprocating motion of the piston rotates the rotating shaft together with the cylinder block, the hydraulic oil is discharged from the low pressure port.
  • Patent Document 1 discloses a swash plate type hydraulic pump.
  • the hydraulic pump includes a swing member that is swingably supported in the housing, and a swash plate that is rotatably supported by the swing member.
  • the swash plate is rotated about an axis independent of the rotation axis while being in contact with the plunger (piston). Further, the tilt angle of the swash plate with respect to the rotation axis is adjusted by swinging the swing member.
  • the stroke of the reciprocating motion of the piston is adjusted according to the inclination angle of the swash plate, and the discharge amount of the hydraulic pump is made variable.
  • the plunger and the swash plate are provided with hemispherical portions having different curvatures. Since the swash plate is rotated about an axis independent of the rotation shaft, the plunger reciprocates while making point contact between the hemispherical portion of the plunger and the hemispherical portion of the swash plate. For this reason, a sliding resistance locally increases at the contact portion between the plunger and the swash plate, and the seizure of the plunger is likely to occur. As a result, there is a problem that a large amount of leakage of the lubricating hydraulic oil is required, and the volumetric efficiency of the hydraulic rotating machine is reduced.
  • An object of the present invention is to provide a hydraulic rotating machine that reduces the sliding resistance of a reciprocating piston and suppresses a decrease in volumetric efficiency according to the amount of leakage of hydraulic oil.
  • a variable capacity hydraulic rotating machine includes a housing, a rotating shaft rotatably supported by the housing, and a plurality of cylinders arranged at intervals around the rotating shaft.
  • a cylinder block that rotates integrally with the rotary shaft around a central axis of the rotary shaft, and is accommodated in the plurality of cylinders of the cylinder block, and the inside of the cylinder moves along the cylinder block as the cylinder block rotates.
  • the retainer bush has a spherical shape with a first curvature, includes a retainer inner circumferential surface that is slidable with respect to the bush outer circumferential surface, and is supported by the retainer bush so as to be swingable about an axis perpendicular to the rotation axis.
  • the retainers are arranged so as to extend in the axial direction, connect the plurality of pistons and the retainers, and interlock the rotation of the plurality of pistons around the central axis with the retainers around the central axis.
  • the retainer is interposed between the swash plate and the retainer in the axial direction, and supports the retainer so that the retainer can rotate about the central axis with respect to the swash plate.
  • the retainer By oscillating the last bearing and the swash plate about the axis, the retainer is oscillated around the axis through the thrust bearing while the retainer inner peripheral surface and the bush outer peripheral surface are in sliding contact with each other.
  • a tilt adjustment mechanism that adjusts the amount of movement of the piston in the reciprocating motion in the axial direction.
  • FIG. 2 is a cross-sectional view showing a state in which a swash plate is inclined in the hydraulic rotating machine of FIG. 1.
  • FIG. 2 is a schematic diagram which shows the rotation locus
  • the hydraulic rotary machine which concerns on one Embodiment of this invention it is a schematic diagram which shows the rotation locus
  • FIG. 1 is a perspective view of a piston pump 1 according to an embodiment of the hydraulic rotating machine of the present invention.
  • FIG. 2 is an enlarged cross-sectional view in which a part of the piston pump 1 of FIG. 1 is enlarged.
  • FIG. 3 is a cross-sectional view showing a state in which a later-described swash plate 16 is inclined in the piston pump 1 of FIG.
  • FIG. 4A is a schematic diagram showing a rotation locus of the piston rod 14 when the swash plate 16 is not inclined in the piston pump 1
  • FIG. 4B is a rotation of the piston rod 14 when the swash plate 16 is inclined. It is a schematic diagram which shows a locus
  • FIG. 5 is an enlarged cross-sectional view for explaining the swing of the piston rod 14 in the piston pump 1.
  • directions of “up”, “down”, “left”, “right”, “front” and “rear” are shown, but the directions are related to the present embodiment. It is shown for convenience in order to describe the structure of the piston pump 1, and does not limit the usage mode of the hydraulic rotating machine according to the present invention.
  • the variable displacement piston pump 1 functions as a hydraulic pump that discharges hydraulic oil by being connected to a drive unit 100 such as an engine.
  • the piston pump 1 includes a housing 10, a rotating shaft 11, a cylinder block 12, a plurality of piston heads 13 (pistons), and a piston rod 14. Furthermore, the piston pump 1 includes a retainer 15, a swash plate 16, a tilt adjustment mechanism 17, a thrust bearing 18, and a swash plate receiving portion 19 (swash plate support portion).
  • the housing 10 functions as a housing that supports each member of the piston pump 1.
  • the rotating shaft 11 is rotatably supported by the housing 10.
  • the rotary shaft 11 is connected to the drive unit 100 and is rotated in the direction of the arrow in FIG. 3 by a rotational driving force generated by the drive unit 100.
  • the left end side of the rotating shaft 11 is rotatably supported by a roller bearing 20 disposed in the housing 10.
  • the right end side of the rotating shaft 11 is similarly rotatably supported by a needle bearing 21 disposed in the housing 10.
  • an oil seal 23 and an O-ring 24 are disposed on the left side of the roller bearing 20 in order to prevent leakage of hydraulic oil in the piston pump 1.
  • a first flow path 10A and a second flow path 10B for discharging and sucking hydraulic oil are formed on the right end side of the housing 10.
  • a retainer bush 11A is provided at a substantially central portion of the rotating shaft 11 in the left-right direction.
  • the retainer bush 11A is a cylindrical member whose outer peripheral surface (retainer bush spherical surface portion 11B) (FIG. 2) has a spherical shape.
  • the retainer bush 11 ⁇ / b> A is supported by the rotary shaft 11 so as to be rotatable around the central axis of the rotary shaft 11 in conjunction with the rotation of the rotary shaft 11.
  • the retainer bush 11 ⁇ / b> A is fitted on the outer peripheral portion of the rotary shaft 11 so as to be able to rotate integrally with the rotary shaft 11.
  • retainer bushing spherical surface portion 11 ⁇ / b> B (bushing outer peripheral surface) has a convex shape toward the outside in the radial direction in the rotation of rotating shaft 11 and a spherical surface having a first curvature centered on spherical surface center SC. It has a shape.
  • the spherical center SC is arranged on the center line (rotation axis) of the rotation shaft 11.
  • the retainer bushing spherical surface portion 11B has a function of supporting a retainer 15 described later in a swingable manner.
  • the cylinder block 12 is a substantially cylindrical unit disposed around the rotating shaft 11.
  • the cylinder block 12 is engaged with the rotating shaft 11 by a spline 11S.
  • the cylinder block 12 rotates around the central axis of the rotation shaft 11 integrally with the rotation shaft 11.
  • a bush 22 is inserted between the rotating shaft 11 and the inner peripheral surface of the cylinder block 12 on the left side of the spline 11S.
  • the bush 22 has a function of absorbing the swinging of the cylinder block 12 caused by the rattling of the spline 11S when the cylinder block 12 rotates.
  • the cylinder block 12 includes a plurality of cylinders 12S arranged around the rotation shaft 11 at intervals.
  • the cylinder 12S is a cylindrical space that extends in the left-right direction. In the present embodiment, nine cylinders 12S are provided around the rotation shaft 11 at equal intervals.
  • a control opening 12T (see FIG. 5) is formed in each cylinder 12S.
  • a valve plate 25 is fixed between the cylinder block 12 and the right end side portion of the housing 10. The valve plate 25 slides with the cylinder block 12 without rotating (see the sliding surface T in FIG. 5).
  • the valve plate 25 is a member having a substantially disk shape arranged around the rotation shaft 11. A plurality of valve openings 25H are opened in the valve plate 25.
  • valve openings 25H communicate with the first flow path 10A described above, and other valve openings 25H communicate with the second flow path 10B.
  • the control openings 12T (FIG. 5) of the plurality of cylinders 12S communicate with the first flow path 10A or the second flow path 10B in order via the valve openings 25H.
  • the hydraulic rotating machine functions as the piston pump 1 as in the present embodiment
  • the low pressure side cylinder 12S is communicated with the first flow path 10A on the suction side
  • the high pressure side cylinder 12S is connected to the discharge side.
  • the hydraulic rotating machine functions as the piston motor 1A (see FIG. 6) as in the modified embodiment described later
  • the high pressure side cylinder 12S is communicated with the second flow path 10B on the suction side
  • the low pressure The cylinder 12S on the side communicates with the first flow path 10A on the discharge side.
  • the piston head 13 is accommodated in a plurality of cylinders 12S of the cylinder block 12, respectively.
  • the piston head 13 rotates around the central axis of the rotary shaft 11 together with the cylinder block 12 while reciprocating along the axial direction (left-right direction) in the cylinder 12S as the cylinder block 12 rotates.
  • the volume of the cylinder 12S fluctuates, and hydraulic oil is sucked and discharged.
  • the plurality of piston rods 14 are arranged so as to extend in the axial direction (left-right direction) of the rotary shaft 11 and connect the plurality of piston heads 13 and the retainer 15 respectively.
  • the piston rod 14 has a function of rotating the retainer 15 around the central axis in conjunction with the rotation of the plurality of piston heads 13 around the central axis.
  • the piston rod 14 is a rod-shaped member having a substantially cylindrical shape. More specifically, the piston rod 14 includes a head side end portion 141 (one end side) and a retainer side end portion 142 (the other end side). An oil groove 143 extending in the left-right direction is formed inside the piston head 13 and the piston rod 14.
  • the oil groove 143 feeds part of the hydraulic oil in the cylinder 12 ⁇ / b> S between the retainer side end 142 and the retainer 15. As a result, seizure of the piston head 13, the piston rod 14, and the retainer 15 is prevented when the rotating shaft 11 is rotated in accordance with the operation of the piston pump 1.
  • the head-side end portion 141 has a spherical shape and is connected to a hemispherical (spherical shape) piston head support portion 13S (FIG. 5) (first connection portion) formed inside the piston head 13.
  • the head-side end portion 141 and the piston head support portion 13S are in surface contact with each other along the spherical surface. That is, the head side end portion 141 of the piston rod 14 and the piston head support portion 13S are coupled so as to be relatively rotatable.
  • the left end side of the head side end 141 is locked by the head fixing ring 13A (FIGS. 1 and 5). Further, the head fixing ring 13A is fixed by a retaining ring 13B.
  • the head-side end portion 141 is supported by the piston head 13 so as to be swingable in the radial direction and the circumferential direction (around the central axis of the rotary shaft 11) in the rotation of the rotary shaft 11. Further, the head-side end portion 141 is connected to the piston head 13, whereby the plurality of piston heads 13 and the piston rod 14 rotate together with the rotating shaft 11.
  • the retainer side end 142 has a spherical shape, and is fitted and connected to a hemispherical (spherical shape) retainer support portion 15D (FIG. 5) (second connection portion) formed inside the retainer 15. .
  • the retainer side end 142 is supported by the retainer 15 so as to be swingable in the radial direction and the circumferential direction (around the central axis of the rotation shaft) in the rotation of the rotation shaft 11.
  • the retainer side end 142 and the retainer support 15D are in surface contact with each other along the spherical surface. That is, the retainer side end portion 142 of the piston rod 14 and the retainer support portion 15D are coupled so as to be relatively rotatable.
  • the contact pressure between the piston rod 14, the piston head 13, and the retainer 15 can be reduced.
  • seizure of the piston rod 14 is suppressed.
  • the retainer side end 142 is connected to the retainer 15, whereby the plurality of piston rods 14 and the retainer 15 rotate together with the rotating shaft 11.
  • the retainer 15 is disposed to face the cylinder block 12 in the axial direction of the rotating shaft 11.
  • the retainer 15 is a ring-shaped member whose inner peripheral surface (retainer spherical portion 15A) has a predetermined spherical shape.
  • the retainer spherical portion 15A of the retainer 15 is slidably fitted to the retainer bush spherical portion 11B of the retainer bush 11A.
  • the retainer 15 is supported by the retainer bush 11A so as to be swingable around an axis extending in a direction orthogonal to the rotation shaft 11 (a direction intersecting the rotation shaft 11 and orthogonal to the paper surface of FIG. 1, the front-rear direction).
  • the above-described axis extends through the spherical surface center SC of FIG. 2 and extends in a direction perpendicular to the paper surface of FIG.
  • the retainer 15 includes a retainer spherical portion 15A (retainer inner peripheral surface), a sliding portion 15B, a swash plate facing portion 15C (retainer outer peripheral surface), and the retainer support portion described above. 15D (second shaft support).
  • the retainer spherical surface portion 15 ⁇ / b> A is an inner peripheral surface of the retainer 15 that continuously extends around the central axis of the rotation shaft 11.
  • the retainer spherical portion 15A has a concave shape toward the radially outer side in the rotation of the rotation shaft 11, and a spherical shape having the same first curvature as the retainer bush spherical portion 11B.
  • the retainer 15 swings left and right with the spherical center SC in FIG. 2 as a fulcrum.
  • the retainer spherical surface portion 15A is in sliding contact with the retainer bushing spherical surface portion 11B.
  • the sliding portion 15 ⁇ / b> B is composed of the left side surface of the retainer 15 and is disposed so as to face the thrust bearing 18.
  • the swash plate facing portion 15C corresponds to the outer peripheral surface of the retainer 15 that is disposed on the radially outer side than the retainer spherical portion 15A.
  • the swash plate 16 is supported in the housing 10 so as to be swingable.
  • the swash plate 16 is disposed to face the retainer 15 on the opposite side of the cylinder block 12 in the axial direction.
  • the swash plate 16 is swung by a tilt adjustment mechanism 17.
  • the swash plate 16 has a substantially hemispherical shape disposed around the rotation shaft 11 so as to face the retainer 15, and includes a swash plate adjusting portion 161 extending from an upper end portion thereof.
  • the swash plate adjustment unit 161 is moved left and right by the tilt adjustment mechanism 17. As a result, the swash plate 16 swings left and right with the spherical center SC of FIG. 2 as a fulcrum.
  • the swash plate 16 includes a bearing fixing portion 162 (fixed surface), a swash plate spherical portion 163 (supported portion), and a retainer facing portion 164 (facing surface) in addition to the swash plate adjusting portion 161 described above.
  • the thrust bearing 18 is fixed to the bearing fixing portion 162.
  • the bearing fixing portion 162 is a ring-shaped wall surface extending in a direction orthogonal to the axial direction of the rotating shaft 11.
  • the swash plate spherical surface portion 163 is disposed on the left side of the bearing fixing portion 162, in other words, on the opposite side of the bearing fixing portion 162 in the axial direction.
  • the swash plate spherical surface portion 163 is formed of a part of a spherical surface having a spherical center SC concentric with the retainer bushing spherical surface portion 11B.
  • the spherical shape of the swash plate spherical surface portion 163 has a second curvature smaller than the first curvature of the retainer bushing spherical surface portion 11B.
  • the spherical shape of the retainer bushing spherical portion 11B is a shape along the first virtual spherical surface SP1
  • the spherical shape of the swash plate spherical portion 163 is concentric with the first virtual spherical surface SP1. It has a shape along the second phantom spherical surface SP2.
  • the radius of the second phantom spherical surface SP2 (the radius of curvature of the retainer bushing spherical surface portion 11B) is larger than the radius of the first phantom spherical surface SP1 (the radius of curvature of the swash plate spherical surface portion 163).
  • the retainer facing portion 164 is an inner peripheral surface of the swash plate 16 disposed to face the swash plate facing portion 15C of the retainer 15 in the radial direction. Although not shown in detail in FIG. 2, a predetermined gap is formed between the swash plate facing portion 15 ⁇ / b> C and the retainer facing portion 164. In the present embodiment, the swash plate 16 is not in direct contact with the retainer 15.
  • the tilt adjustment mechanism 17 is disposed above the cylinder block 12.
  • the tilt adjustment mechanism 17 swings the swash plate 16 left and right around the spherical center SC in FIG. 2 to bring the retainer spherical surface portion 15A and the retainer bush spherical surface portion 11B into sliding contact with each other via the thrust bearing 18.
  • the retainer 15 is swung around the spherical surface center SC.
  • the tilt adjustment mechanism 17 adjusts the amount of movement in the axial direction in the reciprocating motion of the piston head 13. That is, the tilt adjustment mechanism 17 has a function of adjusting the flow rate discharge amount of the piston pump 1.
  • the tilt adjustment mechanism 17 includes a swash plate switching unit 171, a first tilt adjustment unit 172, and a second tilt adjustment unit 173.
  • the swash plate switching unit 171 is fitted in a recess formed at the upper end of the swash plate adjusting unit 161.
  • the driving force transmitted to the swash plate switching unit 171 causes the swash plate adjusting unit 161 to swing left and right.
  • the first tilt adjustment unit 172 biases the swash plate adjustment unit 161 from the right side.
  • the second tilt adjustment unit 173 biases the swash plate adjustment unit 161 from the left. Since the first tilt adjustment unit 172 and the second tilt adjustment unit 173 have the same structure, the structure of the first tilt adjustment unit 172 will be described below as an example.
  • the first tilt adjustment portion 172 includes a tilt piston 174, an adjustment housing 175, a shaft 176, a tilt piston spring 178, and a fixing portion 179.
  • the adjustment housing 175 supports each member of the first tilt adjustment unit 172.
  • the tilting piston 174 is slidable in the left-right direction inside the adjustment housing 175.
  • the tip end portion (left end portion) of the tilting piston 174 is in contact with the swash plate adjusting portion 161 of the swash plate 16.
  • the shaft 176 is a shaft portion that extends inside the adjustment housing 175.
  • the right end portion of the adjustment housing 175 is fixed to the shaft 176 by a nut-shaped fixing portion 179.
  • a tilting piston spring 178 made of a coil spring is disposed between the inner periphery of the tilting piston 174 and the adjustment housing 175.
  • the tilting piston 174 biases the swash plate adjusting portion 161 to the left.
  • O-rings 175A and 177A for preventing oil leakage are disposed inside the adjustment housing 175 and on the outer periphery of the tilt stopper 177, respectively.
  • the thrust bearing 18 is interposed between the swash plate 16 and the retainer 15 in the axial direction of the rotary shaft 11. Specifically, the thrust bearing 18 is disposed between the bearing fixing portion 162 of the swash plate 16 and the sliding portion 15B of the retainer 15. The thrust bearing 18 supports the retainer 15 so that the retainer 15 can rotate around the central axis of the rotation shaft 11 with respect to the swash plate 16.
  • the swash plate receiving portion 19 (FIG. 1) is a member that is disposed in the housing 10 so as to face the swash plate 16 and has a substantially hemispherical shape.
  • the swash plate receiving portion 19 includes a spherical surface 19 ⁇ / b> A that faces the swash plate spherical portion 163 (FIG. 2) of the swash plate 16.
  • the spherical surface 19A has the same second curvature as the swash plate spherical surface portion 163 of the swash plate 16 (FIG. 2).
  • the swash plate receiving portion 19 supports the swash plate spherical portion 163 of the swash plate 16 so that the swash plate 16 can swing left and right around the spherical center SC. Therefore, when the swash plate 16 is swung left and right by the tilt adjustment mechanism 17, the swash plate spherical surface portion 163 is in sliding contact with the spherical surface 19A while being in surface contact.
  • the swash plate receiving portion 19 is disposed in the housing 10 so that the swash plate receiving portion 19 and the thrust bearing 18 sandwich a part of the swash plate 16 in the axial direction (left-right direction). .
  • the piston pump 1 includes a block support portion 26 and a block urging spring 27 (FIG. 1).
  • the block support portion 26 and the block biasing spring 27 are arranged on the radial position side of the piston rod 14.
  • the block support portion 26 is a ring-shaped member that comes into contact with the retainer bushing spherical surface portion 11B (FIG. 2) of the retainer bushing 11A.
  • the portion of the block support portion 26 that contacts the retainer bushing spherical surface portion 11 ⁇ / b> B has a spherical shape with the same curvature as the retainer spherical surface portion 15 ⁇ / b> A of the retainer 15.
  • the block biasing spring 27 is a spring member interposed between the block support portion 26 and the cylinder block 12.
  • the block urging spring 27 urges the cylinder block 12 toward the valve plate 25.
  • swinging of the cylinder block 12 in the axial direction (left-right direction) is reduced by the elastic force of the block urging spring 27.
  • the swash plate adjusting unit 161 When the tilt of the piston pump 1 is adjusted, the swash plate adjusting unit 161 is moved in the direction of the arrow D1 (FIG. 3) by the tilt adjusting mechanism 17 from the state shown in FIG. At this time, the external force applied to the swash plate switching unit 171 (FIG. 1) and the urging force of the tilt piston spring 178 of the first tilt adjustment unit 172 and the second tilt adjustment unit 173 are balanced. The position of the swash plate 16 after adjustment is determined. As the swash plate adjusting portion 161 moves, the swash plate 16 swings smoothly along the spherical shape of the swash plate receiving portion 19 in the direction of the arrow D2 around the spherical center SC (FIG. 2).
  • the retainer 15 rotates in the directions of arrows D3 and D4 along the retainer bush 11A via the thrust bearing 18. Further, according to the rotation of the retainer 15, the piston head 13 connected to the retainer 15 via the piston rod 14 moves in the axial direction in the cylinder 12S. In particular, in FIG. 3, the uppermost piston head 13 moves to the left, and the lowermost piston head 13 moves to the right. As a result, as the cylinder block 12 rotates, the volume of each cylinder 12S changes. That is, the discharge capacity of the piston pump 1 is variable according to the tilt of the swash plate 16.
  • nine cylinders 12S and piston heads 13 are arranged in the cylinder block 12. In this way, by setting the number of cylinders 12S to an odd number, the pulsation of hydraulic pressure generated when the cylinder block 12 is rotationally driven is reduced. In other words, when the number of cylinders 12S and piston heads 13 is an even number, the hydraulic pulsations between the cylinders 12S arranged symmetrically in the radial direction resonate with each other and increase.
  • the distance between the piston rod 14 and the rotation center of the rotating shaft 11 is shorter than in the case of FIG. 4A.
  • the distance between the piston rod 14 and the rotation center of the rotating shaft 11 is longer than that in the case of FIG. 4A.
  • the piston rod 14 at the phase 0 degree in FIG. 4B is shown enlarged.
  • the axis of the piston rod 14 moves from the first virtual axis C1 corresponding to FIG. 4A to the second virtual axis C2.
  • the head-side end portion 141 of the piston rod 14 swings within the piston head support portion 13S of the piston head 13.
  • the rotation trajectory of the piston rod 14 becomes the ellipse P2 as described above.
  • the swinging motions of the nine piston heads 13 are not cancelled.
  • the swing of the cylinder block 12 around the rotation axis tends to increase.
  • the retainer 15 is supported by the retainer bush 11A fitted in the rotating shaft 11.
  • the retainer spherical surface portion 15A of the retainer 15 and the retainer bush spherical surface portion 11B of the retainer bush 11A have the same spherical shape with the same first curvature, and are in surface contact along the respective spherical surfaces.
  • the rotation shaft 11 can stably hold the rotation of the plurality of piston heads 13, so that the swinging motion of the piston heads 13 is suppressed.
  • the retainer bush 11A may rotate integrally with the rotating shaft 11 when the above-described effects are exhibited, and the retainer bush 11A rotates with a slight speed difference with respect to the rotating shaft 11. Also good. Also in this case, the rotating shaft 11, the cylinder block 12, the piston head 13, the piston rod 14, and the retainer 15 rotate substantially integrally at the same peripheral speed.
  • the retainer spherical surface portion 15A of the retainer 15 and the retainer bush spherical surface portion 11B of the retainer bush 11A have the same spherical shape with the same first curvature so that the retainer 15 becomes the retainer bush 11A during tilt adjustment. Can be rotated along.
  • the swash plate receiving portion 19 has a spherical shape concentric with the spherical shape of the retainer bushing spherical portion 11B when viewed in the cross section of FIG. Can swing quickly. For this reason, the tilting of the swash plate 16 and the movement of the retainer 15, the piston rod 14, and the piston head 13 are smoothly interlocked, and the response of the tilt control can be enhanced.
  • the cylinder block 12 does not need to be tilted with respect to the rotating shaft 11 because the discharge capacity of the piston pump 1 (the amount of reciprocation of the piston) is adjusted. For this reason, while being able to improve the responsiveness at the time of tilt adjustment, complication of the tilt control mechanism of the piston pump 1 is suppressed.
  • the head-side end portion 141 of the piston rod 14 can swing in the radial direction with respect to the piston head 13 (arrow DM in FIG. 5), and the retainer-side end portion. 142 can swing in the radial direction with respect to the retainer 15 (arrow DN in FIG. 5).
  • the head side end 141 and the retainer side end 142 of the piston rod 14 have a degree of freedom of rotation with respect to the piston head 13 and the retainer 15, respectively. For this reason, the rocking and rattling in the radial direction of the piston head 13 that occurs when the cylinder block 12 rotates is absorbed by the rocking of the piston rod 14.
  • a contact portion between the piston head 13 and the piston rod 14 and a contact portion between the piston head 13 and the retainer 15 are formed along the spherical shapes of the head side end portion 141 and the retainer side end portion 142. For this reason, the surface pressure of the piston rod 14 is reduced, and seizure of the piston rod 14 during driving is suppressed.
  • the retainer 15 and the swash plate 16 are connected by a thrust bearing 18. For this reason, the sliding resistance which generate
  • a retainer 15 that rotates together with the cylinder block 12 is supported by a retainer bush 11 ⁇ / b> A provided on the rotating shaft 11.
  • a predetermined gap is formed between the swash plate facing portion 15 ⁇ / b> C of the retainer 15 and the retainer facing portion 164 of the swash plate 16. Therefore, compared with the case where a radial bearing is arrange
  • the swash plate receiving portion 19 is disposed in the housing 10 so that the swash plate receiving portion 19 and the thrust bearing 18 sandwich a part of the swash plate 16 along the axial direction. Has been. For this reason, even when a strong pressing force is applied to the retainer 15 in the left direction by the reciprocating motion of the piston head 13, the thrust bearing 18 and the swash plate 16 can stably support the retainer 15.
  • the piston pump 1 (hydraulic rotating machine) according to one embodiment of the present invention has been described above.
  • the present invention is not limited to these forms.
  • the hydraulic rotating machine according to the present invention the following modified embodiments are possible.
  • FIG. 6 is a cross-sectional view when a hydraulic rotating machine according to a modified embodiment of the present invention is used as a piston motor 1A (hydraulic motor).
  • a hydraulic rotating machine according to a modified embodiment of the present invention is used as a piston motor 1A (hydraulic motor).
  • the swash plate 16 is swung in the direction of arrow D ⁇ b> 5 by the tilt adjustment mechanism 17.
  • a phase opposite to that in the case of FIG. 3 is generated in each piston head 13.
  • high-pressure hydraulic oil flows into the cylinder 12S having a small volume as indicated by an arrow DA.
  • the piston motor 1A functions as a motor.
  • the piston 15 rotates with the retainer 15 and the high-pressure side piston head 13 moves to the low-pressure side (the upper piston head 13 in FIG. 6)
  • the hydraulic oil is discharged in the direction of the arrow DB.
  • the variable displacement control of the piston motor 1A is realized by the retainer 15 swinging along the spherical shape of the retainer bush 11A.
  • the head-side end and the retainer-side end of the piston rod 14 are allowed to swing at least in the radial direction with respect to the piston head 13 and the retainer 15, so that the swinging motion of the piston head 13 during rotational driving is achieved. Is suppressed. Other functions and effects can be expressed as in the previous embodiment. In particular, the contact pressure between the piston rod 14, the piston head 13, and the retainer 15 can be reduced by swinging the piston rod 14. As a result, seizure of the piston rod 14 is suppressed.
  • the head side end portion 141 and the retainer side end portion 142 of the piston rod 14 have been described as having a spherical shape as shown in FIG. 5, but the present invention is limited to this. It is not something.
  • the head side end portion 141 and the retainer side end portion 142 have an arc shape when viewed in a cross section along the axial direction of the rotating shaft 11 as shown in FIG. 1, and have a predetermined shape in a direction perpendicular to the paper surface of FIG. It may have a thickness.
  • the piston head support portion 13S of the piston head 13 and the retainer support portion 15D (FIG.
  • the retainer 15 each have a predetermined arc shape in cross-sectional view, and the head side end portion 141 and the retainer side end portion 142 are provided. Any configuration that can be supported is acceptable. Even in this case, the head side end portion 141 and the retainer side end portion 142 can swing in the radial direction (relatively rotatable) while making line contact along the arcs of the piston head 13 and the retainer 15, respectively. Is done. For this reason, when the cylinder block 12 rotates, the radial swing of the piston head 13 is absorbed.
  • FIG. 7 and 8 are enlarged cross-sectional views for explaining the swing of the piston rod in the hydraulic rotating machine according to the modified embodiment of the present invention.
  • members having the same structure and function as those of the previous embodiment (FIG. 5) are denoted by the same reference numerals as those in FIG. 5.
  • a piston head 13M and a piston rod 14A are provided instead of the piston head 13 and the piston rod 14 of FIG.
  • the piston head 13M includes a cylindrical main body 131 and a spherical portion 132 (first connecting portion) having a convex spherical shape provided at the tip of the main body 131.
  • the piston rod 14A includes a head side end portion 144 (one end side) and a retainer side end portion 145 (the other end side).
  • the head-side end portion 144 has a concave portion having a spherical shape with the same curvature as the spherical body portion 132 inside.
  • the retainer side end portion 145 has a convex spherical shape like the spherical portion 132.
  • the retainer 15 includes a retainer support portion 15D (second connecting portion).
  • the retainer support portion 15 ⁇ / b> D includes a concave portion having a spherical shape with the same curvature as the retainer side end portion 145.
  • oil is supplied from the cylinder 12S to each sliding portion via an oil groove 133 formed in the piston head 13M and an oil groove 146 formed in the piston rod 14A.
  • the spherical body portion 132 of the piston head 13M and the head side end portion 144 of the piston rod 14A are connected so as to be relatively rotatable (arrow DM in FIG. 7).
  • the retainer side end portion 145 of the piston rod 14A and the retainer support portion 15D of the retainer 15 are coupled so as to be relatively rotatable (arrow DN in FIG. 7).
  • the piston head 13M has the same structure as that shown in FIG.
  • the piston rod 14B includes a head side end portion 147 (one end side) and a retainer side end portion 148 (the other end side).
  • the head side end portion 147 and the retainer side end portion 148 have a concave portion having a spherical shape inside.
  • the retainer 15 includes a spherical portion 151 (second connecting portion) having the same curvature as the inner peripheral surface of the retainer side end portion 148.
  • oil is supplied from the cylinder 12S to each sliding portion via the oil groove 133 formed inside the piston head 13M and the oil groove 149 formed inside the piston rod 14B.
  • each spherical shape described above need not be a strict spherical surface.
  • a shape approximate to a spherical surface may be employed in consideration of the slidability between the members and the rotational property around the rotation axis 11 of the piston head 13M.
  • the spherical shape in the present invention includes these substantially spherical shapes.
  • one of the head side end portion 141 and the retainer side end portion 142 may be supported by the piston head 13 or the retainer 15 so as to be swingable.
  • the retainer bush 11A has been described as having a continuous spherical shape along the rotation direction of the rotating shaft 11, but the present invention is not limited to this. As long as the retainer bushing 11A can swingably support the retainer 15, a part of the spherical shape may be discontinuously arranged at intervals along the rotation direction.

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

Abstract

L'invention concerne une machine rotative hydraulique conçue de manière à réduire la résistance au glissement d'un piston alternatif et à supprimer la réduction de rendement volumique correspondant à la quantité de fuite d'huile hydraulique. Une pompe à piston (1) est munie d'un arbre rotatif (11), d'un bloc de cylindres (12), d'une tête de piston (13), d'une tige de piston (14), d'un élément de retenue (15), d'un plateau oscillant (16) et d'un mécanisme de régulation d'inclinaison (17). Lorsque le mécanisme de régulation d'inclinaison (17) fait basculer le plateau oscillant (16), le débit de la pompe à piston (1) est modifié de manière variable. L'élément de retenue (15) qui tourne conjointement avec la tête de piston (13) et la tige de piston (14) est soutenu par un manchon de retenue (11A) prévue sur l'arbre rotatif (11). La section sphérique (15A) de l'élément de retenue (15) et la section sphérique (11B) du manchon de retenue (11A) ont des formes sphériques de même courbure. Pendant la régulation de l'inclinaison, l'élément de retenue (15) bascule alors que la section sphérique (11B) de l'élément de retenue est en contact glissant avec le manchon de retenue (11A).
PCT/JP2017/008898 2016-03-28 2017-03-07 Machine rotative hydraulique WO2017169552A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US16/084,848 US10808686B2 (en) 2016-03-28 2017-03-07 Hydraulic rotary machine
EP17774097.4A EP3438451B1 (fr) 2016-03-28 2017-03-07 Machine rotative hydraulique
CN201780018146.0A CN108884815B (zh) 2016-03-28 2017-03-07 液压旋转机

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2016-063803 2016-03-28
JP2016063803 2016-03-28
JP2016249264A JP6688724B2 (ja) 2016-03-28 2016-12-22 液圧回転機
JP2016-249264 2016-12-22

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WO2017169552A1 true WO2017169552A1 (fr) 2017-10-05
WO2017169552A9 WO2017169552A9 (fr) 2017-12-21

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020008006A (ja) * 2018-07-12 2020-01-16 株式会社神戸製鋼所 液圧回転機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4980602A (fr) * 1972-08-16 1974-08-03
JPS57105574A (en) * 1980-12-19 1982-07-01 Japan Steel Works Ltd:The Axial piston pump
JP2003113776A (ja) * 2001-08-03 2003-04-18 Korea Inst Of Machinery & Materials 可変容量型斜板式アキシャルピストンユニット
JP2009250204A (ja) * 2008-04-10 2009-10-29 Yanmar Co Ltd アキシャルピストン装置及び油圧回路並びに作業機械

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4980602A (fr) * 1972-08-16 1974-08-03
JPS57105574A (en) * 1980-12-19 1982-07-01 Japan Steel Works Ltd:The Axial piston pump
JP2003113776A (ja) * 2001-08-03 2003-04-18 Korea Inst Of Machinery & Materials 可変容量型斜板式アキシャルピストンユニット
JP2009250204A (ja) * 2008-04-10 2009-10-29 Yanmar Co Ltd アキシャルピストン装置及び油圧回路並びに作業機械

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020008006A (ja) * 2018-07-12 2020-01-16 株式会社神戸製鋼所 液圧回転機
JP7044652B2 (ja) 2018-07-12 2022-03-30 株式会社神戸製鋼所 液圧回転機

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