WO2014156539A1 - Machine rotative à pression de liquide de type à plateau oscillant opposé - Google Patents

Machine rotative à pression de liquide de type à plateau oscillant opposé Download PDF

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Publication number
WO2014156539A1
WO2014156539A1 PCT/JP2014/055782 JP2014055782W WO2014156539A1 WO 2014156539 A1 WO2014156539 A1 WO 2014156539A1 JP 2014055782 W JP2014055782 W JP 2014055782W WO 2014156539 A1 WO2014156539 A1 WO 2014156539A1
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WO
WIPO (PCT)
Prior art keywords
swash plate
piston
tilt
pressure chamber
tilting
Prior art date
Application number
PCT/JP2014/055782
Other languages
English (en)
Japanese (ja)
Inventor
弘毅 加藤
細川　尊
Original Assignee
カヤバ工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by カヤバ工業株式会社 filed Critical カヤバ工業株式会社
Priority to KR1020157006825A priority Critical patent/KR101743848B1/ko
Priority to DE112014000201.1T priority patent/DE112014000201T5/de
Priority to CN201480002590.XA priority patent/CN104685208A/zh
Priority to US14/431,350 priority patent/US20150240636A1/en
Publication of WO2014156539A1 publication Critical patent/WO2014156539A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0035—Reciprocating-piston machines or engines with 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
    • F01B3/0038—Reciprocating-piston machines or engines with 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 inclined to main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0052—Cylinder barrel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/007—Swash plate
    • F01B3/0073—Swash plate swash plate bearing means or driving or driven axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0639—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control
    • F03C1/0686—Control by changing the inclination of the swash plate
    • 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
    • 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
    • F04B1/26—Control
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Definitions

  • the present invention relates to an opposing type swash plate type hydraulic rotating machine in which a first swash plate and a second swash plate are inclined to face both ends of a cylinder block.
  • JP2008-231924A a cylinder block having a plurality of cylinders, a first piston and a second piston protruding from both ends of the cylinder, and a first swash plate and a second swash plate in which the protruding ends of the first and second pistons are in sliding contact with each other.
  • An opposed type swash plate type hydraulic rotating machine comprising: a swash plate.
  • the first piston follows the first swash plate to reciprocate in the cylinder as the cylinder block rotates, and the second piston follows the second swash plate to reciprocate in the cylinder. Then, the working fluid is supplied to and discharged from the volume chamber in the cylinder.
  • a tilt drive piston for tilting the first swash plate is connected to one side of the first swash plate, and the other side of the first swash plate transmits the tilt of the first swash plate to the second swash plate
  • the tilting interlocking mechanism is connected.
  • the tilting shaft portion of the first swash plate causes the floating phenomenon to separate from the tilting bearing provided on the casing when the first swash plate is driven to tilt.
  • the floating phenomenon includes the force of the tilting drive piston received on one side of the first swash plate when the first swash plate tilts, the reaction force of the tilting interlocking mechanism received on the other side of the first swash plate, Is a phenomenon in which the first swash plate rotates about the rotation axis of the cylinder block by acting as a torque in the same rotational direction, and the tilting shaft portion of the first swash plate separates from the tilt bearing.
  • An object of the present invention is to prevent the floating phenomenon in an opposed type swash plate type hydraulic rotating machine.
  • the opposite type swash plate in which the first piston and the second piston protruding from both ends of the rotating cylinder block reciprocate in the cylinder following the first swash plate and the second swash plate, respectively.
  • Type hydraulic rotary machine a first tilt bearing for tiltably supporting a first swash plate, and a first tilt drive for causing the first swash plate to tilt in a direction intersecting the rotation axis of the cylinder block
  • a facing comprising a piston, a second tilt bearing which tiltably supports a second swash plate, and a second tilt drive piston which tilts the second swash plate in a direction intersecting with the rotation axis of the cylinder block.
  • a swash plate type hydraulic rotating machine is provided.
  • FIG. 1 is a cross-sectional view of an opposed type swash plate type piston motor according to an embodiment of the present invention.
  • FIG. 2 is a schematic diagram which shows the structure which tilts a 1st swash plate and a 2nd swash plate.
  • FIG. 3 is a schematic diagram which shows the structure which tilts a 1st swash plate and a 2nd swash plate.
  • FIG. 4 is a hydraulic circuit diagram for tilting the first swash plate and the second swash plate.
  • the opposing type swash plate type piston motor 1 shown in FIG. 1 is applied to a hydrostatic transmission 90 (see FIG. 4; hereinafter simply referred to as “HST 90”) mounted as a continuously variable transmission on a work vehicle or the like.
  • HST 90 hydrostatic transmission 90
  • the opposed type swash plate type piston motor 1 is inclined to face both ends of the shaft 2 rotating around the rotation axis O 4, the cylinder block 4 supported by the shaft 2, and the cylinder block 4.
  • the first swash plate 30 and the second swash plate 40 are provided.
  • the cylinder block 4 is formed in a cylindrical shape having a hollow portion, and the shaft 2 is inserted therein.
  • a plurality of cylinders 3 are formed in the cylinder block 4 side by side in the circumferential direction.
  • the cylinder 3 is formed to extend in the axial direction, and opens at both end faces 4C and 4D of the cylinder block 4.
  • the first piston 8 and the second piston 9 are respectively inserted into the cylinder 3 from both open ends.
  • the first piston 8 and the second piston 9 have tip portions projecting from the open end of the cylinder 3, and the first shoe 21 and the second shoe 22 are pivotally connected to the respective tip portions.
  • the first piston 8 reciprocates following the end face 30A of the first swash plate 30 via the first shoe 21 and the port plate 16, and the second piston 9 reciprocates the second shoe 22. It reciprocates following the end face 40A of the second swash plate 40 via the same.
  • a volume chamber 7 is defined between the first piston 8 and the second piston 9.
  • the volume chamber 7 is expanded and contracted, and hydraulic oil is supplied and discharged to the volume chamber 7 through the pair of supply and discharge passages 5, 6 (see FIG. 4). Ru.
  • the piston motor 1 uses hydraulic fluid (oil) as the hydraulic fluid, but may use a hydraulic fluid such as a water-soluble substitute fluid instead of the hydraulic fluid.
  • the cylindrical shaft 2 is rotatably supported at both ends by a casing (not shown) via a bearing (not shown).
  • the casing is provided with a cylindrical case (not shown) and lid-like first and second covers (not shown) that close both open ends of the case.
  • the cylinder block 4 is accommodated in the case, the first swash plate 30 is accommodated in the first cover, and the second swash plate 40 is accommodated in the second cover.
  • Splines 2A are formed on the outer periphery of the shaft 2.
  • Splines 4 H are formed on the inner periphery of the cylinder block 4.
  • the spline 4H of the cylinder block 4 is slidably fitted to the spline 2A of the shaft 2, whereby the rotation of the cylinder block 4 with respect to the shaft 2 is restricted, and axial movement with respect to the shaft 2 becomes possible.
  • a first retainer plate 23 and a first retainer holder 25 are interposed between the first swash plate 30 and the cylinder block 4 in the axial direction.
  • a disc-shaped port plate 16 that rotates with the cylinder block 4 is provided between the first shoe 21 and the first swash plate 30, a disc-shaped port plate 16 that rotates with the cylinder block 4 is provided.
  • the port plate 16 is connected to the first retainer plate 23 via a plurality of pins 18.
  • a plurality of center springs 19 are interposed between the first retainer holder 25 and the cylinder block 4 in the circumferential direction.
  • the cylinder block 4 is urged rightward in FIG. 1 by the center spring 19 and pressed against the end face 40A of the second swash plate 40 via the second retainer holder 26, the second retainer plate 24 and the second shoe 22. .
  • the axial position of the cylinder block 4 with respect to the second swash plate 40 is determined.
  • the first swash plate 30 has a pair of tilting and rotating shaft portions (half log portions) 30B that project to the back side.
  • the tilting shaft portion 30B is tiltably supported by a first tilting bearing 33 formed in a casing (not shown).
  • the first swash plate 30 pivots about the first tilting axis O1.
  • the second swash plate 40 has a pair of tilting and rotating shaft portions (half log portions) 40B projecting to the back side.
  • the tilt shaft portion 40B is tiltably supported by a second tilt bearing 43 formed in the casing.
  • the second swash plate 40 pivots about the second tilting axis O2.
  • the first tilt axis O1 and the second tilt axis O2 are orthogonal to the rotation axis O4 of the cylinder block 4.
  • the piston motor 1 includes a first tilting drive mechanism 50 for tilting the first swash plate 30 and a second tilting drive mechanism 60 for tilting the second swash plate 40.
  • first tilting drive mechanism 50 for tilting the first swash plate 30
  • second tilting drive mechanism 60 for tilting the second swash plate 40.
  • the stroke length at which the first piston 8 reciprocates in the cylinder 3 changes.
  • the stroke length at which the second piston 9 reciprocates in the cylinder 3 changes.
  • the stroke length changes, the displacement per revolution of the cylinder block 4 changes, and the output rotational speed of the piston motor 1 changes.
  • the first tilt drive piston 31 moved by hydraulic pressure and the movement of the first tilt drive piston 31 are centered on the first tilt axis O1.
  • a conversion mechanism 38 for converting into a rotational movement is included in the first tilt drive mechanism 50.
  • the line G1 is orthogonal to the rotation axis O4 and to the first tilt axis O1.
  • the first tilting drive piston 31 is arranged to move in a direction parallel to the line G1. Not limited to this, the first tilt drive piston 31 may be arranged to move in a direction intersecting with the line G1 at a slight angle.
  • the conversion mechanism 38 includes a slide metal 36 slidably engaged with the guide groove 35 of the first tilt drive piston 31, and a slide metal projecting from an end of the first swash plate 30 in the direction of the first tilt axis O1. And a pin 37 slidably inserted into the hole 36.
  • a first push side piston pressure chamber 53 and a first pull side piston pressure chamber 54 are respectively defined at both ends of the first tilt drive piston 31.
  • a first tilt control valve 70 is provided to switch the hydraulic pressure introduced to the piston pressure chambers 53, 54. The first tilt drive piston 31 moves due to the hydraulic pressure difference between the piston pressure chambers 53 and 54.
  • the second tilt drive piston 41 moved by hydraulic pressure and the movement in which the second tilt drive piston 41 moves are centered on the second tilt axis O2.
  • a conversion mechanism 48 for converting into a rotational movement.
  • the line G2 is orthogonal to the rotation axis O4 and orthogonal to the second tilting axis O2.
  • the second tilting drive piston 41 is arranged to move in a direction parallel to the line G2. Not limited to this, the second tilt drive piston 41 may be arranged to move in a direction intersecting with the line G2 at a slight angle.
  • the conversion mechanism 48 includes a slide metal 46 slidably engaged with the guide groove 45 of the second tilt drive piston 41, and a slide metal projecting from an end of the second swash plate 40 in the direction of the second tilt axis O2. And a pin 47 slidably inserted into the hole 46.
  • a second push side piston pressure chamber 63 and a second pull side piston pressure chamber 64 are respectively defined at both ends of the second tilting drive piston 41.
  • a second tilt control valve 80 is provided to switch the hydraulic pressure introduced to the piston pressure chambers 63, 64.
  • the second tilt drive piston 41 is moved by the hydraulic pressure difference between the piston pressure chambers 63 and 64.
  • FIG. 4 is a diagram showing the configuration of the hydraulic circuit and control system provided in the HST 90. As shown in FIG.
  • the HST 90 includes a piston motor 1, a piston pump 99, and a closed circuit 100 through which hydraulic fluid circulates.
  • the closed circuit 100 includes a first circulation passage 101 and a second circulation passage 102 that connect the piston motor 1 and the piston pump 99.
  • One end of the first circulation passage 101 is connected to the supply and discharge passage 5 of the piston motor 1, and the other end is connected to the supply and discharge passage 105 of the piston pump 99.
  • One end of the second circulation passage 102 is connected to the supply and discharge passage 6 of the piston motor 1, and the other end is connected to the supply and discharge passage 106 of the piston pump 99.
  • the hydraulic fluid discharged from the piston pump 99 is fed to the piston motor 1 through the closed circuit 100, whereby the piston motor 1 rotates.
  • the output rotation of the piston motor 1 is transmitted to the left and right wheels via a transmission (gear type transmission), a differential gear, etc. (not shown).
  • the piston pump 99 is rotationally driven by an engine (not shown).
  • the piston pump 99 has two supply and discharge passages 105 and 106 for supplying and discharging the hydraulic oil to the volume chamber, and the discharge direction of the hydraulic oil to the supply and discharge passages 105 and 106 by switching the tilt direction of the swash plate 107. Will change.
  • the traveling direction (forward or reverse) of the vehicle is switched.
  • the fluid pressure source 110 is provided with a fixed displacement charge pump 111 which is rotationally driven by the engine, and a charge passage 113 which leads hydraulic oil discharged from the charge pump 111.
  • An oil filter 114, an oil filter 116, and a relief valve 119 are interposed in the charge passage 113.
  • the hydraulic oil that has passed through the relief valve 119 returns to the tank 109.
  • Charge passage 113 is connected to first circulation passage 101 and second circulation passage 102 via check valves 117 and 118.
  • the check valve 117 opens to fill the first circulation passage 101 with the hydraulic oil from the charge passage 113.
  • the check valve 118 opens to fill the second circulation passage 102 with the hydraulic oil from the charge passage 113. For this reason, the pressures of the first circulation passage 101 and the second circulation passage 102 are maintained at or above a predetermined value.
  • Relief valves 121 and 122 are interposed in the charge passage 113 in parallel with the check valves 117 and 118.
  • the relief valve 121 opens and the hydraulic pressure in the first circulation passage 101 is released to the charge passage 113.
  • the relief valve 122 opens and the hydraulic pressure in the second circulation passage 102 is released to the charge passage 113. For this reason, it is suppressed that the pressure of the 1st circulation passage 101 and the 2nd circulation passage 102 exceeds predetermined value.
  • a high pressure selection valve 149 is provided between the first circulation passage 101 and the second circulation passage 102.
  • the hydraulic pressure extracted through the high pressure selection valve 149 is led to the first tilt control valve 70 and the second tilt control valve 80.
  • the first tilt control valve 70 includes an inlet port 71 communicating with the high pressure selection valve 149, an outlet port 72 communicating with the tank 109, and a first push side port 73 communicating with the first push side piston pressure chamber 53; And a first pull side port 74 in communication with the first pull side piston pressure chamber 54.
  • the first tilt control valve 70 includes a valve housing 76 inserted in the casing, a spool valve 79 slidably accommodated in the valve housing 76, and a spool valve 79. In one axial direction, and a solenoid 77 which moves the spool valve 79 in the axial direction against the spring 78.
  • the first tilt control valve 70 is switched to three positions 70A, 70B, 70C.
  • the hydraulic oil from the high pressure selection valve 149 is supplied to the first push side piston pressure chamber 53 through the ports 71, 73, and the hydraulic oil of the first pull side piston pressure chamber 54 is the hydraulic pressure port 74, 72. Is returned to the tank 109.
  • the first tilting drive piston 31 moves in the direction (downward direction) indicated by arrow A in FIG. 2 and the first swash plate 30 is indicated by arrow B As such, it pivots in the direction in which the tilt angle increases. As a result, the displacement volume of the piston motor 1 increases, and the traveling speed of the vehicle decreases.
  • the hydraulic oil from the high pressure selection valve 149 is supplied to the first pull side piston pressure chamber 54 through the ports 71 and 74, and the hydraulic oil of the first push side piston pressure chamber 53 is tanked through the ports 73 and 72. It is returned to 109.
  • the first tilting drive piston 31 moves in the direction (upward direction) indicated by the arrow C in FIG. 3 and the first swash plate 30 is indicated by the arrow D As such, it pivots in the direction in which the tilt angle decreases. As a result, the displacement of the piston motor 1 is reduced, and the traveling speed of the vehicle is increased.
  • the controller 170 adjusts the flow rate of the hydraulic oil supplied to and discharged from the first tilt drive mechanism 50 by switching the positions 70A, 70B, 70C of the first tilt control valve 70, and continuously changes the transmission ratio of the HST 90. Control.
  • the second tilt control valve 80 has an inlet port 81 communicating with the high pressure selection valve 149, an outlet port 82 communicating with the tank 109, and a second push side port 83 communicating with the second push side piston pressure chamber 63; And a second pull-side port 84 communicating with the second pull-side piston pressure chamber 64.
  • the second tilt control valve 80 includes a valve housing 86 installed in the casing, a spool valve 89 slidably accommodated in the valve housing 86, and a spool valve 89. And the solenoid 87 which moves the spool valve 89 in the axial direction against the spring 88.
  • the second tilt control valve 80 switches to three positions 80A, 80B, 80C.
  • the hydraulic oil from the high pressure selection valve 149 is supplied to the second pull side piston pressure chamber 64 through the ports 81 and 84, and the hydraulic oil of the second push side piston pressure chamber 63 is the hydraulic pressure ports 83 and 82. Is returned to the tank 109.
  • the second tilting drive piston 41 moves in the direction (upward direction) indicated by arrow E in FIG. 2, and the second swash plate 40 is indicated by arrow F. As such, it pivots in the direction in which the tilt angle decreases. As a result, the displacement of the piston motor 1 is reduced, and the traveling speed of the vehicle is increased.
  • the hydraulic oil from the high pressure selection valve 149 is supplied to the second push side piston pressure chamber 63 through the ports 81 and 83, and the hydraulic oil of the second pulling side piston pressure chamber 64 is tanked through the ports 84 and 82. It is returned to 109.
  • the second tilting drive piston 41 moves in the direction shown by the arrow H in FIG. 3 (downward), and the second swash plate 40 is shown by the arrow I As such, it pivots in the direction in which the tilt angle increases. As a result, the displacement volume of the piston motor 1 increases and the speed of the vehicle decreases.
  • the controller 170 adjusts the flow rate of the hydraulic oil supplied to and discharged from the second tilt drive mechanism 60 by switching the positions 80A, 80B, 80C of the second tilt control valve 80 to continuously change the transmission ratio of the HST 90. Control.
  • Numerals 171 and 172 are potentiometers for reading the tilt angles of the first swash plate 30 and the second swash plate 40, respectively.
  • the controller 170 performs feedback control of the open / close timing of the first tilt control valve 70 and the second tilt control valve 80 in accordance with the detection values of the potentiometers 171 and 172.
  • the first tilt drive piston 31 pushes the end of the first swash plate 30 in the direction orthogonal to the tilt axis O1 to tilt the first swash plate 30, and the second tilt drive piston
  • the tilting of the second swash plate 40 by pressing the end of the second swash plate 40 in the direction orthogonal to the tilting axis O2 is performed independently of each other.
  • the flow rate of the working fluid supplied to and discharged from the first tilt drive mechanism 50 is adjusted by the first tilt control valve 70, and the flow rate of the working fluid supplied to and discharged from the second tilt drive mechanism 60 is It is adjusted by a second tilt control valve 80 different from the single tilt control valve 70.
  • the first swash plate 30 and the second swash plate 40 are tilted by being pushed by the first tilt drive piston 31 and the second tilt drive piston 41 in the direction intersecting the tilt axes O1 and O2, respectively. Therefore, since the torque for rotating around the central axis O4 does not act on the first swash plate 30 and the second swash plate 40, the tilt shaft portion 30B and the tilt shaft portion 40B are the first tilt bearing 33 and the first tilt bearing 33 and The floating phenomenon away from the second tilting bearing 43 can be prevented.
  • the actuation strokes of the first tilt drive mechanism 50 and the second tilt drive mechanism 60 are continuously adjusted by the operation of the first tilt control valve 70 and the second tilt control valve 80, respectively.
  • the tilt angles of the first swash plate 30 and the second swash plate 40 can be controlled to any level.
  • the flow rate of the working fluid supplied to and discharged from the first tilt drive mechanism 50 and the flow rate of the working fluid supplied to and discharged from the second tilt drive mechanism 60 correspond to the first tilt control valve 70 and the second tilt control valve.
  • the first tilt drive mechanism 50 can adjust the tilt angle of the first swash plate 30 in a responsive manner because the control valve 80 respectively adjusts the tilt angle of the first swash plate 30.
  • the tilt angle can be adjusted responsively.
  • the present embodiment is the piston motor 1 in which the cylinder block is rotated by supplying and discharging the hydraulic oil
  • the piston pump 111 to which the hydraulic oil is supplied and discharged by rotating the cylinder block is used.
  • the invention may be applied.
  • the piston motor constitutes the hydrostatic transmission (HST), but it may constitute another machine or facility.
  • HST hydrostatic transmission

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Abstract

Moteur à piston de type à plateau oscillant opposé dans lequel des premier et second pistons, qui font saillie depuis les deux extrémités d'un bloc-cylindres, avancent et reculent suivant, respectivement, des premier et second plateaux oscillants, le moteur à piston étant équipé : d'un premier palier d'inclinaison destiné à supporter en inclinaison le premier plateau oscillant ; d'un premier piston d'entraînement d'inclinaison destiné à incliner le premier plateau oscillant dans une direction qui coupe l'axe de rotation du bloc-cylindres ; d'un second palier d'inclinaison destiné à supporter en inclinaison le second plateau oscillant ; et d'un second piston d'entraînement d'inclinaison destiné à incliner le second plateau oscillant dans une direction qui coupe l'axe de rotation du bloc-cylindres.
PCT/JP2014/055782 2013-03-29 2014-03-06 Machine rotative à pression de liquide de type à plateau oscillant opposé WO2014156539A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
KR1020157006825A KR101743848B1 (ko) 2013-03-29 2014-03-06 대향식 경사판형 액압 회전기
DE112014000201.1T DE112014000201T5 (de) 2013-03-29 2014-03-06 Hydraulische Rotationsmaschine vom Typ gegenüberliegender Taumelscheiben
CN201480002590.XA CN104685208A (zh) 2013-03-29 2014-03-06 对置式斜板型液压回转机械
US14/431,350 US20150240636A1 (en) 2013-03-29 2014-03-06 Opposed swash plate type fluid pressure rotating machine

Applications Claiming Priority (2)

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ITUB20155999A1 (it) * 2015-11-30 2017-05-30 Merlo Group Innovation Lab S R L Macchina idraulica a cilindri flottanti
CN108869223A (zh) * 2018-08-06 2018-11-23 华中科技大学 一种双斜盘柱塞泵
US10968741B2 (en) * 2019-02-08 2021-04-06 Volvo Car Corporation Variable pre and de-compression control mechanism and method for hydraulic displacement pump
WO2021207638A1 (fr) * 2020-04-10 2021-10-14 Moog Inc. Système de pompe à piston électrohydraulique à couple d'assistance

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JP2008231924A (ja) * 2007-03-16 2008-10-02 Kayaba Ind Co Ltd 対向式斜板型ピストンポンプ・モータ

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KR101743848B1 (ko) 2017-06-05
DE112014000201T5 (de) 2015-06-25
JP6114089B2 (ja) 2017-04-12
CN104685208A (zh) 2015-06-03
US20150240636A1 (en) 2015-08-27
KR20150044940A (ko) 2015-04-27

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