WO2012077157A1 - 斜板型液圧回転機 - Google Patents

斜板型液圧回転機 Download PDF

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Publication number
WO2012077157A1
WO2012077157A1 PCT/JP2010/007103 JP2010007103W WO2012077157A1 WO 2012077157 A1 WO2012077157 A1 WO 2012077157A1 JP 2010007103 W JP2010007103 W JP 2010007103W WO 2012077157 A1 WO2012077157 A1 WO 2012077157A1
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WO
WIPO (PCT)
Prior art keywords
swash plate
cylinder block
bush
plate
type hydraulic
Prior art date
Application number
PCT/JP2010/007103
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大野　猛
鈴木　孝尚
寿夫 和田
Original Assignee
川崎重工業株式会社
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 川崎重工業株式会社 filed Critical 川崎重工業株式会社
Priority to JP2012547597A priority Critical patent/JPWO2012077157A1/ja
Priority to EP10860466.1A priority patent/EP2650538A1/en
Priority to PCT/JP2010/007103 priority patent/WO2012077157A1/ja
Priority to CN2010800690030A priority patent/CN103069161A/zh
Priority to US13/882,832 priority patent/US20130327208A1/en
Priority to KR1020127031763A priority patent/KR20130030761A/ko
Publication of WO2012077157A1 publication Critical patent/WO2012077157A1/ja

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    • 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
    • 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
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/108—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by turning the swash plate (with fixed inclination)
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means
    • 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
    • F04B1/128—Driving means
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2035—Cylinder barrels
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F04B27/0882—Pistons piston shoe retaining means
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F04B27/0886—Piston shoes

Definitions

  • the present invention relates to a swash plate type hydraulic rotating machine suitable as, for example, a swash plate type hydraulic pump or a swash plate type hydraulic motor.
  • FIG. 8 shows a conventional swash plate type hydraulic pump.
  • a conventional swash plate type hydraulic pump 100 includes a cylindrical cylinder block 9 that is spline-fitted to the rotary shaft 3, a plurality of cylinders 11 formed in the cylinder block 9, and a cylinder 11. And a valve plate 4 with which one end of the cylinder block 9 is in contact, and a presser plate 17 and a swash plate 15 provided opposite to the other end of the cylinder block 9. ing.
  • the tip of the piston 13 is a spherical portion 13 a that protrudes from the cylinder 11, and the spherical portion 13 a is spherically supported by a shoe 14 that is in sliding contact with the sliding contact surface 15 c of the swash plate 15.
  • the shoe 14 is fitted in a shoe support hole 17 a provided in the presser plate 17 corresponding to the cylinder 11.
  • the spherical bush 80 that supports the presser plate 17 is a cylindrical member that is spline-fitted to the rotary shaft 3, and is positioned between the cylinder block 9 and the swash plate 15.
  • the outer peripheral surface of the spherical bush 80 gradually increases in diameter from the swash plate 15 side toward the valve plate 4 side, and the outer peripheral surface and the inner peripheral surface of the presser plate 17 are in contact with each other.
  • a set spring 20 is provided between the spherical bush 80 and the cylinder block 9. Due to the spring force of the set spring 20 and the hydraulic pressure in each cylinder 11, the cylinder block 9 is pressed against and closely contacts the valve plate 4, and the shoe 14 is pressed against the sliding contact surface 15 c of the swash plate 15.
  • the piston 13 reciprocates in the cylinder 11 along the inclination of the swash plate 15.
  • the swash plate type hydraulic pump uses the movement of the piston 13 to suck a required amount of working fluid at a low pressure and discharge it to the high pressure side.
  • the rotation of the rotary shaft and the movement of the working fluid are opposite to those of the swash plate type hydraulic pump.
  • the force with which the shoe 14 presses the swash plate 15 depends on the spring force of the set spring 20, and the piston 13 causes the shoe 14 to move the valve plate 4.
  • the force pulling toward the side exceeds the force pressing the shoe 14 by the set spring 20 and the hydraulic pressure.
  • the shoe 14 may float from the swash plate 15 or may fall (tilt).
  • the shoe 14 comes into contact with the sliding contact surface 15 c of the swash plate 15.
  • the swash plate 15 and the shoe 14 may be unevenly worn or galling and seizure may occur due to the contact of the shoe 14, and the life of the shoe 14 and the swash plate 15 may be reduced.
  • the bearing surface that comes into contact with the swash plate of the shoe is made of an aluminum-silicon alloy that is lighter and more excellent in wear resistance than a copper alloy, thereby acting on the shoe. By reducing the centrifugal force, lifting of the shoe from the swash plate is prevented.
  • an object of the present invention is to provide a technique for preventing the shoe from lifting from the swash plate in a swash plate type hydraulic rotating machine such as a swash plate type hydraulic pump or a swash plate type hydraulic motor. As a result, it aims at providing the structure which can be equal to the further increase in the rotational speed of a swash plate type hydraulic rotating machine.
  • the swash plate type hydraulic rotating machine according to the present invention is in sliding contact with the valve plate between the rotary plate, the valve plate and the swash plate facing away from each other in the axial direction of the rotary shaft, and between the valve plate and the swash plate.
  • a cylinder block externally fitted to the rotating shaft, a plurality of cylinders provided in the cylinder block, a plurality of pistons inserted into the cylinder so as to reciprocate in the axial direction, and the swash plate from the cylinder
  • a plurality of shoes pivotably connected to the tip of the piston protruding to the side, and an annular presser plate that is loosely fitted to the rotary shaft between the swash plate and the cylinder block and holds the shoe
  • a bush that supports the presser plate, a bush that is provided between the bush and the cylinder block, and the bush that is provided between the presser plate and the cylinder block.
  • the pressing plate and a spring member for urging the bush so as to press the swash plate side, gap between the axial direction of the bush and the cylinder block is one that is 0 or very small in the assembled state.
  • the size of the gap is preferably 0 or more than 0 and 1.2 mm or less.
  • the swash plate type hydraulic rotating machine includes a rotating shaft, a valve plate and a swash plate facing away from each other in the axial direction of the rotating shaft, and the valve plate and the sliding plate between the valve plate and the swash plate.
  • a cylinder block that is externally fitted to the rotating shaft so as to be in contact; a plurality of cylinders provided in the cylinder block; a plurality of pistons that are inserted into the cylinder so as to be capable of reciprocating in the axial direction; A plurality of shoes that are swingably connected to the tip of the piston that protrudes toward the swash plate, and an annular ring that is loosely fitted to the rotary shaft between the swash plate and the cylinder block and holds the shoe A presser plate, provided between the presser plate and the cylinder block, a bush for supporting the presser plate, and provided between the bush and the cylinder block.
  • a spring member which shoe urges the bush so as to press the pressing plate to the swash-plate-side, but with a filling member to fill the axial clearances of the bush and the cylinder block.
  • the filling member may be one or more shim plates. Further, a time-curable or thermosetting filler may be provided between the filling member and any one of the bush and the cylinder block. Alternatively, the filling member may be a press-fitting bush.
  • the swash plate type hydraulic rotating machine configured as described above, since the gap between the cylinder block and the bush is zero or very small, movement of the bush toward the valve plate is restricted when the bush comes into contact with the cylinder block. . That is, the movement of the press plate that presses the shoe against the swash plate toward the valve plate is restricted. Therefore, for example, when the rotational speed of the rotary shaft increases and the moment of overturning the shoe caused by the inertial force or centrifugal force that pulls the piston toward the valve plate becomes greater than the spring force of the set spring, the shoe is inclined. Do not lift or fall over the board.
  • the shoe is prevented from being lifted or overturned from the swash plate, so that the shoe slides on the swash plate in a state where it comes into contact with the swash plate.
  • the bushing is pressed against the cylinder block. Since the movement of the plate toward the valve plate is restricted, it is possible to prevent the shoe from being lifted from the swash plate or falling down.
  • FIG. 1 is a longitudinal sectional view showing a schematic configuration of a swash plate type hydraulic pump according to an embodiment of the present invention.
  • FIG. 2 is an enlarged view of a portion X surrounded by a two-dot chain line in FIG.
  • FIG. 3 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing Example 1 of a spherical bush and a cylinder block provided with a gap in the axial direction.
  • FIG. 4 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing Example 2 of a spherical bush and a cylinder block provided with a gap in the axial direction.
  • FIG. 1 is a longitudinal sectional view showing a schematic configuration of a swash plate type hydraulic pump according to an embodiment of the present invention.
  • FIG. 2 is an enlarged view of a portion X surrounded by a two-dot chain line in FIG.
  • FIG. 3 is
  • FIG. 5 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing an example 2 of a spherical bush and a cylinder block in which an interval in the axial direction is filled.
  • FIG. 6 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing an example 3 of a spherical bush and a cylinder block in which an interval in the axial direction is filled.
  • FIG. 7 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing a fourth example of a spherical bush and a cylinder block in which an interval in the axial direction is filled.
  • FIG. 8 is a longitudinal sectional view showing a schematic configuration of a conventional swash plate type hydraulic pump.
  • FIG. 9 is a view showing a state of a shoe lifted from a swash plate in a conventional swash plate type hydraulic pump.
  • the swash plate type hydraulic pump 10 has a rotating shaft 3 supported by a casing (not shown).
  • the rotary shaft 3 is connected to a drive source (not shown) such as an engine.
  • a thick cylindrical cylinder block 9 is fitted on the rotary shaft 3. Specifically, a spline provided on the outer periphery of the rotating shaft 3 and a spline 9 b provided on the inner periphery of the cylinder block 9 are engaged. Thereby, the cylinder block 9 rotates around the rotating shaft 3 as the rotating shaft 3 rotates.
  • a disc-shaped valve plate 4 fixed to the casing is provided on one side of the cylinder block 9 (in the right side of the drawing in FIG. 1).
  • the valve plate 4 is in sliding contact with a valve plate sliding contact surface 97 which is one end surface of the cylinder block 9.
  • a pair of intake / exhaust ports 5 and 6 are formed in the valve plate 4, and these communicate with an intake / exhaust passage (not shown) formed in the casing.
  • an annular swash plate 15 through which the rotary shaft 3 passes is provided so as to face the valve plate 4.
  • the swash plate 15 and the cylinder block 9 are separated from each other, and the surface of the swash plate 15 facing the cylinder block 9 is a slidable contact surface 9c on which a shoe 14 described later slides.
  • the swash plate 15 is tilted from a direction perpendicular to the axial direction of the rotating shaft 3 (hereinafter simply referred to as the axial direction L), and is configured such that its maximum tilt angle can be changed by a tilting actuator (not shown).
  • the swash plate 15 side along the axial direction L is referred to as “first side”
  • the valve plate 4 side along the axial direction L is referred to as “second side”.
  • the first side is the opposite side of the second side.
  • the cylinder block 9 is integrally provided with a guide portion 91 inserted into a spherical bush 80 described later and a main body portion 92 provided with a cylinder 11 into which the piston 13 is inserted.
  • the main body 92 has a larger diameter than the guide 91, and the guide 91 protrudes from the main body 92 to the first side. For this reason, the cylinder block 9 has a two-stage end face facing the first side.
  • the first step end surface is a first end surface 95 located on the first side of the guide portion 91
  • the second step end surface is a second end surface 96 located on the first side of the main body portion 92.
  • the cylinder block 9 has the above-described valve plate sliding contact surface 97 as an end surface facing the second side.
  • a plurality of cylinders 11 (only two are shown in FIG. 1) are formed concentrically around the rotation shaft 3.
  • the cylinder 11 is a cylindrical space extending in the axial direction L, and opens toward the first side.
  • the cylinder block 9 is provided with a cylinder port 11a for communicating the inside of each cylinder 11 with the intake / exhaust ports 5 and 6.
  • a piston 13 is inserted into each cylinder 11 so as to reciprocate in the axial direction L within the cylinder 11.
  • a spherical portion 13 a that protrudes from the cylinder block 9 to the first side is formed at the end portion on the first side of the piston 13.
  • the spherical portion 13 a of the piston 13 is fitted into a spherical support portion 14 a formed on the second side of the shoe 14.
  • the shoe 14 is swingably connected to the tip of the piston 13.
  • the first side of the shoe 14 is in sliding contact with the sliding contact surface 15 c of the swash plate 15.
  • Each shoe 14 rotates around the rotary shaft 3 while being in sliding contact with the sliding contact surface 15 c of the swash plate 15 by the rotation of the rotary shaft 3.
  • An annular pressing plate 17 is provided between the cylinder block 9 and the swash plate 15.
  • a plurality of shoe support holes 17 a provided corresponding to the cylinders 11 are formed in the presser plate 17.
  • the shoe 14 is fitted in the shoe support hole 17a.
  • the outer periphery of the shoe 14 has a small-diameter portion 14c that can be fitted into the shoe support hole 17a, and a large-diameter portion 14d that is larger in diameter than the shoe support hole 17a on the first side of the small-diameter portion 14c.
  • the step 14 between the small-diameter portion 14c and the large-diameter portion 14d of the shoe 14 comes into contact with the peripheral portion of the shoe support hole 17a toward the second side, so that the movement of the shoe 14 to the second side is restricted.
  • the pressing plate 17 is supported on the rotary shaft 3 through a spherical bush 80 so as to be swingable.
  • the outer peripheral surface 81 of the spherical bush 80 gradually increases in diameter toward the second side and is formed with a smooth curved surface.
  • a flange 82 is formed at the end of the outer peripheral surface 81 of the spherical bush 80 on the second side.
  • the spherical bush 80 is inserted toward the first side on the inner periphery of the presser plate 17, and the outer peripheral surface 81 of the spherical bush 80 is in contact with the inner peripheral surface 17 b of the presser plate 17.
  • a fitting portion 83 and a guide hole portion 84 are formed in order from the first side.
  • a spline extending along the axial direction L is formed in the fitting portion 83 of the spherical bush 80, and this spline is fitted with a spline formed on the outer periphery of the rotary shaft 3.
  • the spherical bush 80 can rotate integrally with the rotary shaft 3 and move in the axial direction L.
  • the guide hole portion 84 of the spherical bush 80 has an opening directed to the second side, and is formed in a hollow shape into which the guide portion 91 of the cylinder block 9 can be inserted toward the first side.
  • the outer periphery of the guide portion 91 of the cylinder block 9 and the inner periphery of the guide hole portion 84 of the spherical bush 80 are in contact.
  • the spherical bush 80 can be moved in the axial direction L without being shaken by being guided by the guide portion 91 of the cylinder block 9.
  • a set spring 20 is provided between the spherical bush 80 and the cylinder block 9 to urge them so as to repel them in the axial direction L.
  • a plurality of spring accommodating holes 93 that open toward the first side are formed in the main body 92 of the cylinder block 9, and set springs 20 that are coil springs are fitted into the respective spring accommodating holes 93. Yes.
  • the first side of the set spring 20 protrudes from the cylinder block 9 and abuts against the flange 82 of the spherical bush 80 at the protruding end. Due to the spring force of the set spring 20 and the hydraulic pressure in the cylinder 11, the valve plate sliding contact surface 97 of the cylinder block 9 is pressed against and closely contacts the valve plate 4.
  • the presser plate 17 is pressed to the first side by the spherical bush 80 pressed to the first side by the spring force of the set spring 20 and the hydraulic pressure in the cylinder 11.
  • the shoe 14 is pressed against the sliding contact surface 15 c of the swash plate 15 by the presser plate 17 pressed toward the first side.
  • the operation of the swash plate type hydraulic pump 10 having the above-described configuration when one of the intake / exhaust ports 5 and 6 is used as an intake port and the other intake / exhaust port 6 as a discharge port will be described.
  • the rotary shaft 3 is rotationally driven by a drive device such as an engine
  • the cylinder block 9 rotates integrally with the rotary shaft 3, and the valve plate sliding contact surface 9 a of the cylinder block 9 slides with respect to the valve plate 4. Rotates while touching.
  • Each shoe 14 held by the presser plate 17 rotates together with the cylinder block 9 and the piston 13 while making sliding contact with the sliding contact surface 15 c of the swash plate 15.
  • each piston 13 reciprocates in the cylinder 11 with a stroke corresponding to the maximum tilt angle of the swash plate 15, and in the intake stroke in which each piston 13 pushes from the top dead center to the bottom dead center,
  • the pressure oil sucked into each cylinder 11 is used as high pressure oil from the discharge port 6 to the suction / discharge passage.
  • discharge When the maximum tilt angle of the swash plate 15 is adjusted by a tilt actuator (not shown), the stroke of each piston 13 is changed, whereby the discharge capacity discharged from each cylinder 11 can be variably controlled. .
  • the swash plate type hydraulic pump 10 is configured such that in the assembled state, the gap in the axial direction L between the cylinder block 9 and the spherical bush 80 is zero or very small.
  • assembled state means a state in which the swash plate type hydraulic pump 10 is assembled.
  • the state in which the swash plate type hydraulic pump 10 is operating is not excluded, and the gap in the axial direction L between the cylinder block 9 and the spherical bush 80 may be 0 or very small in the operating state.
  • the gap is 0 means that the spherical bush 80 and the cylinder block 9 are continuous in the axial direction L, and there is no gap between them.
  • the cylinder block 9 and the spherical bush 80 are in contact with each other.
  • a state in which the bush 80 has a gap G (gap) in the axial direction L and the gap G is filled with the filling member F is also included. If the gap between the spherical bush 80 and the cylinder block 9 in the axial direction L is 0, the spherical bush 80 is brought into direct or indirect contact with the cylinder block 9 so that the spherical bush 80 moves in the axial direction L toward the second side. It becomes impossible to move.
  • the gap is very small means that there is a minute gap ⁇ L in the axial direction L between the cylinder block 9 and the spherical bush 80. If there is a minute gap ⁇ L in the axial direction L between the spherical bush 80 and the cylinder block 9, the spherical bush 80 can move in the axial direction L to the second side by the size of the gap ⁇ L. However, the size of the gap ⁇ L is sufficiently small. The size of the gap ⁇ L is such that the amount of movement of the presser plate 17 to the second side accompanying the movement of the spherical bushing 80 to the second side is within a range in which the shoe 14 is not separated from the sliding contact surface 15 c of the swash plate 15.
  • the size of the gap ⁇ L is greater than 0 and 1.2 mm or less, and more desirably greater than 0 and 0.8 mm or less.
  • the gap in the axial direction L between the cylinder block 9 and the spherical bush 80 is designed to be about 3 to 5 mm.
  • an axis line is formed between the first end surface 95 of the cylinder block 9 and the hole bottom 85 (second end surface) of the guide hole portion 84 of the spherical bush 80.
  • An interval G in the direction L is provided.
  • This gap G is filled with a filling member F. Therefore, the cylinder block 9 and the spherical bush 80 are continuous in the axial direction L with no gap, and the gap in the axial direction L is zero.
  • the filling member F is one or more shim plates 30. The number and thickness of the shim plates 30 are appropriately selected according to the size of the gap G.
  • the shim plate 30 is used as the filling member F, even if the size of the gap G varies due to dimensional errors of individual parts, if the number of shim plates 30 is increased or decreased during assembly, the cylinder block 9
  • the gap G in the axial direction L with the spherical bush 80 can be filled with high accuracy.
  • the swash plate type hydraulic pump 10 having the above-described configuration, when the rotary shaft 3 rotates at a high speed in a state where the hydraulic pressure in the cylinder 11 is reduced due to low pressure operation or the like, a shoe by inertia force or centrifugal force that pulls the piston 13 toward the second side. In some cases, the moment to cause 14 to fall is greater than the spring force of the set spring 20. In this case, if the presser plate 17 is pulled by the piston 13 and moves to the second side, the pressing force of the shoe 14 against the swash plate 15 decreases and the shoe 14 falls over.
  • the spherical bush 80 is directly or indirectly connected to the cylinder block 9 when a force is generated to move the presser plate 17 to the second side.
  • the contact to the second side is restricted by contact, and the presser plate 17 is restricted to move to the second side by making contact with the spherical bush 80.
  • the movement of the presser plate 17 to the second side is restricted. Therefore, even in the above case, the shoe 14 is attached to the swash plate 15. It does not float or fall over from the sliding contact surface 15c.
  • the pump 14 is reduced in efficiency due to the sliding rotation of the shoe 14 in a state where the shoe 14 comes into contact with the sliding contact surface 15c of the swash plate 15, the swash plate 15 or Occurrence of uneven wear, galling and seizure of each shoe 14 and the like is suppressed.
  • the set spring 20 having the conventional spring force can be used, so that the friction force between the shoe 14 and the swash plate 15 increases due to the increase of the spring force. Therefore, there is no possibility that the efficiency is lowered or seizure occurs.
  • the swash plate 15 of the swash plate 15 of the shoe 14 is lifted or falls, the number of parts to be added is small and the structure is simple. Further, when the gap G in the axial direction L is filled with the filling member F, the cylinder block 9 and the spherical bush 80 rotate synchronously, so the filling member F and the cylinder block 9 do not slide relatively, and the filling member F and spherical bush 80 do not slide relatively. Therefore, excessive friction does not occur between the cylinder block 9 and the filling member F, and between the spherical bush 80 and the filling member F, and the rotation speed of the swash plate hydraulic pump 10 can be further increased. .
  • FIG. 3 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing an example of a spherical bush and a cylinder block provided with a gap in the axial direction.
  • the swash plate type hydraulic pump 10 shown in FIG. 3 is provided with a small gap ⁇ L in the axial direction L between the cylinder block 9 and the spherical bush 80.
  • the first end surface 95 of the cylinder block 9 and the hole bottom 85 of the guide hole 84 of the spherical bush 80 are separated in the axial direction L, and a gap ⁇ L in the axial direction L exists between them. is doing.
  • the size of the gap ⁇ L is designed to be greater than 0 and 1.2 mm or less, and more desirably greater than 0 and 0.8 mm or less in the assembled swash plate type hydraulic pump 10.
  • FIG. 4 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing Example 2 of a spherical bush and a cylinder block provided with a gap in the axial direction.
  • the second end face 96 of the cylinder block 9 and the flange 82 of the spherical bush 80 are separated from each other in the axial direction L, and a minute gap ⁇ L in the axial direction L exists between them.
  • the set spring 20 includes a plurality of disc springs provided so as to repel between the hole bottom 85 of the guide hole 84 of the spherical bush 80 and the first end surface 95 of the cylinder block 9. It is.
  • FIG. 5 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing a second example of a spherical bush and a cylinder block in which an interval in the axial direction is filled.
  • a gap G in the axial direction L is provided between the first end surface 95 of the cylinder block 9 and the hole bottom 85 of the guide hole portion 84 of the spherical bush 80. This gap G is filled with a filling ring 31.
  • the filling ring 31 is an annular filling member F.
  • An annular groove-shaped accommodation portion 32 is formed in the hole bottom 85 of the guide hole portion 84 of the spherical bush 80, and a part on the first side of the filling ring 31 is embedded in the accommodation portion 32.
  • the end surface on the second side of the filling ring 31 is in contact with the first end surface 95 of the cylinder block 9.
  • the filler 33 is hardened in the state which the filling ring 31 and the 1st end surface 95 of the cylinder block 9 contact
  • the filler 33 may be omitted.
  • FIG. 6 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing Example 3 of a spherical bush and a cylinder block in which the axial distance is filled.
  • a gap G in the axial direction L is provided between the first end surface 95 of the cylinder block 9 and the hole bottom 85 of the guide hole portion 84 of the spherical bush 80.
  • This gap G is filled with the press-fitting bush 41.
  • the press-fitting bush 41 is a cylindrical filling member F.
  • An annular groove-shaped press-fit portion 42 is formed in the hole bottom 85 of the guide hole portion 84 of the spherical bush 80, and the press-fit bush 41 is press-fitted into the press-fit portion 42 toward the first side.
  • the press-fit bush 41 press-fitted into the press-fit portion 42 of the spherical bush 80 cannot be inserted and removed from the press-fit portion 42 due to friction.
  • the second end surface of the press-fitting bush 41 is in contact with the first end surface 95 of the cylinder block 9.
  • a high-strength adhesive may be applied to the outer periphery of the press-fit bush 41, and the press-fit bush 41 and the press-fit bush 41 may be bonded via this adhesive.
  • the press-fitting bush 41 may be loosely fitted without being press-fitted.
  • FIG. 7 is a partially enlarged view of a longitudinal sectional view of a swash plate type hydraulic pump showing a fourth example of a spherical bush and a cylinder block in which an interval in the axial direction is filled. In the example shown in FIG.
  • a gap G in the axial direction L is provided between the second end surface 96 where the spring accommodation hole 93 of the cylinder block 9 is opened and the flange 82 of the spherical bush 80.
  • the gap G is filled with a filling column 35 that is a filling member F.
  • the gap in the axial direction L between the spherical bush 80 and the cylinder block 9 is zero.
  • the cylinder block 9 is provided with a plurality of filling member accommodation holes 98 that open toward the swash plate 15. A filling column 35 is inserted into the filling member accommodation hole 98.
  • the filling column 35 protrudes from the filling member accommodation hole 98 of the cylinder block 9 to the first side, and the protruding first side end surface is in contact with the flange 82 of the spherical bush 80.
  • the time-curable or thermosetting filler 36 is first injected into the filling member accommodation hole 98 of the cylinder block 9, and then the filling column 35 is fitted. . Then, the filler 36 is hardened in a state where the end surface on the first side of the filling column 35 is in contact with the flange 82 of the spherical bush 80.
  • the filler 36 By providing the filler 36 between the cylinder block 9 and the filling column 35 in this way, even if there is a variation in the size of the gap G due to dimensional errors of individual parts, the gap G is used as the filling column. 35 and the filler 36 can be filled with high accuracy. It is desirable that the filler 36 has an adhesive performance that fixes the filling column 35 in the filling member accommodation hole 98 of the cylinder block 9. In this way, when a high-strength adhesive is applied to the outer peripheral portion of the filling column 35 and the filling column 35 and the cylinder block 9 are bonded via this adhesive, the filler 33 may be omitted.
  • the filling member F (filling ring 31, press-fit bush 41, filling column 35) is used to fill the gap G in the axial direction L between the cylinder block 9 and the spherical bush 80.
  • these filling members F may be provided on either the cylinder block 9 or the spherical bush 80.
  • a swash plate type hydraulic pump has been described as an example of the swash plate type hydraulic rotary machine.
  • the swash plate type hydraulic rotary machine to which the present invention is applied is not limited to this.
  • the swash plate type hydraulic rotating machine may be a swash plate type hydraulic motor.
  • the lift of the shoe from the swash plate can be prevented even if the rotational speed of the rotary shaft is increased.
  • the present invention can be widely applied to a swash plate type hydraulic rotating machine having a swash plate having a variable maximum tilt angle regardless of the detailed structure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
PCT/JP2010/007103 2010-12-07 2010-12-07 斜板型液圧回転機 WO2012077157A1 (ja)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2012547597A JPWO2012077157A1 (ja) 2010-12-07 2010-12-07 斜板型液圧回転機
EP10860466.1A EP2650538A1 (en) 2010-12-07 2010-12-07 Skew plate-type hydraulic rotary machine
PCT/JP2010/007103 WO2012077157A1 (ja) 2010-12-07 2010-12-07 斜板型液圧回転機
CN2010800690030A CN103069161A (zh) 2010-12-07 2010-12-07 斜板式液压旋转机
US13/882,832 US20130327208A1 (en) 2010-12-07 2010-12-07 Swash plate type hydraulic rotating machine
KR1020127031763A KR20130030761A (ko) 2010-12-07 2010-12-07 사판형 액압 회전기

Applications Claiming Priority (1)

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PCT/JP2010/007103 WO2012077157A1 (ja) 2010-12-07 2010-12-07 斜板型液圧回転機

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WO2012077157A1 true WO2012077157A1 (ja) 2012-06-14

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EP (1) EP2650538A1 (ko)
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WO2014156547A1 (ja) * 2013-03-29 2014-10-02 カヤバ工業株式会社 対向式斜板型液圧回転機
WO2015166629A1 (ja) * 2014-05-01 2015-11-05 川崎重工業株式会社 斜板形液圧回転機及びその製造方法
CN107387351A (zh) * 2017-09-04 2017-11-24 杭州力龙液压有限公司 柱塞组件、柱塞泵及液压传动装置
CN108547748A (zh) * 2018-04-09 2018-09-18 张家港市海工船舶机械制造有限公司 一种低噪音轴向柱塞泵
JP2020183744A (ja) * 2019-05-09 2020-11-12 ナブテスコ株式会社 油圧ポンプ及び建設機械

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KR20150042855A (ko) 2013-03-29 2015-04-21 카야바 고교 가부시기가이샤 액압 회전기
JP6246582B2 (ja) * 2013-12-16 2017-12-13 日立建機株式会社 液圧回転機械
DE102016223307A1 (de) 2016-11-24 2018-05-24 Danfoss Power Solutions Gmbh & Co. Ohg Hydraulische axialkolbeneinheit mit zentralbefestigtem niederhalter
CN108131266B (zh) * 2018-02-01 2019-08-30 李涌权 流体泵

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WO2014156547A1 (ja) * 2013-03-29 2014-10-02 カヤバ工業株式会社 対向式斜板型液圧回転機
JPWO2014156547A1 (ja) * 2013-03-29 2017-02-16 Ｋｙｂ株式会社 対向式斜板型液圧回転機
US9856851B2 (en) 2013-03-29 2018-01-02 Kyb Corporation Opposed swash plate type fluid pressure rotating machine
WO2015166629A1 (ja) * 2014-05-01 2015-11-05 川崎重工業株式会社 斜板形液圧回転機及びその製造方法
JP2015212522A (ja) * 2014-05-01 2015-11-26 川崎重工業株式会社 斜板形液圧回転機及びその製造方法
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DE112015002089B4 (de) 2014-05-01 2019-08-01 Kawasaki Jukogyo Kabushiki Kaisha Taumelscheiben-Flüssigkeitsdruck-Drehvorrichtung - vorzugsweise Axialkolbenmaschine, mit schwingungsfähiger Gleitschuh-Halteplatte, die von einer verschiebbaren sphärischen Laufbuchse beaufschlagt ist, welche bezüglich der Antriebswelle einen lagerseitig einstellbaren Bewegungsbeschränkungsmechanismus aufweist – und ein Verfah-ren zu deren Herstellung
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GB2540072B (en) * 2014-05-01 2020-06-24 Kawasaki Heavy Ind Ltd Swash plate type liquid-pressure rotating device and method for manufacturing same
CN107387351A (zh) * 2017-09-04 2017-11-24 杭州力龙液压有限公司 柱塞组件、柱塞泵及液压传动装置
CN108547748A (zh) * 2018-04-09 2018-09-18 张家港市海工船舶机械制造有限公司 一种低噪音轴向柱塞泵
JP2020183744A (ja) * 2019-05-09 2020-11-12 ナブテスコ株式会社 油圧ポンプ及び建設機械

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KR20130030761A (ko) 2013-03-27
US20130327208A1 (en) 2013-12-12
CN103069161A (zh) 2013-04-24
JPWO2012077157A1 (ja) 2014-05-19
EP2650538A1 (en) 2013-10-16

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