WO2013153684A1 - 斜軸式アキシャルピストンポンプ・モータ - Google Patents
斜軸式アキシャルピストンポンプ・モータ Download PDFInfo
- Publication number
- WO2013153684A1 WO2013153684A1 PCT/JP2012/064741 JP2012064741W WO2013153684A1 WO 2013153684 A1 WO2013153684 A1 WO 2013153684A1 JP 2012064741 W JP2012064741 W JP 2012064741W WO 2013153684 A1 WO2013153684 A1 WO 2013153684A1
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- WIPO (PCT)
- Prior art keywords
- shaft
- cylinder block
- drive shaft
- support
- mounting hole
- Prior art date
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Classifications
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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
- F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure
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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
- F04B1/128—Driving means
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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
- F04B1/2014—Details or component parts
- F04B1/2035—Cylinder barrels
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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
- F04B1/2014—Details or component parts
- F04B1/2042—Valves
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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
- F04B1/24—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 inclined to the main shaft axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/11—Kind or type liquid, i.e. incompressible
Definitions
- the present invention relates to an oblique axis type axial piston pump / motor.
- the cylinder block is disposed in a state where the axis of the cylinder block is inclined with respect to the drive shaft rotatably supported by the casing. ing.
- a center shaft and a plurality of piston rods are provided on one end surface facing the drive shaft in the cylinder block.
- the center shaft is disposed at a position on the axis of the cylinder block, and the plurality of piston rods are disposed at equal intervals on a circumference centered on the center shaft.
- the support end projecting from one end surface of the cylinder block in the center shaft and the support end projecting from one end surface of the cylinder block in the piston rod are each configured in a spherical shape, and tilt to one end surface of the drive shaft. Supported as possible.
- a valve plate that rotatably supports the cylinder block is in contact with the other end face of the cylinder block.
- the valve plate is provided with a high pressure port and a low pressure port that are selectively connected to the cylinder bore in accordance with the rotational position of the cylinder block.
- a pressure spring is generally interposed between the center shaft and the cylinder block.
- This pressing spring is for preventing leakage when oil passes between the high pressure port of the valve plate and the cylinder bore by pressing the other end face of the cylinder block against the valve plate. Therefore, if a pressure spring having a large mounting load is used as this pressing spring, oil leakage is surely prevented.
- a pressure spring having a large mounting load is used as this pressing spring, oil leakage is surely prevented.
- the shaft portion of the center shaft is configured to have a large diameter, a pressing spring having a large mounting load can be applied, and oil between the valve plate and the cylinder block can be applied. It is possible to improve the volumetric efficiency of the motor by reliably preventing leakage.
- the support end portion of the center shaft and the support end portion of the piston rod are supported on the end surface of the drive shaft by the retainer plate. That is, if the support end of the center shaft and the support end of the piston rod are supported on the end surface of the drive shaft by the retainer plate, the support end of the center shaft and the support end of the piston rod are separated from the end surface of the drive shaft.
- the movement can be prevented, for example, there is no possibility of causing a situation in which the axis of the cylinder block is shifted, and the piston rod can be reliably moved in a stroke.
- the outer dimension of the support end must be larger than the shaft. Therefore, when the shaft portion of the center shaft is configured to have a large diameter so as to apply a pressing spring having a large mounting load, the outer dimensions of the support end portion of the center shaft must be configured to be large. As a result, it is necessary to enlarge the inner diameter of the shaft insertion hole formed in the retainer plate, and the strength of the retainer plate is reduced, so that the support end of the center shaft and the support end of the piston rod are the end surfaces of the drive shaft. A situation may occur that separates from.
- the present invention prevents oil leakage between the valve plate and the cylinder block without causing a situation in which the support end of the center shaft and the support end of the piston rod are separated from the end surface of the drive shaft.
- An object of the present invention is to provide an oblique axis type axial piston pump motor that can be reliably prevented.
- an oblique axis type axial piston pump / motor is disposed inside a casing, has a shaft mounting hole on an axial center of one end surface, and a circle centered on the axial center.
- a cylinder block having a plurality of cylinder bores on the periphery, a plurality of piston rods respectively disposed on the cylinder bores of the cylinder block in a state where a support end projects from the cylinder block, and a base portion of which is a shaft mounting hole of the cylinder block
- a center shaft having a support end projecting from the shaft mounting hole, a drive shaft rotatably supported by the casing in a state in which one end is disposed inside the casing, The support end of the center shaft is placed at a position on one of the end faces of the drive shaft arranged inside.
- a retainer plate that is movably supported, and that supports a support end of the piston rod in a tiltable manner on a circumference centered on the axis of one end surface of the drive shaft; and the other end surface of the cylinder block;
- a valve plate interposed between the casing and rotatably supporting the cylinder block inside the casing, and performing switching control of pressure to the plurality of cylinder bores in accordance with a rotational position of the cylinder block;
- a pressure spring that is disposed in the shaft mounting hole of the cylinder block and acts to press the cylinder block against the valve plate, and when the drive shaft and the cylinder block rotate around their respective axes, According to the tilt angle of the drive shaft and cylinder block, the piston rod In the oblique axis type axial piston pump motor that moves the bore, the center shaft is mounted in the shaft mounting hole of the cylinder block, and has a shaft receiving hole at one end and a spring at the other end.
- An outer race having a housing hole, and an inner shaft having a support portion having an outer dimension larger than that of the base portion at a distal end of a shaft-shaped base portion, and being attached to the shaft portion housing hole of the outer race via the base portion.
- An end surface of the drive shaft is attached to a shaft mounting hole of the cylinder block with one end of the outer race in a state in which the pressing spring is received in the spring receiving hole It is characterized by being supported so as to be tiltable.
- the center shaft is constituted by the outer race and the inner shaft, a pressing spring having a large mounting load can be applied without affecting the outer dimension of the support portion. Therefore, after securing the strength of the retainer plate and preventing the support end of the center shaft and the support end of the piston rod from separating from the end surface of the drive shaft, the mounting load of the pressing spring can be increased. It becomes possible to more reliably prevent oil leakage between the valve plate and the cylinder block.
- FIG. 1 is a cross-sectional view of an oblique axis type axial piston pump / motor according to an embodiment of the present invention.
- 2 is an exploded cross-sectional view of a center shaft applied to the oblique axis type axial piston pump / motor shown in FIG.
- FIG. 1 shows an oblique axis type axial piston motor according to an embodiment of the present invention.
- the oblique axis type axial piston motor exemplified here is used as a traveling hydraulic motor for a vehicle used as a construction machine such as a wheel loader, and includes a casing 10.
- the casing 10 includes a hollow casing main body 11 having one end opened, and a guide plate 12 attached to one end of the casing main body 11 so as to close the opening of the casing main body 11.
- the drive shaft 30 and the cylinder block 40 are accommodated in the hollow interior 11a.
- the drive shaft 30 has a large-diameter second bearing support portion 32 at one end portion of the first bearing support portion 31 having a cylindrical shape, and has a large-diameter disk shape at one end portion of the second bearing support portion 32.
- a disk unit 33 is provided.
- the drive shaft 30 is supported by the casing body 11 via the first bearing support portion 31 and the second bearing support portion 32 with the disk portion 33 positioned in the hollow interior 11 a of the casing body 11. More specifically, a first taper roller bearing 51 is provided between the first bearing support portion 31 of the drive shaft 30 and the casing body 11, and the second bearing support portion 32 of the drive shaft 30 and the casing body are provided.
- a second taper roller bearing 52 is provided, and the drive shaft 30 can be rotated about its own axis 30C relative to the casing body 11.
- the second taper roller bearing 52 is configured to be larger than the first taper roller bearing 51, and the drive shaft 30, the casing body 11, and the taper roller 52 a with the large diameter portion facing the hollow interior 11 a of the casing body 11. It is interposed between.
- the disk portion 33 of the drive shaft 30 is provided with a shaft support portion 33a and a plurality of rod support portions 33b on its end surface.
- the shaft support portion 33a and the rod support portion 33b are substantially hemispherical recesses that open to the end surface of the disk portion 33, respectively.
- the shaft support portion 33 a is formed only at a position on the axis 30 ⁇ / b> C of the drive shaft 30 in the disk portion 33.
- the rod support portions 33b are arranged on a common circumference around the axis 30C of the drive shaft 30, and are provided at seven positions that are equally spaced from each other.
- An escape passage 33c is opened in the shaft support portion 33a.
- the escape passage 33c extends from the shaft support portion 33a along the axis 30C of the drive shaft 30, and then extends so as to be gradually inclined in the outer peripheral direction toward the other end side. It is open to the outer peripheral surface of the drive shaft 30 between the second bearing support portion 32.
- the cylinder block 40 is a columnar member having a circular cross section along the radial direction, and includes a shaft mounting hole 41 and a plurality of cylinder bores 42.
- the shaft mounting hole 41 and the cylinder bore 42 are voids formed along the axis 40 ⁇ / b> C of the cylinder block 40.
- the shaft mounting hole 41 and the cylinder bore 42 have a circular shape with a uniform cross section along the radial direction, and open to one end face 40 a of the cylinder block 40.
- the shaft mounting hole 41 is uniquely formed at a position on the axis 40 ⁇ / b> C of the cylinder block 40.
- the cylinder bores 42 are arranged on a common circumference centered on the axis 40C of the cylinder block 40, and are provided at seven positions that are equally spaced from each other.
- the circumference where the cylinder bore 42 is provided is set to the same dimension as the circumference where the rod support portion 33 b is provided in the disk portion 33 of the drive shaft 30.
- one end surface 40a where the shaft mounting hole 41 and the cylinder bore 42 open is configured as a plane orthogonal to the axis 40C, while the other end surface is formed as a concave surface 40b.
- the concave surface 40b of the cylinder block 40 is formed in a spherical shape having a center on the extension of the axis 40C of the cylinder block 40.
- a communication hole 43 and a plurality of communication passages 44 are opened in the concave surface 40 b of the cylinder block 40.
- the communication hole 43 is an opening provided only at a position on the axis 40 ⁇ / b> C of the cylinder block 40 and communicates with the shaft mounting hole 41.
- the inner diameter of the communication hole 43 is smaller than the inner diameter of the shaft mounting hole 41.
- the communication passage 44 is an opening provided on a circumference centered on the axis 40C of the cylinder block 40, and is arranged at seven positions that are equally spaced from each other.
- the circumference where the communication passage 44 is provided is set to a radius smaller than the circumference where the cylinder bore 42 is provided.
- Each communication passage 44 has an inner diameter smaller than that of the cylinder bore 42 and communicates with the individual cylinder bore 42.
- a valve plate 60 is disposed between the concave surface 40 b of the cylinder block 40 and the guide plate 12 of the casing 10.
- the valve plate 60 has a sliding projecting spherical surface 61 and a sliding projecting cylindrical surface 62, and slidably contacts the concave surface 40 b of the cylinder block 40 via the sliding projecting spherical surface 61.
- the surface 62 is slidably contacted with the guide surface 12a of the guide plate 12 via the surface 62.
- the sliding projection spherical surface 61 is a spherical protruding portion having the same radius of curvature as the concave surface 40b of the cylinder block 40, and can slide in close contact with the concave surface 40b of the cylinder block 40. It is.
- the sliding projecting cylindrical surface 62 is a convex cylindrical surface projecting toward the opposite side of the sliding projecting spherical surface 61.
- the guide surface 12 a of the guide plate 12 with which the sliding projecting cylinder surface 62 abuts has the same radius of curvature as the sliding projecting cylinder surface 62, and has a concave shape with a larger arc length than the sliding projecting cylinder surface 62. It is a cylindrical surface and is formed at a portion facing the disk portion 33 of the drive shaft 30.
- the guide surface 12a of the guide plate 12 includes the center point X of the shaft support portion 33a provided on the disk portion 33 of the drive shaft 30, and a line orthogonal to the axis 30C of the drive shaft 30 is the central axis of the cylinder. The position is set as follows.
- symbol 70 in a figure is an actuator for moving the valve plate 60 along the guide surface 12a of the guide plate 12.
- FIG. 1 an actuator piston 71 as an output element is engaged with the valve plate 60 via a linkage pin 72 so as to be tiltable.
- a high-pressure port and a low-pressure port are opened in a portion corresponding to the communication passage 44 of the cylinder block 40 on the sliding projecting spherical surface 61 of the valve plate 60.
- the high-pressure port and the low-pressure port are connected to a plurality of cylinder bores 42 located on one side when the cylinder block 40 is divided into two on a virtual plane including the axis 40C of the cylinder block 40 and the axis 30C of the drive shaft 30, for example.
- a low pressure port is provided to communicate with a plurality of cylinder bores 42 located on the other side.
- reference numeral 63 in the drawing is a communication passage that penetrates a portion of the valve plate 60 that extends from the sliding projection spherical surface 61 to the sliding projection cylindrical surface 62.
- the communication path 63 is open to the sliding projection spherical surface 61 at a portion facing the axis 40 ⁇ / b> C of the cylinder block 40.
- a piston rod 80 is disposed in the cylinder bore 42, and a center shaft 90 is disposed in the shaft mounting hole 41.
- the piston rod 80 has a taper shape in which the outer diameter gradually increases from the base end toward the tip, and has a support ball head (support end) 81 at the base end, and a piston portion 82 at the tip end. Therefore, it is slidably inserted into the cylinder bore 42 via the piston portion 82.
- the support ball head portion 81 of the piston rod 80 has a spherical shape with an outer diameter that can be slidably inserted into the rod support portion 33 b formed on the disk portion 33 of the drive shaft 30.
- the support ball head 81 of the piston rod 80 is configured to have an outer diameter larger than the outer diameter of the piston portion 82.
- the center shaft 90 is mounted in the shaft mounting hole 41 of the cylinder block 40 and includes an inner shaft 910 and an outer race 920 as shown in FIG.
- the inner shaft 910 has a cylindrical shaft base (base) 911 and a shaft support ball head (support) 912 provided at the base end of the shaft base 911.
- the shaft support sphere head 912 of the inner shaft 910 has a spherical shape with an outer diameter d1 that can be slidably inserted into the shaft support 33a formed on the disk portion 33 of the drive shaft 30.
- the shaft base portion 911 has an outer diameter d2 smaller than the outer diameter d1 of the shaft support ball head 912. As shown in FIG.
- an oil passage 913 is provided in the inner shaft 910 between the end surface of the shaft base 911 and the top of the shaft support ball head 912.
- the oil passage 913 guides this oil to the escape passage 33c formed in the drive shaft 30. Is for.
- the outer race 920 has a cylindrical shape with an outer diameter that can be attached to the shaft attachment hole 41 of the cylinder block 40 without rattling. As shown in FIG. 1, the length of the outer race 920 along the axial direction is longer than that of the shaft mounting hole 41 so that a part of the outer race 920 protrudes to the outside when mounted in the shaft mounting hole 41. As shown in FIG. 2, the outer race 920 is provided with a shaft housing hole 921 and a spring housing hole 922 at a portion on the axial center.
- the shaft accommodating hole 921 is a space that opens at one end surface of the outer race 920, and the cross section along the radial direction has a circular shape.
- the inner diameter of the shaft accommodating hole 921 is formed to a dimension that allows the shaft base 911 of the inner shaft 910 to be mounted without rattling.
- the spring accommodating hole 922 is a space that opens on the other end surface of the outer race 920.
- the spring accommodating hole 922 has a circular cross section along the radial direction, and accommodates the pressing spring 930 therein.
- the pressing spring 930 is a coil spring that is configured so that the outer diameter is slightly smaller than the inner diameter of the spring accommodation hole 922 and the total length in the unloaded state is longer than that of the spring accommodation hole 922.
- a partition wall portion 923 is interposed between the shaft portion accommodation hole 921 and the spring accommodation hole 922.
- the partition wall portion 923 is a disk-shaped portion having a small-diameter through-hole 923 a at the center, and partitions the shaft portion accommodation hole 921 and the spring accommodation hole 922, and receives a spring receiver with respect to the pressing spring 930. It has a function.
- the plurality of piston rods 80 and the center shaft 90 are mounted on a rod support part 33b or a shaft support part 33a formed on the disk part 33 of the drive shaft 30 with their respective spherical heads 81 and 912.
- the retainer plate 100 is fixed to the end surface of the disk portion 33 so that it can be tilted with respect to the end surface of the disk portion 33 in a state in which the movement of the ball heads 81 and 912 from the end surface of the disk portion 33 is restricted. Is supported.
- the retainer plate 100 is a plate-like member having a rod insertion hole 101 at a portion facing the rod support portion 33b of the disk portion 33 and a shaft insertion hole 102 at a portion facing the shaft support portion 33a.
- the rod insertion hole 101 is formed with an inner diameter smaller than the support ball head 81 of the piston rod 80
- the shaft insertion hole 102 is formed with an inner diameter smaller than the shaft support ball head 912 of the center shaft 90. It is.
- the piston rod 80 may be inserted into the rod insertion hole 101 and the center shaft 90 may be inserted into the shaft insertion hole 102 in advance.
- the drive shaft 30 and the cylinder block 40 are separated by a center shaft 90 and a plurality of piston rods 80 interposed between the disk portion 33 of the drive shaft 30 and the cylinder block 40. Is in a state of being linked to each other with the axis centers 30C and 40C intersecting each other.
- the piston rod 80 is sequentially directed toward the drive shaft 30 in the cylinder bore 42 connected to the high pressure port.
- the piston rod 80 is sequentially retracted and the cylinder block 40 is rotated, so that it functions as an oblique axis type axial piston motor having the drive shaft 30 as an output shaft. .
- the shaft support ball head 912 of the center shaft 90 and the support ball head 81 of the piston rod 80 are supported by the disk portion 33 of the drive shaft 30 by the retainer plate 100. ing. Accordingly, the shaft support ball head 912 of the center shaft 90 and the support ball head 81 of the piston rod 80 can be prevented from moving away from the end surface of the disk portion 33. For example, the axial center 40C of the cylinder block 40 is displaced. Therefore, smooth rotation of the cylinder block 40 and the drive shaft 30 can be ensured, and the piston rod 80 can be reliably moved in a stroke.
- the outer diameter of the shaft support ball head 912 is affected even when a pressing spring 930 having a large mounting load is applied. There is nothing. That is, when applying a pressing spring 930 having a large outer dimension in order to prevent oil leakage between the cylinder block 40 and the valve plate 60 more reliably, the outer diameter dimension of the outer race 920 is enlarged and the spring accommodating hole 922 is formed. What is necessary is just to form large, and it is not necessary to comprise the shaft base part 911 of the inner shaft 910 in large diameter.
- the outer diameter of the shaft support ball head 912 it is not necessary to configure the outer diameter of the shaft support ball head 912 to be large, and it is not necessary to increase the inner diameter of the shaft insertion hole 102 of the retainer plate 100, so that sufficient strength can be ensured for the retainer plate 100. It becomes possible. As a result, it is possible to reliably prevent the shaft support sphere head 912 of the center shaft 90 and the support sphere head 81 of the piston rod 80 from being separated from the disk portion 33 of the drive shaft 30.
- the oblique axis type axial piston motor is exemplified, but the present invention can also be applied to an oblique axis type axial piston pump.
- this invention is not necessarily limited to that which can change the tilt angle, and the tilt angle does not change. It can also be applied to a fixed capacity type.
- the shaft housing hole 921 and the spring housing hole 922 of the outer race 920 are formed to have substantially the same inner diameter, but the spring housing is accommodated regardless of the inner diameter of the shaft housing hole 921.
- the inner diameter of the hole 922 may be enlarged. In this case, if a larger outer diameter is applied as the outer race 920, a pressing spring having a larger mounting load can be applied.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Hydraulic Motors (AREA)
- Reciprocating Pumps (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
30 駆動軸
40 シリンダブロック
40a 一端面
41 シャフト装着孔
42 シリンダボア
60 弁板
80 ピストンロッド
81 支持球頭部
90 センタシャフト
100 リテーナプレート
910 インナシャフト
911 シャフト基部
912 シャフト支持球頭部
920 アウタレース
921 軸部収容孔
922 バネ収容孔
930 押圧バネ
Claims (1)
- ケーシングの内部に配設し、一端面の軸心上にシャフト装着孔を備えるとともに、軸心を中心とした円周上に複数のシリンダボアを有したシリンダブロックと、
支持端部が前記シリンダブロックから突出する状態で前記シリンダブロックのシリンダボアにそれぞれ配設した複数のピストンロッドと、
基部が前記シリンダブロックのシャフト装着孔に装着され、かつ支持端部が前記シャフト装着孔から突出したセンタシャフトと、
一方の端部を前記ケーシングの内部に配置した状態で前記ケーシングに回転可能に支持させた駆動軸と、
前記ケーシングの内部に配置した駆動軸の一方の端面においてその軸心上となる位置に前記センタシャフトの支持端部を傾動可能に支持させるとともに、前記駆動軸の一方の端面においてその軸心を中心とした円周上に前記ピストンロッドの支持端部を傾動可能に支持させるリテーナプレートと、
前記シリンダブロックの他端面と前記ケーシングとの間に介在し、前記ケーシングの内部において前記シリンダブロックを回転可能に支持するとともに、前記シリンダブロックの回転位置に応じて前記複数のシリンダボアに対する圧力の切換制御を行う弁板と、
前記シリンダブロックのシャフト装着孔に配設し、前記シリンダブロックを前記弁板に押し付けるように作用する押圧バネと
を備え、前記駆動軸及び前記シリンダブロックがそれぞれの軸心を中心として回転した場合にこれら駆動軸及びシリンダブロックの傾転角に応じて前記ピストンロッドが前記シリンダボアを行程移動する斜軸式アキシャルピストンポンプ・モータにおいて、
前記センタシャフトは、
前記シリンダブロックのシャフト装着孔に装着され、一方の端部に軸部収容孔を有するとともに、他方の端部にバネ収容孔を有したアウタレースと、
軸状を成す基部の先端に前記基部よりも大きな外形寸法の支持部を有し、前記基部を介して前記アウタレースの軸部収容孔に装着されるインナシャフトと
を備え、前記バネ収容孔に前記押圧バネを収容させた状態で前記アウタレースの一方の端部を前記シリンダブロックのシャフト装着孔に装着し、かつ前記インナシャフトの支持部を介して前記駆動軸の端面に傾動可能に支持させることを特徴とする斜軸式アキシャルピストンポンプ・モータ。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/699,900 US9194381B2 (en) | 2012-04-13 | 2012-06-08 | Bent axis type axial piston pump/motor |
DE112012000086.2T DE112012000086B4 (de) | 2012-04-13 | 2012-06-08 | Axialkolbenpumpe/-Motor mit geneigter Achse |
CN201280001451.6A CN103459842B (zh) | 2012-04-13 | 2012-06-08 | 斜轴式轴向活塞泵·马达 |
KR1020127030079A KR101367500B1 (ko) | 2012-04-13 | 2012-06-08 | 사축식 액셜 피스톤 펌프·모터 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012092286A JP5063823B1 (ja) | 2012-04-13 | 2012-04-13 | 斜軸式アキシャルピストンポンプ・モータ |
JP2012-092286 | 2012-04-13 |
Publications (1)
Publication Number | Publication Date |
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WO2013153684A1 true WO2013153684A1 (ja) | 2013-10-17 |
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PCT/JP2012/064741 WO2013153684A1 (ja) | 2012-04-13 | 2012-06-08 | 斜軸式アキシャルピストンポンプ・モータ |
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US (1) | US9194381B2 (ja) |
JP (1) | JP5063823B1 (ja) |
KR (1) | KR101367500B1 (ja) |
CN (1) | CN103459842B (ja) |
DE (1) | DE112012000086B4 (ja) |
WO (1) | WO2013153684A1 (ja) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014129926A1 (ru) * | 2013-02-21 | 2014-08-28 | Fomin Vladimir Fjodorovich | Аксиально-плунжерный насос с рекуперацией энергии |
JP6426717B2 (ja) * | 2013-05-22 | 2018-11-21 | ハイダック ドライブ センター ゲゼルシャフト ミット ベシュレンクテル ハフツング | 斜板式アキシャルピストンポンプ |
US9121395B2 (en) * | 2013-09-25 | 2015-09-01 | The United States of America, as represented by the Administator of the U.S. Environmental Protection Agency | Method for assembling a bent-axis pump/motor |
DE102014206755A1 (de) * | 2014-02-18 | 2015-08-20 | Robert Bosch Gmbh | Verstelleinrichtung einer Axialkolbenmaschine |
DE102014212600B4 (de) * | 2014-06-30 | 2019-04-25 | Danfoss Power Solutions Gmbh & Co. Ohg | Integrierte Schmierpumpe |
EP3020966B1 (en) | 2014-11-11 | 2020-01-22 | Danfoss A/S | Axial piston machine |
CN104481797B (zh) * | 2014-11-29 | 2017-02-22 | 南京萨伯工业设计研究院有限公司 | 液压马达缸体配油盘组件及其加工方法 |
US10612530B2 (en) | 2015-09-30 | 2020-04-07 | Komatsu Ltd. | Bent-axis hydraulic pump motor |
CN107299843A (zh) * | 2015-10-07 | 2017-10-27 | 熵零控股股份有限公司 | 一种柱塞流体机构 |
CN106567740A (zh) * | 2015-10-09 | 2017-04-19 | 熵零控股股份有限公司 | 一种柱塞流体机构 |
CN106593536B (zh) * | 2015-10-14 | 2021-08-24 | 熵零控股股份有限公司 | 小余隙柱塞流体机构 |
CN106593535B (zh) * | 2015-10-14 | 2021-06-22 | 熵零控股股份有限公司 | 主动驱动流体机构 |
CN106761941A (zh) * | 2015-11-20 | 2017-05-31 | 熵零股份有限公司 | 柱塞流体机构 |
CN107060882A (zh) * | 2015-12-12 | 2017-08-18 | 熵零技术逻辑工程院集团股份有限公司 | 一种缩小可变排量流体机构余隙容积的方法、流体机构 |
KR102010585B1 (ko) * | 2018-07-04 | 2019-08-13 | 김찬영 | 유압 모터를 포함하는 공기 조화 장치 및 그를 포함하는 카고 크레인 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS44253Y1 (ja) * | 1967-03-11 | 1969-01-08 | ||
JPS4810722B1 (ja) * | 1969-06-12 | 1973-04-06 | ||
JPS5236303A (en) * | 1975-09-15 | 1977-03-19 | Konbinato Mashin Budouranichi | Mutiipiston type axiallflow hydraulic pumps |
JPS5635568U (ja) * | 1979-08-28 | 1981-04-06 | ||
JPS5638583A (en) * | 1979-09-07 | 1981-04-13 | Kayaba Ind Co Ltd | Slanted-axis-type pump |
JPH1150952A (ja) * | 1997-08-06 | 1999-02-23 | Kayaba Ind Co Ltd | アキシャルピストンポンプまたはモータ |
Family Cites Families (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3073254A (en) * | 1959-12-24 | 1963-01-15 | United Aircraft Corp | Pressure balanced pump |
GB1007129A (en) | 1962-04-06 | 1965-10-13 | Dowty Hydraulic Units Ltd | Hydraulic reciprocating pumps and motors |
US3208395A (en) | 1963-08-30 | 1965-09-28 | Budzich Tadeusz | Cylinder barrel suspension for fluid pressure energy translating device |
FR1605089A (ja) | 1968-01-30 | 1973-01-12 | ||
FR2135776A5 (ja) | 1971-04-28 | 1972-12-22 | Renault | |
DE2262026C3 (de) | 1972-12-19 | 1978-06-22 | Hans Dipl.-Ing. 7502 Malsch Molly | Axialkolbenmaschine |
AU536164B2 (en) | 1979-11-21 | 1984-04-19 | Ifield Engineering Pty. Ltd. | Hydraulic pump or motor |
JPS57137662A (en) * | 1981-02-18 | 1982-08-25 | Hitachi Ltd | Axial piston |
JPS58177816U (ja) | 1982-05-21 | 1983-11-28 | 日本無線株式会社 | 漁網深度表示装置 |
DE3340333C1 (de) | 1983-11-08 | 1985-06-27 | Hydromatik GmbH, 7915 Elchingen | Taumelscheiben-Axialkolbenpumpe |
JPH0810722B2 (ja) | 1986-02-19 | 1996-01-31 | 株式会社日立製作所 | 移載装置 |
JPH0746924B2 (ja) | 1987-05-29 | 1995-05-24 | ヤンマーディーゼル株式会社 | トラクタ−の作業機装着装置 |
JP2503355Y2 (ja) | 1988-05-19 | 1996-06-26 | エヌテイエヌ株式会社 | 斜軸型ピストンポンプ・モ―タの主軸受装置 |
JP3392975B2 (ja) * | 1995-02-27 | 2003-03-31 | 日立建機株式会社 | 可変容量型斜軸式液圧回転機 |
DE19649195C1 (de) | 1996-11-27 | 1998-01-08 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit Lagerspülung |
JP3776585B2 (ja) | 1998-03-09 | 2006-05-17 | カヤバ工業株式会社 | アキシャルピストンポンプまたはモータ |
CA2418775A1 (en) * | 2000-06-20 | 2001-12-27 | Folsom Technologies, Inc. | Hydraulic pump and motor |
DE10030147C1 (de) * | 2000-06-20 | 2002-06-06 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine |
WO2007060822A1 (ja) * | 2005-11-24 | 2007-05-31 | Komatsu Ltd. | 斜軸式可変容量型ポンプ・モータ |
ITBS20070094A1 (it) * | 2007-07-12 | 2009-01-13 | Omfb S P A Hydraulic Component | Pompa ad asse inclinato |
JP5405342B2 (ja) | 2010-02-12 | 2014-02-05 | 日立建機株式会社 | 液圧回転機 |
-
2012
- 2012-04-13 JP JP2012092286A patent/JP5063823B1/ja active Active
- 2012-06-08 WO PCT/JP2012/064741 patent/WO2013153684A1/ja active Application Filing
- 2012-06-08 DE DE112012000086.2T patent/DE112012000086B4/de active Active
- 2012-06-08 CN CN201280001451.6A patent/CN103459842B/zh active Active
- 2012-06-08 US US13/699,900 patent/US9194381B2/en active Active
- 2012-06-08 KR KR1020127030079A patent/KR101367500B1/ko not_active IP Right Cessation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS44253Y1 (ja) * | 1967-03-11 | 1969-01-08 | ||
JPS4810722B1 (ja) * | 1969-06-12 | 1973-04-06 | ||
JPS5236303A (en) * | 1975-09-15 | 1977-03-19 | Konbinato Mashin Budouranichi | Mutiipiston type axiallflow hydraulic pumps |
JPS5635568U (ja) * | 1979-08-28 | 1981-04-06 | ||
JPS5638583A (en) * | 1979-09-07 | 1981-04-13 | Kayaba Ind Co Ltd | Slanted-axis-type pump |
JPH1150952A (ja) * | 1997-08-06 | 1999-02-23 | Kayaba Ind Co Ltd | アキシャルピストンポンプまたはモータ |
Also Published As
Publication number | Publication date |
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DE112012000086B4 (de) | 2017-11-09 |
CN103459842A (zh) | 2013-12-18 |
CN103459842B (zh) | 2014-08-27 |
DE112012000086T5 (de) | 2014-07-03 |
KR20130129069A (ko) | 2013-11-27 |
KR101367500B1 (ko) | 2014-02-25 |
JP5063823B1 (ja) | 2012-10-31 |
US20150030471A1 (en) | 2015-01-29 |
JP2013221431A (ja) | 2013-10-28 |
US9194381B2 (en) | 2015-11-24 |
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