WO2019080384A1 - 一种全外排压紧式轴向柱塞泵或马达 - Google Patents

一种全外排压紧式轴向柱塞泵或马达

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Publication number
WO2019080384A1
WO2019080384A1 PCT/CN2018/073225 CN2018073225W WO2019080384A1 WO 2019080384 A1 WO2019080384 A1 WO 2019080384A1 CN 2018073225 W CN2018073225 W CN 2018073225W WO 2019080384 A1 WO2019080384 A1 WO 2019080384A1
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WO
WIPO (PCT)
Prior art keywords
spring
piston pump
axial piston
housing
boss
Prior art date
Application number
PCT/CN2018/073225
Other languages
English (en)
French (fr)
Inventor
邓海顺
王海峰
王庆春
汪春燕
王涛
何士举
毛飞宇
Original Assignee
安徽理工大学
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 安徽理工大学 filed Critical 安徽理工大学
Publication of WO2019080384A1 publication Critical patent/WO2019080384A1/zh

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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
    • F04B1/14—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 stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F04B1/148—Bearings therefor
    • 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
    • F03C1/061—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 stationary cylinders
    • F03C1/0615—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 stationary cylinders distributing members
    • 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
    • F03C1/061—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 stationary cylinders
    • F03C1/0623—Details, component parts
    • 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
    • F03C1/061—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 stationary cylinders
    • F03C1/0623—Details, component parts
    • F03C1/0631—Wobbler or actuated element
    • 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
    • F03C1/061—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 stationary cylinders
    • F03C1/0623—Details, component parts
    • F03C1/0631—Wobbler or actuated element
    • F03C1/0634—Actuated element bearing means 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
    • F03C1/0644—Component parts
    • F03C1/0663—Casings, housings
    • F03C1/0665—Cylinder barrel 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
    • F03C1/0676—Arrangement for pressing the cylinder barrel against the valve 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
    • F04B1/14—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 stationary cylinders
    • F04B1/141—Details or component parts
    • 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
    • F04B1/14—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 stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • 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
    • F04B1/14—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 stationary cylinders
    • F04B1/18—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 stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • F04B1/188—Plate-like distribution members
    • 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
    • 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
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels

Definitions

  • the invention relates to the technical field of an axial piston pump or a motor in a hydraulic machine, in particular to a full-extreme compression axial piston pump or motor.
  • Axial piston pumps and motors are important components of the hydraulic system.
  • axial piston pumps and motors are reversible, with only partial structural differences. Therefore, only the full-extreme compression axial piston pump is discussed in the present invention, and the structural design of the motor can be similar.
  • the axial piston pump is a variable displacement pump with small volume, high efficiency and high working pressure.
  • the power is driven by the main shaft through the spline to rotate the rotor.
  • the multiple plungers evenly distributed on the rotor pass the ball hinge and the pressure plate to slide the shoes. Pressing on the surface of the friction plate of the swash plate, since the plane of the swash plate has a certain inclination angle with respect to the rotation axis, the plunger not only rotates together with the rotor, but also reciprocates linearly along the plunger hole of the rotor to complete the plunger pump. The process of sucking and draining oil.
  • the pressing mechanism of the axial piston pump must provide the pre-tightening force to the sliding shoe pair and the distribution pair, and at the same time ensure that the cylinder or the distribution plate is in a floating state, thereby achieving the optimal oil film thickness of the hydraulic static balance, so that the cylinder body and the matching
  • the oil pan, the sliding shoe and the variable head are operated under pure liquid friction.
  • the common plunger pump There are two kinds of compression methods for the common plunger pump: one is to install a spring in the plunger hole of the cylinder body, and provide an axial thrust to the plunger, so that the plunger ball head acts on the sliding shoe, and the sliding shoe is pressed Tight to the surface of the swash plate, but the uninterrupted telescopic movement will cause huge wear on the spring, which will eventually lead to spring fatigue failure, which will adversely affect the working stability of the plunger pump.
  • the second is to provide a central spring between the cylinder and the pressure plate. The central spring is placed against the pressure plate to generate pre-pressure. There is enough clearance between the pressure plate and the cylinder, the plunger can move freely, and the spring is always in compression state. It is only subjected to static load and does not cause fatigue failure.
  • the structural size of the spring is small and the pre-stress is large, that is, the rigidity of the spring is large, which puts high requirements on the structural design of the plunger pump and improves the processing difficulty.
  • the patent of Chinese Patent Publication No. CN104863813A proposed by the first inventor of the present invention discloses a swash plate type axial piston pump or a pressing device for a motor.
  • the cylinder body of the pressing device and the bottom surface of the sliding shoe are provided with an outwardly protruding annular ring, and the compression spring is placed in the spring cavity of the pressure ring, and the compression spring provides a thrust to the pressure ring, so that the pressure ring is pressed against the pressure ring.
  • the disc presses the shoe against the surface of the swash plate.
  • the pressing device provides a continuous pressure between the shoe and the swash plate by providing a continuous pressure to the pressure plate, and provides an effective and effective squeezing method for the axial piston pump or the motor, thereby improving the axial direction.
  • the working stability of the plunger pump or motor is not limited:
  • the sliding shoe pair of the pressing mechanism and the distribution pair share a pressing device, and the sliding shoe pair and the distribution pair interact with each other, which increases the design difficulty.
  • the pressing mechanism has high requirements on the processing precision of the pressure ring and the pressure plate, and no positioning mechanism is added, which is easy to take off the boot phenomenon, which improves the assembly difficulty and reduces the production efficiency.
  • the invention relates to a full-extact compression axial piston pump or motor, which provides a stable sliding shoe pair by providing continuous pressure to the pressure plate, and applies a thrust to the cylinder through a spring to make the cylinder
  • the body is in a floating state, forming a stable distribution pair.
  • the fully externally-pressed axial piston pump or motor makes the sliding shoe pair and the distribution pair of the plunger pump in a separate pressing state without affecting each other, and has a simple structure and is easy to assemble, thereby effectively improving the plunger pump or the motor. Work performance.
  • a full-extact compression axial piston pump or motor including a distribution plate, a cylinder block, a casing, a swash plate and a transmission shaft, the front end cover and the casing
  • the body is connected by a screw; the rear end cover is connected to the housing by bolts; the transmission shaft is driven to rotate by a spline driving distribution plate and a swash plate, and the full outer row pressing mechanism comprises a distribution pair outer row pressing device and sliding
  • the shoe is equipped with a pair of outer pressing devices.
  • the distribution pair outer row pressing device comprises a self-lubricating guide column, a self-lubricating guide sleeve and a cylindrical coil spring; the cylinder body is provided with an outer ring boss, and a guide post hole is opened on the boss.
  • the self-lubricating guide post is installed in the guide post hole of the cylinder; the housing is provided with an inner ring boss, and a guide sleeve hole and a spring mounting groove are formed on the boss, and the self-lubricating guide sleeve is mounted on the housing
  • the cylindrical coil spring is installed in the spring mounting groove of the housing, and is in contact with the outer ring boss surface of the cylinder body, and the pressure is applied to the boss by the compression spring; the cylinder body and the housing pass The self-lubricating guide post and the guide sleeve are slidably matched.
  • the sliding shoe pair outer pressing device comprises a base and a universal ball spring plunger; the inclined surface of the swash plate is provided with a one-out outward boss, and the swash plate has a base on the boss
  • the mounting hole is installed in the corresponding base mounting hole; the universal ball spring plunger is mounted on the base, the ball head is in contact with the surface of the pressure plate, and the spring is compressed to apply pressure to the surface of the pressure plate through the ball head.
  • a plurality of guide post mounting holes are arranged on the outer ring boss of the cylinder to be uniformly and symmetrically distributed around the axis.
  • the guide sleeve mounting holes on the housing are consistent with the center position of the cylinder guide post mounting holes, and the number is the same.
  • the spring mounting groove on the housing is concentric with the guide sleeve mounting hole.
  • the beveled end of the swash plate is provided with a boss that is outwardly outward, and the surface of the boss is parallel to the surface of the swash plate.
  • the swash plate boss is provided with a plurality of base mounting holes uniformly distributed symmetrically about the axis.
  • the surface of the base is machined with an external thread and is screwed to the base mounting hole.
  • the front end of the base is provided with a blind hole, and the internal thread is processed, and the surface of the universal ball spring plunger is machined with an external thread and is screwed with the base.
  • the outer row is compacted and the anti-overturning ability is strong.
  • the spring force in the invention acts on the outer ring of the cylinder block and the pressure plate, and the force arm is large, which is more advantageous for balancing the cylinder body and the sliding shoe and preventing overturning.
  • the invention applies pressure to the surface of the pressure plate through the ball head of the universal ball spring spring plunger, and the pressure plate presses the sliding shoe against the surface of the swash plate, and the spring in the universal ball spring spring plunger is always in a compressed state, and no telescopic movement is prevented, thereby preventing The fatigue failure of the spring due to the telescopic movement; the main friction form of the ball head and the pressure plate of the universal ball spring plunger is rolling friction, which greatly reduces the friction and wear of the pressure plate.
  • the invention adopts a self-lubricating guide column and a guide sleeve which are uniformly and symmetrically distributed around the axis to realize precise positioning of the cylinder body and the shell.
  • the self-lubricating guide column and the guide sleeve have high precision of matching, excellent guiding function, self-lubricating characteristics, and do not affect the cylinder.
  • the body is floating and easy to disassemble and replace, reducing production costs.
  • the cylindrical coil spring and the universal ball spring plunger are uniformly mounted symmetrically about the axis, which is equivalent to uniformly applying the spring force to the cylinder block and the swash plate to form a stable distribution pair and a sliding shoe pair, and the spring is always Being in a compressed state slows down the fatigue failure of the spring and improves the reliability of the plunger pump.
  • the invention adopts two sets of independent pressing devices to realize the pressing action of the distribution pair and the sliding shoe pair, and the two sets of pressing mechanisms do not affect each other, thereby improving the stability of the pressing device.
  • Figure 1 is a schematic structural view of the present invention
  • Figure 2 is a schematic view of the pressing torque of the present invention
  • Figure 3 is a cross-sectional view of the cylinder block of the present invention.
  • Figure 4 is a cross-sectional view of the housing of the present invention.
  • Figure 5 is a partial elevational view of the housing of the present invention.
  • Figure 6 is a front elevational view of the valve plate of the present invention.
  • Figure 7 is a cross-sectional view of the swash plate of the present invention.
  • Figure 8 is a schematic view of the base of the present invention.
  • Figure 9 is a schematic view of the flow sub-clamping mechanism of the present invention.
  • Figure 10 is a schematic view of a fully externally packed multi-row axial piston pump.
  • Figure 11 is a schematic view of a full-outer compression axial piston pump that drives the cylinder to rotate with a drive shaft.
  • a full-extact compression axial piston pump or motor including a distribution plate 2 , a cylinder 3 , a housing 4 , and a swash plate 10 .
  • the drive shaft 11, the front end cover 12 and the housing 4 are connected by screws; the rear end cover 1 is connected with the housing 4 by bolts; the drive shaft 11 is driven by the spline driving the distribution plate 2 and the swash plate 10,
  • the full-external pressing mechanism includes a distribution pair outer row pressing device 5 and a sliding shoe pair outer row pressing device 7.
  • the distribution pair outer row pressing device 5 comprises a self-lubricating guide column 51, a self-lubricating guide sleeve 53, and a cylindrical coil spring 52; the cylinder block 3 is provided with an outer ring boss, and a guide post hole is formed on the boss.
  • the self-lubricating guide post 51 is mounted in the guide post hole of the cylinder block 3; the housing 4 is provided with an inner ring boss, and a guide sleeve hole and a spring mounting groove are formed on the boss, the self-lubricating guide sleeve 53 is mounted in the guide hole of the housing 4, the cylindrical coil spring 52 is mounted in the spring mounting groove of the housing 4, and is in contact with the outer ring boss surface of the cylinder 3, and the pressure is applied to the boss by the compression spring.
  • the cylinder 3 and the housing 4 are slidably engaged by a self-lubricating guide post and a guide sleeve.
  • the sliding shoe pair outer row pressing device 7 comprises a base 71 and a universal ball spring plunger 72; the inclined surface of the swash plate 10 is provided with a one-out outward boss, and the boss of the swash plate 10 is provided a base mounting hole, the base 71 is mounted in a corresponding base mounting hole; the universal ball spring plunger 72 is mounted on the base 71, and the ball head is in contact with the surface of the pressure plate 9, compressing the spring, and pressing the ball through the ball Pressure is applied to the surface of the disc.
  • the transmission shaft 11 is connected to the swash plate 10 and the valve plate 2 by a spline, and the transmission shaft 11 drives the swash plate 10 and the valve plate 2 to rotate;
  • the cylinder 3 The cylinder 4 is in a floating state with the housing 4 through the self-lubricating guide post 51 and the self-lubricating guide sleeve 53;
  • the cylindrical coil spring 52 is mounted in a spring mounting groove of the housing 4 which is uniformly symmetrically distributed around the axis, and the cylinder
  • the surface of the outer ring boss on the body 3 is in contact with each other, and the cylinder 3 is pressed to make the cylinder 3 and the valve plate 2 abut against each other to form a flow distribution pair;
  • the universal ball spring plunger 72 is mounted evenly around the axis of the swash plate 10.
  • a spring acts on the surface of the pressure plate 9, pressing the pressure plate 9 against the surface of the swash plate 10, so that the sliding shoe 8 and the swash plate 10 are closely fitted to form a sliding shoe pair; the sliding shoe pair and the distribution pair are separately pressed Tightly, do not affect each other, and the springs in the cylindrical coil spring 52 and the universal ball spring plunger 72 are always in a compressed state, and there is no reciprocating linear motion, which reduces the fatigue loss of the spring, and the cylindrical coil spring 52 is outside the cylinder 3.
  • the ring, the universal ball spring plunger 72 is located on the outer ring of the boss of the swash plate 10. The spring force has a large force arm, which effectively reduces the design requirements of the spring.
  • the working mode of the above embodiment of the present invention is as shown in Figs. 1 and 2: when the transmission shaft 11 drives the valve disc 2 and the swash plate 10 to rotate clockwise, the upper plunger 6 of Fig. 1 starts to suck oil, and the lower plunger 6 starts to drain oil. .
  • the suction in the suction plunger chamber will cause the plunger 6 to be disengaged from the swash plate 10 together with the shoe 8, and the pressing force on the platen 9 will press the shoe 8 against the swash plate 10, causing the shoe 8 to be pressed against the swash plate 10. s surface. It can be seen from FIG.
  • the force arm A of the pressing force of the sliding portion of the sliding shoe pair in the embodiment of the present invention is far larger than the force arm B of the central spring pressing force in the prior art, which is more advantageous for the balance of the sliding shoe 8 and prevents slippage.
  • the boot 8 is overturned.
  • the force arm C of the pressing force is close to the maximum outer diameter of the cylinder block 3, and the force arm is large, which is more favorable for the stability of the cylinder block 3 and prevents the cylinder block 3 from tipping over.
  • the self-lubricating guide post 51 is interference-fitted with the guide post mounting hole on the outer ring boss of the cylinder block 3, and the guide post mounting hole surrounds the cylinder block 3.
  • the axes are evenly symmetrically distributed.
  • the self-lubricating guide sleeve 53 has an interference fit with the guide sleeve mounting hole on the inner ring boss of the housing 4, and the guide sleeve mounting hole and the matching guide post mounting hole are in the same position, and the number is the same.
  • the guide column and the guide sleeve which are uniformly and symmetrically fitted and matched will accurately position the cylinder block 3, and the self-lubricating characteristics of the guide pillar and the guide bushing will not affect the floating of the cylinder block 3.
  • the self-lubricating guide column and the guide bush are slidably engaged to realize the connection between the cylinder block 3 and the casing 4, which is convenient for disassembly and replacement, and avoids the phenomenon of replacing the cylinder block 3 or the casing 4 as a whole due to damage of the connecting component, and improves the axial direction.
  • the working stability of the plunger pump or motor greatly reduces production costs and assembly difficulties.
  • the spring mounting groove is coaxial with the guide sleeve mounting hole, and the cylindrical coil spring 52 is mounted in the spring mounting groove to act on the cylinder 3.
  • the surface of the boss, the axis of the cylindrical coil spring 52 coincides with the axis of the self-lubricating guide post 51, and the spring force acts uniformly in the region centered on the axis of the self-lubricating guide post 51; a plurality of uniformly distributed cylindrical coil springs 52 At the same time, it will provide a constant pressure to the cylinder 3.
  • the self-lubricating guide column 51 also provides a guiding action to the cylindrical coil spring 52, so that the cylindrical coil spring 52 always acts along the axial direction, avoiding the radial large fluctuation of the spring.
  • the pressing structure makes the axial piston pump structure more compact, reduces the volume of the pump, and saves production costs.
  • the beveled end of the swash plate 10 is provided with a boss that is outwardly outward, and the surface of the boss is parallel to the slope of the swash plate 10, and the boss
  • the upper opening is provided with a base mounting hole uniformly distributed symmetrically about the axis, and the base 71 is screwed to the corresponding base mounting hole.
  • the universal ball spring plunger 72 is mounted on the base 71, and the ball is pressed against the platen 9 by its ball head to bring the shoe 8 into close contact with the swash plate 10.
  • the base 71 is directly mounted from the outer surface of the boss of the swash plate 10, which greatly reduces the assembly difficulty and saves processing time. At the same time, the base 71 serves as a common part for detachable replacement, which avoids the integral processing of the swash plate 10 and reduces the processing cost caused by the damage of the base 71.
  • the full-row compression type multi-row axial piston pump, the swash plate in this embodiment has a plurality of staggered planes, and the commonly used compression
  • the method cannot provide continuous and stable pressure to the sliding shoe pair and the distribution pair, and the pressing device has a complicated structure and low stability. If the full-extacting axial piston pump or motor structure of the above embodiment of the present invention is used, the sliding pair and the distribution pair can be separately pressed to effectively improve the operational reliability of the axial piston pump or the motor.
  • the structure is simple and easy to assemble.
  • a full outer row compression axial piston pump as shown in FIG.
  • this embodiment drives the cylinder to rotate by the drive shaft to realize the process of sucking and discharging oil, but the full outer pressing mechanism is still applicable.
  • a plurality of bases are uniformly symmetrically mounted on the outer ring of the cylinder outer ring, and a corresponding universal ball spring plunger is mounted on the base, and the separate pressing of the flow distribution pair is realized by the action of the spring force; the pressing of the auxiliary part of the sliding shoe
  • the above embodiments are the same.
  • the above embodiment shows that the full-external compression type axial piston pump or the pressing mechanism of the motor of the present invention has universal applicability to an axial piston pump or a motor, and has a broad market prospect.

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Abstract

一种全外排压紧式轴向柱塞泵或马达，包括配流盘（2）、缸体（3）、壳体（4）、斜盘（10）和传动轴（11），前端盖（12）与壳体（4）通过螺钉连接；后端盖（1）与壳体（4）通过螺栓连接；缸体（3）与壳体（4）通过自润滑导柱（51）、自润滑导套（53）滑动配合，圆柱螺旋弹簧（52）安装在壳体（4）凸台中，作用在缸体（3）凸台表面，实现配流副压紧；万向滚珠弹簧柱塞（72）安装在斜盘（10）凸台的底座（71）上，其球头作用在压盘（9）表面，实现滑靴副压紧。滑靴副与配流副均为外排压紧，互不干扰，弹簧力作用力臂大，滑靴（8）和缸体（3）的抗倾覆能力强，结构简单实用，易于装配。

Description

一种全外排压紧式轴向柱塞泵或马达 技术领域
本发明涉及液压机械中的轴向柱塞泵或马达技术领域，具体为一种全外排压紧式轴向柱塞泵或马达。
背景技术
轴向柱塞泵和马达是液压***的重要元件，在原理上，轴向柱塞泵和马达是可逆的，只在部分结构上存在差异。因此本发明书中只论述全外排压紧式轴向柱塞泵，马达的结构设计可以与之相类似。
轴向柱塞泵是一种体积小，效率高，工作压力高的变量泵，动力由主轴通过花键带动转子旋转，均匀分布在转子上的多个柱塞通过球铰、压盘将滑靴压在斜盘的摩擦板表面上，由于斜盘平面相对于旋转轴线有一定的倾角，因此柱塞不仅与转子一起旋转，还沿着转子的柱塞孔作往复直线运动，完成柱塞泵的吸排油的过程。
轴向柱塞泵的压紧机构必须给滑靴副和配流副提供预紧力，同时保证缸体或配流盘处于浮动状态，从而达到液压静力平衡的最佳油膜厚度，使缸体与配油盘、滑靴与变量头之间处于纯液体摩擦下运转。常用柱塞泵的压紧方式有两种：一是在缸体的柱塞孔中安装弹簧，对柱塞提供一个轴向的推力，使柱塞球头作用在滑靴上，将滑靴压紧在斜盘表面，但是不间断的伸缩运动将会对弹簧产生巨大的磨损，最终导致弹簧疲劳失效，对柱塞泵的工作稳定性产生不良影响。二是在缸体和压盘之间设置中心弹簧，中心弹簧顶着压盘，产生预压力，压盘和缸体之间有足够的间隙，柱塞能够***，并且弹簧始终处于压 缩状态，且只受静载荷作用，不会产生疲劳失效。但是弹簧的结构尺寸要小而预压力要大，即弹簧的刚度要大，这对柱塞泵的结构设计提出了较高要求，且提高了加工难度。
为了提供一种结构简单的普适性压紧机构，本发明的第一发明人提出的中国专利公布号CN104863813A的专利公开了一种斜盘式轴向柱塞泵或马达的压紧装置。该压紧装置的缸体和滑靴底面设有向外凸出的圆环形挡块，压缩弹簧放置在压环的弹簧腔内，压缩弹簧对压环提供一个推力，使压环压向压盘，将滑靴压紧在斜盘表面。该压紧装置通过对压盘提供一个持续的压力来实现滑靴与斜盘的紧密贴合，为轴向柱塞泵或马达提供了一种实际有效的外排压紧方式，提高了轴向柱塞泵或马达的工作稳定性。但仍有如下问题需要解决：
1.该压紧机构的滑靴副与配流副共用一个压紧装置，滑靴副与配流副相互影响，增加了设计难度。
2.该压紧机构对于压环和压盘的加工精度要求较高，且没有加装定位机构，容易发生脱靴现象，提高了装配难度，降低了生产效率。
本发明涉及的一种全外排压紧式轴向柱塞泵或马达，通过对压盘提供持续的压力，使柱塞泵形成稳定的滑靴副，通过弹簧对缸体施加推力，使缸体处于浮动状态，形成稳定的配流副。全外排压紧式轴向柱塞泵或马达使柱塞泵的滑靴副与配流副处于单独压紧状态，互不影响，且结构简单，易于装配，有效的提高了柱塞泵或马达的工作性能。
发明内容
本发明的目的在于提供一种全外排压紧式轴向柱塞泵或马达，以 解决上述背景技术中提出的问题。
为实现上述目的，本发明提供如下技术方案：一种全外排压紧式轴向柱塞泵或马达，包括配流盘、缸体、壳体、斜盘和传动轴,所述前端盖与壳体通过螺钉连接；所述后端盖与壳体通过螺栓连接；所述传动轴通过花键驱动配流盘和斜盘转动，所述全外排压紧机构包括配流副外排压紧装置和滑靴副外排压紧装置。
优选的方案，所述配流副外排压紧装置包括自润滑导柱、自润滑导套、圆柱螺旋弹簧；所述缸体设有外圈凸台，并在凸台上开设导柱孔，所述自润滑导柱安装在缸体的导柱孔中；所述壳体设有内圈凸台，并在凸台上开设导套孔和弹簧安装槽，所述自润滑导套安装在壳体的导套孔中，所述圆柱螺旋弹簧安装在壳体的弹簧安装槽中，并与缸体的外圈凸台表面接触，通过压缩弹簧给凸台提供压力；所述缸体与壳体通过自润滑导柱、导套滑动配合。
优选的方案，所述滑靴副外排压紧装置包括底座和万向滚珠弹簧柱塞；所述斜盘的斜面设有一周向外的凸台，所述斜盘的凸台上设有底座安装孔，所述底座安装在相应的底座安装孔中；所述万向滚珠弹簧柱塞安装在底座上，其球头与压盘表面接触，压缩弹簧，通过球头给压盘表面施加压力。
优选的方案，所述缸体外圈凸台上开设若干个围绕轴线均匀对称分布的导柱安装孔。
优选的方案，所述壳体上的导套安装孔与缸体导柱安装孔中心位置一致，且数量相同。
优选的方案，所述壳体上的弹簧安装槽与导套安装孔同轴心。
优选的方案，所述斜盘的斜面端设有一周向外的凸台，且凸台表面与斜盘表面平行。
优选的方案，所述斜盘凸台上设置若干个围绕轴线均匀对称分布的底座安装孔。
优选的方案，所述底座的表面加工外螺纹，并与底座安装孔螺纹连接。
优选的方案，所述底座的前端开设盲孔，并加工内螺纹，万向滚珠弹簧柱塞表面加工有外螺纹，并与底座螺纹连接。
与现有技术相比，本发明的有益效果是：
1.外排压紧，抗倾覆能力强。本发明中的弹簧力作用于缸体和压盘的外圈，作用力臂大，更有利于缸体和滑靴的平衡，防止倾覆。
2.降低弹簧损耗，减少压盘磨损。本发明通过万向滚珠弹簧柱塞的球头给压盘表面施加压力，压盘将滑靴压紧在斜盘表面，万向滚珠弹簧柱塞中弹簧始终处于压缩状态，没有伸缩运动，防止了弹簧因为伸缩运动而导致的疲劳失效；万向滚珠弹簧柱塞的球头与压盘的主要摩擦形式是滚动摩擦，大大降低了压盘的摩擦磨损。
3.定位精准，易于装配。本发明采用围绕轴线均匀对称分布的自润滑导柱、导套配合实现缸体与壳体的精准定位，自润滑导柱、导套配合精度高，导向功能优异，具有自润滑特性，不影响缸体的浮动性，且易于拆卸更换，降低了生产成本。
4.弹簧力的分布更为合理均匀。本发明中圆柱螺旋弹簧和万向滚 珠弹簧柱塞都是围绕轴线均匀对称安装的，相当于将弹簧力均匀施加在缸体和斜盘上，形成稳定的配流副和滑靴副，且弹簧一直处于压缩状态，减缓了弹簧的疲劳失效，提高了柱塞泵的可靠性。
5.互为独立的压紧机构。本发明采用两组互为独立的压紧装置实现配流副和滑靴副的压紧作用，两组压紧机构互不影响，提高了压紧装置的稳定性。
附图说明
图1为本发明结构示意图；
图2为本发明压紧力矩示意图；
图3为本发明中缸体的剖视图；
图4为本发明中壳体的剖视图。
图5为本发明中壳体的局部视图。
图6为本发明中配流盘的正视图。
图7为本发明中斜盘的剖视图。
图8为本发明中底座示意图。
图9为本发明中配流副压紧机构示意图。
图10为全外排压紧式多排轴向柱塞泵示意图。
图11为以传动轴带动缸体转动的全外排压紧式轴向柱塞泵示意图。
图中：1-后端盖；2-配流盘；3-缸体；4-壳体；5-配流副外排压紧装置；51-自润滑导柱；52-圆柱螺旋弹簧；53-自润滑导套；6-柱塞；7-滑靴副外排压紧装置；71-底座；72-万向滚珠弹簧柱塞；8- 滑靴；9-压盘；10-斜盘；11-传动轴；12-前端盖。
具体实施方式
为使本发明实施方式的目的、技术方案和优点更加清楚，下面将结合本发明实施方式中的附图，对本发明实施方式中的技术方案进行清楚、完整地描述，显然，所描述的实施方式是本发明一部分实施方式，而不是全部的实施方式。基于本发明中的实施方式，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施方式，都属于本发明保护的范围。
请参阅图1至图9所示，本发明提供一种技术方案：一种全外排压紧式轴向柱塞泵或马达，包括配流盘2、缸体3、壳体4、斜盘10和传动轴11，所述前端盖12与壳体4通过螺钉连接；所述后端盖1与壳体4通过螺栓连接；所述传动轴11通过花键驱动配流盘2和斜盘10转动，所述全外排压紧机构包括配流副外排压紧装置5和滑靴副外排压紧装置7。所述配流副外排压紧装置5包括自润滑导柱51、自润滑导套53、圆柱螺旋弹簧52；所述缸体3设有外圈凸台，并在凸台上开设导柱孔，所述自润滑导柱51安装在缸体3的导柱孔中；所述壳体4设有内圈凸台，并在凸台上开设导套孔和弹簧安装槽，所述自润滑导套53安装在壳体4的导套孔中，所述圆柱螺旋弹簧52安装在壳体4的弹簧安装槽中，并与缸体3的外圈凸台表面接触，通过压缩弹簧给凸台提供压力；所述缸体3与壳体4通过自润滑导柱、导套滑动配合。所述滑靴副外排压紧装置7包括底座71和万向滚珠弹簧柱塞72；所述斜盘10的斜面设有一周向外的凸台，所述斜盘10 的凸台上设有底座安装孔，所述底座71安装在相应的底座安装孔中；所述万向滚珠弹簧柱塞72安装在底座71上，其球头与压盘9表面接触，压缩弹簧，通过球头给压盘表面施加压力。
在本发明中，在一个具体的例子中，如图1所示，传动轴11与斜盘10和配流盘2通过花键连接，传动轴11驱动斜盘10和配流盘2转动；缸体3与壳体4通过自润滑导柱51和自润滑导套53滑动连接，缸体3处于浮动状态；圆柱螺旋弹簧52安装在壳体4的围绕轴线均匀对称分布的弹簧安装槽中，并与缸体3上的外圈凸台表面接触，对缸体3施加压力，使缸体3与配流盘2紧贴在一起，形成配流副；万向滚珠弹簧柱塞72安装在围绕斜盘10轴线均匀对称安装的底座71上，弹簧作用在压盘9表面，将压盘9压向斜盘10表面，使滑靴8与斜盘10紧密贴合形成滑靴副；滑靴副与配流副单独压紧，互不影响，且圆柱螺旋弹簧52和万向滚珠弹簧柱塞72中的弹簧始终处于压缩状态，无往复直线运功，降低了弹簧的疲劳损耗，圆柱螺旋弹簧52处于缸体3的外圈，万向滚珠弹簧柱塞72处于斜盘10凸台的外圈，弹簧力的力臂较大，有效的降低了弹簧的设计要求。
本发明以上实施例的工作方式如图1和2所示：当传动轴11驱动配流盘2和斜盘10顺时针转动时，图1中上面柱塞6开始吸油，下面柱塞6开始排油。吸油柱塞腔中的吸力将使柱塞6连同滑靴8脱离斜盘10，压盘9上的压紧力将使滑靴8压向斜盘10，使滑靴8压紧在斜盘10的表面。由图2可见，本发明实施例的滑靴副压紧部分压紧力的力臂A远大于现有技术中中心弹簧压紧力的力臂B,更有利 于滑靴8的平衡，防止滑靴8倾覆。同时，在配流副压紧部分，压紧力的力臂C接近于缸体3的最大外径，作用力臂大，更有利于缸体3的稳定，防止缸体3倾覆。
在本发明中，作为一个优选的实施例，如图1所示，自润滑导柱51与缸体3外圈凸台上的导柱安装孔过盈配合，且导柱安装孔围绕缸体3轴线均匀对称分布。自润滑导套53与壳体4内圈凸台上的导套安装孔过盈配合，且导套安装孔与相配合的导柱安装孔处于同一位置，数量相同。均匀对称安装配合的导柱、导套将会对缸体3实现精准定位，且导柱、导套的自润滑特性将不影响缸体3的浮动。以自润滑导柱、导套滑动配合方式实现缸体3与壳体4的连接，方便拆卸更换，避免了因连接部件损坏而整体更换缸体3或壳体4现象的产生，提升了轴向柱塞泵或马达的工作稳定性，大大降低了生产成本和装配难度。
在本发明中，作为一个优选的实施例，如图1和图5所示，弹簧安装槽与导套安装孔同轴心，圆柱螺旋弹簧52安装在弹簧安装槽中，作用在缸体3的凸台表面，圆柱螺旋弹簧52的轴线与自润滑导柱51的轴线相重合，弹簧力均匀的作用在以自润滑导柱51轴线为中心的区域内；多个均匀对称分布的圆柱螺旋弹簧52同时作用，将提供给缸体3持续稳定的压力。同时，自润滑导柱51也提供给圆柱螺旋弹簧52导向作用，使圆柱螺旋弹簧52始终沿着轴线方向作用，避免了弹簧的径向大波动。此压紧结构使轴向柱塞泵结构更加紧凑，缩小了泵的体积，节约了生产成本。
在本发明中，作为一个优选的实施例，如图1和图7所示，斜盘10的斜面端设有一周向外的凸台，且凸台表面与斜盘10的斜面平行，凸台上开设有围绕轴线均匀对称分布的底座安装孔，底座71与相应的底座安装孔螺纹连接。万向滚珠弹簧柱塞72安装在底座71上，通过其球头对压盘9施加压力，使滑靴8与斜盘10紧密贴合。底座71自斜盘10的凸台外表面直接安装，大大降低了装配难度，节约了加工时间。同时底座71作为一个可拆卸更换的常用零件，避免了和斜盘10的整体加工，降低了因底座71损坏而产生的加工成本。
在本发明中，作为一个可选的实施例，如图10所示的全外排压紧式多排轴向柱塞泵，此实施例中的斜盘具有多个交错平面，常用的压紧方式无法给滑靴副和配流副提供持续稳定的压力，且压紧装置结构复杂，稳定性不高。若采用本发明以上实施例的全外排压紧式轴向柱塞泵或马达结构，则可对滑靴副和配流副实现单独压紧，有效提高轴向柱塞泵或马达的运转可靠性，结构简单，易于装配。
在本发明中，作为一个可选的实施例，如图11所示的全外排压紧式轴向柱塞泵。与以上实施例的传动方式不同，该实施例以传动轴驱动缸体转动，来实现吸排油的过程，但全外排压紧机构依然适用。在缸体外圈凸台上均匀对称安装若干个底座，在底座上安装相应的万向滚珠弹簧柱塞，通过弹簧力的作用实现对配流副的单独压紧；滑靴副部分的压紧与上述实施例相同。以上实施例表明本发明的全外排压紧式轴向柱塞泵或马达的压紧机构对轴向柱塞泵或马达具有普遍适用性，市场前景广泛。
需要说明的是，在本文中，诸如第一和第二等之类的关系术语仅仅用来将一个实体或者操作与另一个实体或操作区分开来，而不一定要求或者暗示这些实体或操作之间存在任何这种实际的关系或者顺序。而且，术语“包括”、“包含”或者其任何其他变体意在涵盖非排他性的包含，从而使得包括一系列要素的过程、方法、物品或者设备不仅包括那些要素，而且还包括没有明确列出的其他要素，或者是还包括为这种过程、方法、物品或者设备所固有的要素。在没有更多限制的情况下，由语句“包括一个……”限定的要素，并不排除在包括所述要素的过程、方法、物品或者设备中还存在另外的相同要素。
以上实施方式仅用以说明本发明的技术方案，而非对其限制；尽管参照前述实施方式对本发明进行了详细的说明，本领域的普通技术人员应当理解：其依然可以对前述各实施方式所记载的技术方案进行修改，或者对其中部分技术特征进行等同替换；而这些修改或者替换，并不使相应技术方案的本质脱离本发明各实施方式技术方案的精神和范围。

Claims (10)

  1. 一种全外排压紧式轴向柱塞泵或马达，包括配流盘(2)、缸体(3)、壳体(4)、斜盘(10)和传动轴(11)，其特征在于：所述前端盖(12)与壳体(4)通过螺钉连接；所述后端盖(1)与壳体(4)通过螺栓连接；所述传动轴(11)通过花键驱动配流盘(2)和斜盘(10)转动，所述全外排压紧机构包括配流副外排压紧装置(5)和滑靴副外排压紧装置(7)。
  2. 根据权利要求1所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述配流副外排压紧装置(5)包括自润滑导柱(51)、自润滑导套(53)、圆柱螺旋弹簧(52)；所述缸体(3)设有外圈凸台，并在凸台上开设导柱孔，所述自润滑导柱(51)安装在缸体(3)的导柱孔中；所述壳体(4)设有内圈凸台，并在凸台上开设导套孔和弹簧安装槽，所述自润滑导套(53)安装在壳体(4)的导套孔中，所述圆柱螺旋弹簧(52)安装在壳体(4)的弹簧安装槽中，并与缸体(3)的外圈凸台表面接触，通过压缩弹簧给凸台提供压力；所述缸体(3)与壳体(4)通过自润滑导柱、导套滑动配合。
  3. 根据权利要求1所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述滑靴副外排压紧装置(7)包括底座(71)和万向滚珠弹簧柱塞(72)；所述斜盘(10)的斜面设有一周向外的凸台，所述斜盘(10)的凸台上设有底座安装孔，所述底座(71)安装在相应的底座安装孔中；所述万向滚珠弹簧柱塞(72)安装在底座(71)上，其球头与压盘(9)表面接触，压缩弹簧，通过球头给压盘表面施加压力。
  4. 根据权利要求2所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述缸体(3)外圈凸台上开设若干个围绕轴线均匀对称分布的导柱安装孔。
  5. 根据权利要求2或4所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述壳体(4)上的导套安装孔与缸体(3)导柱安装孔中心位置一致，且数量相同。
  6. 根据权利要求2或5所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述壳体(4)上的弹簧安装槽与导套安装孔同轴心。
  7. 根据权利要求3所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述斜盘(10)的斜面端设有一周向外的凸台，且凸台表面与斜盘表面平行。
  8. 根据权利要求3或7所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述斜盘(10)凸台上设置若干个围绕轴线均匀对称分布的底座安装孔。
  9. 根据权利要求3或8所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述底座(71)的表面加工外螺纹，并与底座安装孔螺纹连接。
  10. 根据权利要求3或9所述的一种全外排压紧式轴向柱塞泵或马达，其特征在于：所述底座(71)的前端开设盲孔，并加工内螺纹，万向滚珠弹簧柱塞(72)表面加工有外螺纹，并与底座(71)螺纹连接。
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