WO2017015782A1 - 一种新型轴向柱塞泵 - Google Patents

一种新型轴向柱塞泵 Download PDF

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Publication number
WO2017015782A1
WO2017015782A1 PCT/CN2015/084987 CN2015084987W WO2017015782A1 WO 2017015782 A1 WO2017015782 A1 WO 2017015782A1 CN 2015084987 W CN2015084987 W CN 2015084987W WO 2017015782 A1 WO2017015782 A1 WO 2017015782A1
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WIPO (PCT)
Prior art keywords
plunger
wobble plate
hole
piston pump
sliding shoe
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PCT/CN2015/084987
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English (en)
French (fr)
Inventor
岳艺明
徐兵
李莹
黎贻晨
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杭州绿聚科技有限公司
岳艺明
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Application filed by 杭州绿聚科技有限公司, 岳艺明 filed Critical 杭州绿聚科技有限公司
Priority to PCT/CN2015/084987 priority Critical patent/WO2017015782A1/zh
Publication of WO2017015782A1 publication Critical patent/WO2017015782A1/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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections

Definitions

  • This invention relates to the field of hydraulic pumps and, more particularly, to a novel axial piston pump.
  • the pump is the power component and core component of the pressure system, so it has important significance for its design and research.
  • the structure of the pump mainly includes plunger type, vane type, gear type, vane type and gear type pump have poor sealing effect, low volumetric efficiency, and serious leakage under the condition of increased working pressure.
  • the three pairs of key friction pairs of the common plunger pump structure include the plunger and the cylinder hole, the sliding shoe and the swash plate, the distribution plate and the end face of the cylinder, all of which are in surface contact, so the sealing effect is relatively good, and the pressure is relatively high and the viscosity is low.
  • the medium volume can guarantee a relatively high volumetric efficiency, and the friction pair has a relatively low PV value relative to the vane and gear pumps. Therefore, most of the existing pumps employ a plunger type structure.
  • the plunger type pump can be divided into an axial piston type structure and a radial plunger type according to the arrangement of the plungers.
  • the radial type plunger pump has a large specific power and is limited by the circumferential arrangement space, and is only used for low speed and large torque.
  • the axial piston type pump reduces the wear and power loss of the friction pair.
  • the axial piston pump operates by utilizing a change in volume produced by the plunger reciprocating in parallel within the cylinder bore of the cylinder.
  • the driving spindle drives the cylinder to rotate.
  • the plunger sliding in the cylinder bore performs a reciprocating motion under the action of the swash plate to realize one oil absorption and oil pressure.
  • the swashplate abuts and pushes the plunger assembly, which pushes the high pressure oil out of the plunger. Since the swash plate presses the plunger assembly at an angle, the radial pressure of the plunger and the cylinder is large.
  • radial pressure directly affects The rated pressure, life and efficiency of the pump, but when the plunger is in the suction stroke, the pressure in the plunger chamber is negative pressure, which is not enough for the plunger to extend, and the plunger cannot automatically return, resulting in the self-priming capability of the axial piston pump. Poor, even in severe cases, it may cause strong cavitation cavitation, resulting in large flow, pressure pulsation, hydraulic shock and noise, resulting in severe friction and wear of the axial piston pump distribution pair, plunger pair and sliding shoe pair. Greatly reduce the service life of the axial piston pump.
  • the return mechanism of the plunger pump mainly consists of the return stroke return stroke and the return spring return stroke. According to its working principle, it can be divided into fixed clearance return and floating clearance return, but it is inevitable that there will be friction between the return disc and the sliding shoe.
  • the problem is that in order to solve the problem of backlash friction of the plunger, the following methods are usually used: (1) The auxiliary pump is supplied with oil return. The plunger protrudes outward under the auxiliary pump's charge pressure. At this time, the axial piston pump has no self-priming capability, and an additional charge pump is required in the hydraulic system, which increases the system cost. (2) A spring is mounted in each of the plunger chambers, and the plunger is pressed against the swash plate by the spring force.
  • the sliding shoe pair needs to withstand high-frequency alternating tensile and compressive stress, and the phenomenon that the sliding shoe pair is loose, pulled off or even broken occurs sometimes, and the sliding shoe pieces are pulled off. It will cause instantaneous failure of the plunger pump, which will seriously affect the safe and stable operation of the entire hydraulic system.
  • the patent document with the application number CN201310171205.1 discloses an axial piston pump returning mechanism, the plunger of which is stepped, and the wall of the cylinder body is provided with a step along the axial direction of the cylinder body.
  • a cylinder bore, the stepped cylinder bores are spaced along the circumferential direction of the cylinder, the plunger is placed in the stepped cylinder bore, and the large diameter section of the plunger is matched with the large diameter section of the stepped cylinder bore, and the plunger is small
  • the diameter section is matched with the small diameter section of the stepped cylinder bore; when the plunger reciprocates in the stepped cylinder bore, a gap is formed between the end surface of the small diameter section of the plunger and the bottom surface of the small diameter section of the stepped cylinder bore
  • An oil chamber, an annular wall is formed between the outer wall surface of the small diameter section of the plunger and the inner wall surface of the large diameter section of the stepped cylinder bore, and each of the oil chambers corresponds to
  • a first oil passage is disposed at intervals on the wall of the cylinder, and each of the oil chambers is in communication with an annular region through a first oil passage, and a liquid resistance is disposed in each of the first oil passages;
  • the annular regions are in communication with each other.
  • the structural strength of the stepped plunger is reduced compared with the original plunger, and the plunger pump may cause the column when it is running.
  • the cylinder still needs to rotate, which brings certain pressure pulsation, hydraulic shock and noise to the hydraulic system, which affects the safe operation of the entire hydraulic system.
  • a novel axial piston pump including an end cover, a front housing, a pump shaft disposed in the front housing, a rear housing, and an oblique mounting in the rear housing a disc and a cylinder, the end cap, the front casing, the rear casing and the cylinder are sequentially fixed Connecting, the pump shaft is connected to the swash plate at one end of the housing, and the plunger pump is further provided with a swash plate and a plunger assembly, and the cylinder body is provided with a plunger hole, a valve hole and an extrusion valve group.
  • the pressing valve group and the pressing valve group are located in the valve hole, one end of the plunger assembly is embedded in the plunger hole, and the other end of the plunger assembly is connected to the oscillating disc, the oscillating disc and the swash plate Conflicting setting;
  • the oscillating disc includes an inner wobble plate and an outer wobble plate, and the inner wobble plate is rotatably connected to the outer wobble plate by an inner wobble plate fixing sleeve, and the outer wobble plate is rotatably connected to the rear casing through an outer wobble plate fixing sleeve.
  • the inner wobble plate is provided with a sliding shoe hole for inserting a sliding shoe, and the sliding shoe is connected with the plunger assembly, and the sliding shoe can reciprocate axially along the cross wobble plate.
  • the present invention is further configured to: a sliding shoe disc is embedded on the inner wobble plate, and the sliding shoe hole is located on the sliding shoe plate, and the sliding shoe is embedded in the sliding shoe plate through the sliding shoe hole.
  • the present invention is further configured to: the plunger assembly includes a plunger and a plunger seat, the plunger seat is in sliding connection with the plunger hole, and both ends of the plunger are integrally provided with a plunger ball head,
  • the shoe covers the plunger head of the plunger adjacent to the side of the cross wobble plate, and the plunger seat covers the plunger ball head of the plunger away from the side of the cross wobble plate.
  • the shoe comprises a front shoe and a rear shoe, the front shoe and the rear shoe covering the plunger ball head and constituting a ball joint structure.
  • the invention is further provided that the inner wobble plate and the outer wobble plate are each connected with a rotating shaft, and the rotating shaft is respectively embedded in the outer wobble plate fixing sleeve and the inner wobble plate fixing sleeve.
  • the present invention is further configured such that the inner wobble wheel rotation axis and the outer wobble plate rotation axis axis are perpendicular to each other.
  • the invention is further configured such that the pump shaft is mounted with a bearing assembly including a tapered roller bearing, a bushing, and an angular contact ball bearing that are sequentially connected.
  • the present invention is further configured such that the suction valve block includes a plurality of axially placed suction check valves that are embedded in the cylinder valve bore.
  • the invention is further configured such that the extrusion valve block includes a plurality of radially disposed extrusion check valves, the extrusion check valves being embedded in the cylinder valve bore.
  • the present invention is further configured to: the cylinder body includes a liquid inlet port and a liquid discharge port, the valve hole is in communication with the plunger hole, the suction valve group is located in the valve hole near the liquid inlet, and the pressure valve group is located in the valve hole Set inside the drain port.
  • the swash plate is connected to the plunger assembly through the swash plate, and the two ends of the plunger have a spherical structure, and the force is a two-force state, which greatly reduces the radial force of the plunger hole, thereby Reduced friction loss, can greatly improve the working pressure of the axial piston pump, improve the service life, improve efficiency, reduce material requirements, and broaden the range of material selection.
  • it is beneficial to increase the swing angle of the swash plate and the increase of the swing angle of the swash plate is beneficial to increase the return distance of the plunger seat, thereby increasing the displacement of the plunger pump.
  • the sliding shoe of the present invention integrates the returning disc of the prior art with the sliding shoe, the sliding shoe and the plunger ball head.
  • there are always some plungers in the oil pressing stroke thereby pressing the sliding shoe plate in the oblique direction.
  • the plunger in the liquid suction stroke is returned by the integral sliding shoe disc, and the rear sliding shoe assembles the plunger in the sliding shoe disc, thereby improving the looseness, pulling off and even chipping of the spherical surface of the plunger sliding shoe;
  • the return mode of the invention does not need the assistance of the spring, avoids the phenomenon that the spring plunger pump life is reduced due to the high-frequency alternating stress of the spring, and effectively overcomes the lateral force effect of the cylinder body, especially for The axial piston pump simplifies the structural design without the need for other return mechanisms.
  • the oscillating disc can be rotated and connected by the inner wobble plate and the outer wobble plate through the fixed sleeve and the rotating shaft, the structure is reliable, the processing is convenient, the material requirements are reduced, the range of material selection is widened, and the design of the friction pair of the matching plunger assembly is optimized and simplified. System structure reduces system cost.
  • the overall sliding shoe structure can realize the overall dynamic and static pressure support of the sliding shoe, reduce the specific pressure, increase the design space, improve the single-side wear phenomenon of the single sliding shoe, and improve the stability.
  • the valve distribution structure is adopted to reduce the key friction pairs of a pair of axial piston pumps, the corresponding leakage amount is reduced, the volumetric efficiency is improved, and the working pressure of the pump is improved.
  • the valve body has a built-in embedded structure, and the suction valve group and the pressure valve group are embedded in the cylinder body, which has better sealing performance and response speed, and has the characteristics of small impact and low noise, and can achieve high volumetric efficiency.
  • a tapered roller bearing and an angular contact ball bearing are used to form a bearing set, which effectively bears the axial force and the radial force acting on the swash plate.
  • the rigidity of the swash plate is increased, and the overall working life of the pump is improved.
  • FIG. 1 is a schematic cross-sectional view showing a novel axial piston pump according to an embodiment of the present invention
  • FIG. 2 is a cross-sectional view showing a novel axial piston pump according to an embodiment of the present invention
  • FIG. 3 is a cross-sectional view showing a novel axial piston pump oscillating disc according to an embodiment of the present invention
  • FIG. 4 is a side view of a novel axial piston pump according to an embodiment of the present invention.
  • Figure 5 is a cross-sectional view showing a novel axial piston pump oscillating disc according to an embodiment of the present invention.
  • a novel axial piston pump includes an end cap 15, a front housing, a pump shaft 10 disposed in the front housing 9, a rear housing 4, a swash plate 17 mounted in the rear housing 4, and a cylinder block 8.
  • the end cover 15, the front housing 9, the rear housing 4 and the cylinder 8 are sequentially and fixedly connected.
  • the pump shaft 10 is connected to the swash plate 17 at one end of the housing, and the swash plate and the pump body are integrally arranged.
  • the rear housing 4 is further provided with a swash plate 18 and a plunger assembly 13 .
  • the cylinder 8 is provided with a plunger hole, a valve hole, an extrusion valve group 12 and a press-in valve group, and the pressure valve group 12 is extruded.
  • the press-in valve group is located in the valve hole, one end of the plunger assembly 13 is embedded in the plunger hole, and the other end of the plunger assembly 13 is connected to the oscillating disc 18, and the symmetry dial 18 and the swash plate 17 are in conflict with each other.
  • an oil film layer is formed between the oscillating disc 18 and the swash plate 17;
  • the oscillating disc 18 comprises an inner wobble plate 2 and an outer wobble plate 1.
  • the inner wobble plate 2 is rotatably connected to the outer wobble plate 1 by an inner wobble plate fixing sleeve 3, and the outer wobble plate 1 is rotatably connected to the rear case by an outer wobble plate fixing sleeve 5.
  • the body 4 has a sliding shoe hole for inserting a sliding shoe, and the sliding shoe hole is evenly distributed on the inner wobble plate 2, the number is nine, the sliding shoe, the sliding shoe hole, the plunger assembly 13 and the column
  • the plug holes are arranged in one-to-one correspondence, and the sliding shoe is connected to the plunger assembly 13, and the sliding shoe can reciprocate axially along the traverse disk 18.
  • the inner swinging disc 2 is embedded with a sliding shoe 27, a sliding shoe
  • the holes are located in the shoe tray 27 and the shoes are embedded in the shoe holes.
  • the inner wobble plate 2 and the outer wobble plate 1 are each connected with a rotating shaft 19 which is respectively embedded in the outer wobble plate fixing sleeve 5 and the inner wobble plate fixing sleeve 3.
  • the axis projections of the inner wobble plate rotating shaft 19 and the outer wobble plate rotating shaft 19 are perpendicular to each other. Two rotating shafts 19 are disposed on the inner wobble plate 2 and the outer wobble plate 1.
  • the two rotating shafts 19 on the inner wobble plate 2 are coaxially arranged, and the two rotating shafts 19 on the outer wobble plate 1 are coaxially arranged, and the outer wobble plate 1 is disposed.
  • the inner wobble plate fixing sleeve 5 is pivoted about the vertical axis by the rotating shaft 19; the inner wobble plate fixing sleeve 3 is screwed onto the outer wobble plate 1, and the inner wobble plate 2 is fixed to the inner sleeve by the rotating shaft 19
  • the inner swing can be oscillated about the horizontal axis, and can also oscillate around the vertical axis with the outer wobble plate 1.
  • the plunger assembly 13 includes a plunger 132 and a plunger seat 131.
  • the plunger seat 131 is in sliding connection with the plunger hole.
  • the plunger 132 is integrally provided with a plunger ball head 133 at both ends thereof, and the sliding shoe covers the plunger 132.
  • a plunger ball head 133 on one side of the traverse plate, the plunger seat 131 covers the plunger ball 133 of the plunger 132 away from the side of the oscillating disc and constitutes a ball joint structure.
  • the shoe includes a front shoe 6 and a rear shoe 7, and the front shoe 6 and the rear shoe 7 enclose the plunger ball head 133 and constitute a ball joint structure.
  • the arrangement of the front sliding shoe 6 and the rear sliding shoe 7 facilitates the processing of the plunger ball head 133 to be coated, and the bearing shaft 14 is mounted on the pump shaft 10, and the bearing assembly 14 includes cones connected in sequence.
  • the roller bearing 143, the boss 142, and the angular contact ball bearing 141 are directly connected to the cylinder block 8 and are integrally provided with the cylinder block 8.
  • the thrust of the swash plate 17 acts on the tapered roller bearing 143, is transmitted to the angular contact ball bearing 141 through the sleeve 142, and is finally pressed by the end cover 15, which is also embedded with a seal for sealing oil and dust. Enter the seal ring 16.
  • the suction valve block 11 includes a plurality of axially placed suction check valves.
  • the cylinder block 8 further includes a liquid supply 20, the valve holes are located on the liquid supply 20, and the suction check valves are embedded in the valve holes.
  • Extrusion valve Group 12 includes a plurality of radially placed extrusion check valves that are embedded in the valve bore.
  • the cylinder block 8 includes a liquid inlet port and a liquid discharge port, the valve hole is in communication with the plunger hole, the liquid inlet port and the liquid discharge port are in communication with the valve hole, and the suction valve block 11 is located in the valve hole near the liquid inlet port, and is pressed out.
  • the valve block 12 is located in the valve bore adjacent to the drain port.
  • a spline hole is formed in the center of the swash plate 17, and the swash plate 17 is coupled to the pump shaft 10 through a spline hole and a spline.
  • the swash plate 17 is connected to the plunger assembly 13 through the swash plate 18, and the plunger 132 has a spherical structure at both ends, and the force is a two-force state, which greatly reduces the radial direction of the plunger hole.
  • the force is reduced, thereby reducing the friction loss, which can greatly increase the working pressure of the axial piston pump, improve the service life, improve the efficiency, reduce the material requirements, and broaden the range of material selection.
  • the shoe tray 27 of the present invention integrates the returning disc of the prior art with the shoe, the shoe and the plunger ball head.
  • there are always some plungers 132 in the oil pressure stroke thereby pressing the shoe plate 27 Tightly on the swash plate 17, the plunger 132 in the liquid suction stroke is returned by the integral sliding shoe 27, and the rear shoe 7 fits the plunger 132 in the sliding shoe 27, improving the looseness, pulling and even breaking of the spherical pair.
  • the return mode of the present invention does not require the aid of a spring, avoids the phenomenon that the axial piston pump life is reduced due to the high-frequency alternating stress of the spring, and effectively overcomes the lateral direction of the cylinder 8.
  • the force, especially for axial piston pumps eliminates the need for other return mechanisms and simplifies the structural design.
  • the mechanical structure of the swash plate 18 improves the force of the plunger 132 and the cylinder 8 and has a return function.
  • the oscillating disc 18 is rotated and connected by the inner wobble plate 2 and the outer wobble plate 1 through a fixed sleeve and a rotating shaft. Reliable, easy to process, reduce material requirements, broaden selection The material range is beneficial to optimize the matching design of the matching plunger assembly 13 to simplify the system structure and reduce the system cost.
  • the overall structure of the sliding shoe 27 can realize the overall dynamic and static pressure support of the sliding shoe, reduce the specific pressure, increase the design space, improve the single-side wear phenomenon of the single sliding shoe, and improve the stability.
  • the valve distribution structure is adopted to reduce the key friction pairs of a pair of axial piston pumps, the corresponding leakage amount is reduced, the volumetric efficiency is improved, and the working pressure of the pump is improved.
  • the valve body has a built-in embedded structure, and the suction valve group and the pressure-out valve group are embedded in the cylinder block 8, which has good sealing performance and response speed, and has the characteristics of small impact and low noise, and can achieve a high volume. effectiveness.
  • the tapered swash plate bearing 143 and the angular contact ball bearing 141 are used in front of the rotary swash plate 17 to form a bearing set, which effectively bears the axial force and the radial force acting on the swash plate 17.
  • the rigidity of the swash plate 17 is increased, and the overall working life of the pump is improved.
  • each plunger assembly 13 absorbs and presses the liquid once. As the pump shaft 10 rotates continuously, each plunger assembly 13 continuously and independently performs the action of sucking and pressing liquid. So that the plunger pump works properly.
  • the return disk As a traverse disk 18 returning, it is divided into an inner wobble plate 2 and an outer wobble plate 1, and the outer wobble plate 1 is inlaid and fixed to the plunger pump rear casing 4 through the outer wobble plate fixing sleeve 5.
  • the swinging of the outer wobble plate 1 about the central axis of the wobble plate is realized, and the inner wobble plate 2 is inlaid and fixed to the outer wobble plate 1 by the inner wobble plate fixing sleeve 3, so that the inner wobble plate 2 swings around the central axis of the wobble plate.
  • the return of the plunger 131 is achieved.

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

Abstract

一种轴向柱塞泵，包括端盖（15）、前壳体（9）、设置在前壳体（9）内的泵轴（10）、后壳体（4）、安装在后壳体（4）内的斜盘（17）和缸体（8），所述端盖（15）、前壳体（9）、后壳体（4）和缸体（8）顺次固定连接，所述泵轴（10）背对壳体一端连接斜盘（17），所述柱塞泵内还设有十字摆盘（18）和柱塞组件（13），所述缸体（8）内设有柱塞孔、阀孔、压出阀组（12）和压入阀组，压出阀组（12）和压入阀组位于阀孔内，柱塞组件（13）一端嵌设于柱塞孔内，柱塞组件（13）另一端连接十字摆盘。所述柱塞泵通过设置滑靴盘将现有技术中的回程盘和滑靴、滑靴和柱塞球头镶嵌为一体，减小了缸体和柱塞座的侧向力，同时有利于增大斜盘的摆角，有利于增大柱塞座的回程距离，加大柱塞泵的排量，提高了柱塞泵的效率，进一步简化了缸体设计。

Description

一种新型轴向柱塞泵 技术领域
本发明涉及液压泵领域，更具体地说，它涉及一种新型轴向柱塞泵。
背景技术
泵是压力系统的动力元件和核心元件，因此对其设计和研究有及其重要的意义。泵的结构形式主要包括柱塞式、叶片式、齿轮式，叶片式和齿轮式泵的密封效果差，容积效率低，在工作压力提高的情况下泄漏严重。常用柱塞泵结构的三对关键摩擦副包括柱塞与缸孔、滑靴与斜盘、配流盘与缸体端面，都是面接触，因此密封效果相对较好，在压力比较高和低粘度介质的工况下可以保证比较高的容积效率，并且相对于叶片式和齿轮式泵，摩擦副有比较低的PV值。因此，现有的泵大多采用了柱塞式的结构。
柱塞式结构的泵按照柱塞的布置方式可以分为轴向柱塞式结构和径向柱塞式结构。径向型柱塞泵的比功率大，且受周向布置空间的限制，仅用于低速大转矩的场合；轴向柱塞式结构的泵减小了摩擦副的磨损和功率损失因此大部分柱塞泵采用轴向柱塞式结构。
轴向柱塞泵是利用柱塞在缸体的缸体孔内平行往复运动产生的容积变化进行工作的。工作时，驱动主轴驱动缸体旋转，在缸体旋转一周的过程中，滑动于缸体孔内的柱塞在斜盘的作用下做一次往复运动，实现一次吸油和压油。柱塞处于压油行程时，斜盘紧贴并推动柱塞组件，柱塞组件将柱塞内的高压油顶出。由于斜盘以一定角度挤压柱塞组件，导致柱塞与缸体径向压力较大。径向压力的数值直接影响 泵的额定压力、寿命和效率，但当柱塞处于吸油行程时，柱塞腔内压力为负压，不足以使柱塞伸出，柱塞不能自动回程，导致轴向柱塞泵自吸能力差，严重时甚至会引起强烈的空化气蚀现象，产生较大的流量、压力脉动、液压冲击和噪声，导致轴向柱塞泵配流副，柱塞副和滑靴副的严重摩擦磨损，大大降低轴向柱塞泵的使用寿命。
目前柱塞泵的回程机构主要由回程盘回程、回程弹簧回程，按照其工作原理又可分为定间隙回程、浮动间隙回程等，但是均不可避免的会存在回程盘与滑靴之间相互摩擦的问题，为解决柱塞的回程摩擦问题，通常会采用以下方法：(1)辅助泵供油回程。柱塞在辅助泵补油压力作用下向外伸出，此时，轴向柱塞泵无自吸能力，而且需在液压系统中额外增加补油泵，增加了系统成本。(2)在每个柱塞腔内安装弹簧，利用弹簧推力将柱塞压紧在斜盘上。此时弹簧承受交变应力，存在严重的疲劳问题，极大地缩短轴向柱塞泵的使用寿命。(3)采用中心弹簧压紧回程盘。由于受到轴向柱塞泵空间的限制，弹簧设计困难，只能提供部分柱塞回程力，无法完全解决柱塞回程问题。(4)滑靴夹在回程盘和斜盘之间并具有一定的间隙，回程盘和斜盘固定连接，即机械强制回程。这种结构较为复杂，使斜盘尺寸加大，此外，滑靴副需要承受高频交变拉压应力，滑靴副松动、拉脱甚至碎裂的现象时有发生，拉脱的滑靴碎片会造成柱塞泵瞬时失效，严重影响整个液压系统的安全稳定运行。
市场上申请号为CN201310171205.1的专利文件公开了一种轴向柱塞泵回程机构，其柱塞呈阶梯状，缸体的壁上沿缸体轴向设有阶梯 状缸孔，该阶梯状缸孔沿缸体的周向间隔分布，柱塞置于阶梯状缸孔内，柱塞的大直径段与阶梯状缸孔的大直径段间隙配合，柱塞的小直径段与阶梯状缸孔的小直径段间隙配合；柱塞在阶梯状缸孔内往复移动时，柱塞的小直径段的端面与阶梯状缸孔的小直径段的底面之间始终形成一个油腔，柱塞的小直径段的外壁面与阶梯状缸孔的大直径段的内壁面之间始终形成一个环形区域，每个所述油腔一一对应地与缸体的一个腰形槽连通；缸体的壁上间隔地开设有第一油道，每个所述油腔一一对应地通过一个第一油道与一个环形区域连通，每个第一油道内设有液阻；各环形区域相互连通。该技术方案通过阶梯状柱塞和柱塞孔的设置来用于改善现有技术中的回程问题，但是呈阶梯状柱塞和柱塞孔加工需要保证同轴度，其难度较大，且对于柱塞泵内的两者配合需要较高的精度等级，进一步加大了加工难度，其次阶梯状柱塞与原先的柱塞相比其结构强度被降低了，柱塞泵运行时可能会引起柱塞断裂的状况，在该技术方案中其缸体依然需要转动，给液压系统带来了一定的压力脉动、液压冲击和噪声，影响整个液压系统的安全运行。
发明内容
针对现有技术存在的不足，本发明的目的在于提供一种摩擦损失较小、效率较高的新型柱塞泵。
为实现上述目的，本发明提供了如下技术方案：一种新型轴向柱塞泵，包括端盖、前壳体、设置在前壳体内的泵轴、后壳体、安装在后壳体内的斜盘和缸体，所述端盖、前壳体、后壳体和缸体顺次固定 连接，所述泵轴背对壳体一端连接斜盘，所述柱塞泵内还设有十字摆盘和柱塞组件，所述缸体内设有柱塞孔、阀孔、压出阀组和压入阀组，压出阀组和压入阀组位于阀孔内，柱塞组件一端嵌设于柱塞孔内，柱塞组件另一端连接十字摆盘，所述十字摆盘与斜盘呈抵触设置；
所述十字摆盘包括内摆盘和外摆盘，所述内摆盘通过内摆盘固定套筒转动连接外摆盘，所述外摆盘通过外摆盘固定套筒转动连接后壳体，所述内摆盘上开设有用于嵌设滑靴的滑靴孔，所述滑靴连接柱塞组件，滑靴能够沿十字摆盘轴向往复运动。
本发明进一步设置为：所述内摆盘上嵌设有滑靴盘，滑靴孔位于滑靴盘上，所述滑靴通过滑靴孔嵌设于滑靴盘内。
本发明进一步设置为：所述柱塞组件包括柱塞和柱塞座，所述柱塞座与柱塞孔嵌设滑动连接，所述柱塞两端均一体设置有柱塞球头，所述滑靴包覆柱塞靠近十字摆盘一侧的柱塞球头，所述柱塞座包覆柱塞远离十字摆盘一侧的柱塞球头。
本发明进一步设置为：所述滑靴包括前滑靴和后滑靴，所述前滑靴和后滑靴包覆柱塞球头且构成球铰结构。
本发明进一步设置为：所述内摆盘和外摆盘均连接有转动轴，所述转动轴分别嵌设于外摆盘固定套筒和内摆盘固定套筒。
本发明进一步设置为：所述内摆盘转动轴和外摆盘转动轴轴线投影相互垂直。
本发明进一步设置为：所述泵轴上安装有轴承组件，所述轴承组件包括依次相连的圆锥滚子轴承、轴套、角接触球轴承。
本发明进一步设置为：所述吸入阀组包括若干个轴向放置的吸入单向阀，所述吸入单向阀内嵌于缸体阀孔。
本发明进一步设置为：所述压出阀组包括若干个径向放置的压出单向阀，所述压出单向阀内嵌于缸体阀孔。
本发明进一步设置为：所述缸体包括进液口和排液口，所述阀孔与柱塞孔相连通，吸入阀组位于阀孔内靠近进液口设置，压出阀组位于阀孔内靠近排液口设置。
通过采用上述技术方案，斜盘通过十字摆盘与柱塞组件连接，柱塞两端均有球形结构，受力为二力杆状态，极大地减小了柱塞孔的径向受力，从而减少了摩擦损失，可以大幅提高轴向柱塞泵的工作压力，提高使用寿命，提高效率，降低了材料要求，拓宽了材料选择的范围。同时有利于增大斜盘的摆角，斜盘摆角的增大有利于增大柱塞座的回程距离，从而加大柱塞泵的排量。
本发明的滑靴盘将现有技术中的回程盘和滑靴、滑靴和柱塞球头镶嵌为一体，运行中总有一些柱塞处于压油行程，从而将滑靴盘压紧在斜盘上，通过整体滑靴盘使处于吸液行程的柱塞回程，后滑靴将柱塞装配在滑靴盘中，改善了柱塞滑靴球面副松动、拉脱甚至碎裂的现象；此外，本发明回程方式不需弹簧的辅助，避免了因弹簧承受高频交变应力而使轴向柱塞泵寿命下降的现象，并且有效克服了缸体所受的侧向力作用，尤其是针对轴向柱塞泵，不需其他回程机构，简化了结构设计。
通过十字摆盘机械结构改善了柱塞及缸体受力，同时具有回程功 能，十字摆盘由内摆盘和外摆盘通过固定套筒和转动轴实现转动连接，结构可靠，便于加工，降低材料要求，拓宽选材范围，有利于优化匹配柱塞组件摩擦副设计，简化系统结构，降低系统成本。
整体的滑靴盘结构可以实现滑靴的整体动静压支撑，降低比压，设计的空间增加，改善单个滑靴的单边磨损现象，提高稳定性。
采用阀配流结构形式，减小一对轴向柱塞泵关键的摩擦副，相应的泄漏量减小，容积效率提高，泵的工作压力提高。配流阀体内置嵌入式结构，吸入阀组和压出阀组内嵌于缸体上，具有较好的密封性能和响应速度，而且具有冲击小、噪音低等特点，可以达到较高的容积效率。旋转式斜盘前采用圆锥滚子轴承和角接触球轴承构成轴承组，有效的承担了作用在斜盘上的轴向力和径向力。增加了斜盘的刚度，提高了泵整体的工作寿命。
附图说明
图1为本发明实施例一种新型轴向柱塞泵的剖面示意图；
图2为本发明实施例一种新型轴向柱塞泵的剖面图；
图3为本发明实施例一种新型轴向柱塞泵十字摆盘的剖面示意图；
图4为本发明实施例一种新型轴向柱塞泵的侧面示意图；
图5为本发明实施例一种新型轴向柱塞泵十字摆盘的剖面图。
附图标记：1、外摆盘；2、内摆盘；3、内摆盘固定套筒；4、后壳体；5、外摆盘固定套筒；6、前滑靴；7、后滑靴；8、缸体；9、前壳体；10、泵轴；11、吸入阀组；12、压出阀组；13、柱塞组件； 131、柱塞座；132、柱塞；133、柱塞球头；14、轴承组件；141、角接触球轴承；142、轴套；143、圆锥滚子轴承；15、端盖；16、密封圈；17、斜盘；18、十字摆盘；19、转动轴；20、配液体；21、油封；22、水封；23、支架；24、挡圈；25、垫片；26、连接块；27、滑靴盘。
具体实施方式
参照图1至图5对本发明实施例做进一步说明。
一种新型轴向柱塞泵，包括端盖15、前壳体、设置在前壳体9内的泵轴10、后壳体4、安装在后壳体4内的斜盘17和缸体8，所述端盖15、前壳体9、后壳体4和缸体8顺次固定连接，所述泵轴10背对壳体一端连接斜盘17，斜盘和泵轴遗体一体设置，所述后壳体4内还设有十字摆盘18和柱塞组件13，所述缸体8内设有柱塞孔、阀孔、压出阀组12和压入阀组，压出阀组12和压入阀组位于阀孔内，柱塞组件13一端嵌设于柱塞孔内，柱塞组件13另一端连接十字摆盘18，所述十字摆盘18与斜盘17呈抵触设置，在柱塞泵运行时，十字摆盘18与斜盘17之间形成油膜层；
十字摆盘18包括内摆盘2和外摆盘1，内摆盘2通过内摆盘固定套筒3转动连接外摆盘1，外摆盘1通过外摆盘固定套筒5转动连接后壳体4，内摆盘2上开设有用于嵌设滑靴的滑靴孔，滑靴孔均匀分布于内摆盘2上，数量为9个，滑靴、滑靴孔、柱塞组件13和柱塞孔均呈一一对应设置，滑靴连接柱塞组件13，滑靴能够沿十字摆盘18轴向往复运动。优选方案为内摆盘2上嵌设有滑靴盘27，滑靴 孔位于滑靴盘27内，滑靴嵌设于滑靴孔内。内摆盘2和外摆盘1均连接有转动轴19，转动轴19分别嵌设于外摆盘固定套筒5和内摆盘固定套筒3。内摆盘转动轴19和外摆盘转动轴19轴线投影相互垂直。内摆盘2和外摆盘1上均设置两个转动轴19，内摆盘2上两个转动轴19同轴设置，外摆盘1上两个转动轴19同轴设置，外摆盘1通过转动轴19在外摆盘固定套筒5内可绕竖直轴线摆动；内摆盘固定套筒3螺纹连接在外摆盘1上，内摆盘2通过转动轴19在内摆盘固定套筒3内可绕水平轴线摆动，又可随外摆盘1绕竖直轴线摆动。
柱塞组件13包括柱塞132和柱塞座131，柱塞座131与柱塞孔嵌设滑动连接，柱塞132两端均一体设置有柱塞球头133，滑靴包覆柱塞132靠近十字摆盘一侧的柱塞球头133，柱塞座131包覆柱塞132远离十字摆盘一侧的柱塞球头133且构成球铰结构。滑靴包括前滑靴6和后滑靴7，前滑靴6和后滑靴7包覆柱塞球头133且构成球铰结构。前滑靴6和后滑靴7的设置有利于柱塞球头133被包覆的加工工艺，方便其加工，所泵轴10上安装有轴承组件14，所述轴承组件14包括依次相连的圆锥滚子轴承143、轴套142、角接触球轴承141，轴套142直接连接在缸体8上且与缸体8一体设置。斜盘17的推力作用于圆锥滚子轴承143上，通过轴套142传递至角接触球轴承141，最终通过端盖15压紧，所述前端盖15内还镶嵌有用于密封油液和防止灰尘进入的密封圈16。
吸入阀组11包括若干个轴向放置的吸入单向阀，缸体8还包括配液体20，阀孔位于配液体20上，吸入单向阀内嵌于阀孔。压出阀 组12包括若干个径向放置的压出单向阀，压出单向阀内嵌于阀孔。缸体8包括进液口和排液口，阀孔与柱塞孔相连通，进液口和排液口与阀孔相连通，吸入阀组11位于阀孔内靠近进液口设置，压出阀组12位于阀孔内靠近排液口设置。斜盘17中心开设花键孔，所述斜盘17通过花键孔和花键与泵轴10连接。
通过采用上述技术方案，斜盘17通过十字摆盘18与柱塞组件13连接，柱塞132两端均有球形结构，受力为二力杆状态，极大地减小了柱塞孔的径向受力，从而减少了摩擦损失，可以大幅提高轴向柱塞泵的工作压力，提高使用寿命，提高效率，降低了材料要求，拓宽了材料选择的范围。同时有利于增大斜盘17的摆角，斜盘17摆角的增大有利于增大柱塞座的回程距离，从而加大柱塞泵的排量。
本发明的滑靴盘27将现有技术中的回程盘和滑靴、滑靴和柱塞球头镶嵌为一体，运行中总有一些柱塞132处于压油行程，从而将滑靴盘27压紧在斜盘17上，通过整体滑靴盘27使处于吸液行程的柱塞132回程，后滑靴7将柱塞132装配在滑靴盘27中，改善了球面副松动、拉脱甚至碎裂的现象；此外，本发明回程方式不需弹簧的辅助，避免了因弹簧承受高频交变应力而使轴向柱塞泵寿命下降的现象，并且有效克服了缸体8所受的侧向力作用，尤其是针对轴向柱塞泵，不需其他回程机构，简化了结构设计。
通过十字摆盘18机械结构改善了柱塞132及缸体8受力，同时具有回程功能，十字摆盘18由内摆盘2和外摆盘1通过固定套筒和转动轴实现转动连接，结构可靠，便于加工，降低材料要求，拓宽选 材范围，有利于优化匹配柱塞组件13摩擦付设计，简化系统结构，降低系统成本。
整体的滑靴盘27结构可以实现滑靴的整体动静压支撑，降低比压，设计的空间增加，改善单个滑靴的单边磨损现象，提高稳定性。
采用阀配流结构形式，减小一对轴向柱塞泵关键的摩擦副，相应的泄漏量减小，容积效率提高，泵的工作压力提高。配流阀体内置嵌入式结构，吸入阀组和压出阀组内嵌于缸体8上，具有较好的密封性能和响应速度，而且具有冲击小、噪音低等特点，可以达到较高的容积效率。旋转式斜盘17前采用圆锥滚子轴承143和角接触球轴承141构成轴承组，有效的承担了作用在斜盘17上的轴向力和径向力。增加了斜盘17的刚度，提高了泵整体的工作寿命。
本发明一种新型轴向柱塞泵的具体工作过程：当泵轴10带动斜盘17一同旋转时，通过回程十字摆盘18的摆动将作用力均匀施加到每个滑靴上，使柱塞132背对柱塞座131一端的柱塞球头133和滑靴发生沿十字摆盘18轴向的往复运动，同时柱塞座131受到旋转的斜盘17给滑靴、滑靴给柱塞的作用力，使柱塞座131在缸体8内的柱塞孔内作往复运动，缸体8则静止不动。
当泵轴10带动斜盘17旋转一周，每个柱塞组件13各吸液、压液一次，随着泵轴10的不断旋转，各柱塞组件13也连续地独立完成吸、压液的动作，从而使柱塞泵正常工作。
通过将回程盘设计成十字摆盘18回程，分为内摆盘2和外摆盘1，外摆盘1通过外摆盘固定套筒5镶嵌固定到柱塞泵后壳体4上， 实现外摆盘1绕摆盘中心轴线上下方向的摆动，内摆盘2通过内摆盘固定套筒3镶嵌固定到外摆盘1上，实现内摆盘2绕摆盘中心轴线左右方向的摆动，配合斜盘17的旋转运动，实现柱塞131回程。
以上所述仅是本发明的优选实施方式，本发明的保护范围并不仅局限于上述实施例，凡属于本发明思路下的技术方案均属于本发明的保护范围。应当指出，对于本技术领域的普通技术人员来说，在不脱离本发明原理前提下的若干改进和润饰，这些改进和润饰也应视为本发明的保护范围。

Claims (10)

  1. 一种新型轴向柱塞泵，包括端盖、前壳体、设置在前壳体内的泵轴、后壳体、安装在后壳体内的斜盘和缸体，所述端盖、前壳体、后壳体和缸体顺次固定连接，所述泵轴背对壳体一端连接斜盘，其特征在于，所述柱塞泵内还设有十字摆盘和柱塞组件，所述缸体内设有柱塞孔、阀孔、压出阀组和压入阀组，压出阀组和压入阀组位于阀孔内，柱塞组件一端嵌设于柱塞孔内，柱塞组件另一端连接十字摆盘，所述十字摆盘与斜盘呈抵触设置；
    所述十字摆盘包括内摆盘和外摆盘，所述内摆盘通过内摆盘固定套筒转动连接外摆盘，所述外摆盘通过外摆盘固定套筒转动连接后壳体，所述内摆盘上开设有用于嵌设滑靴的滑靴孔，所述滑靴连接柱塞组件，滑靴能够沿十字摆盘轴向往复运动。
  2. 根据权利要求1所述的一种新型轴向柱塞泵，其特征在于，所述内摆盘上嵌设有滑靴盘，滑靴孔位于滑靴盘上，所述滑靴通过滑靴孔嵌设于滑靴盘内。
  3. 根据权利要求2所述的一种新型轴向柱塞泵，其特征在于，所述柱塞组件包括柱塞和柱塞座，所述柱塞座与柱塞孔嵌设滑动连接，所述柱塞两端均一体设置有柱塞球头，所述滑靴包覆柱塞靠近十字摆盘一侧的柱塞球头，所述柱塞座包覆柱塞远离十字摆盘一侧的柱塞球头。
  4. 根据权利要求3所述的一种新型轴向柱塞泵，其特征在于，所述滑靴包括前滑靴和后滑靴，所述前滑靴和后滑靴包覆柱塞球头且构成球铰结构。
  5. 根据权利要求4所述的一种新型轴向柱塞泵，其特征在于，所述内摆盘和外摆盘均连接有转动轴，所述转动轴分别嵌设于外摆盘固定套筒和内摆盘固定套筒。
  6. 根据权利要求5所述的一种新型轴向柱塞泵，其特征在于，所述内摆盘转动轴和外摆盘转动轴轴线投影相互垂直。
  7. 根据权利要求1所述的一种新型轴向柱塞泵，其特征在于，所述泵轴上安装有轴承组件，所述轴承组件包括依次相连的圆锥滚子轴承、轴套、角接触球轴承。
  8. 根据权利要求1所述的一种新型轴向柱塞泵，其特征在于，所述吸入阀组包括若干个轴向放置的吸入单向阀，所述吸入单向阀内嵌于缸体阀孔。
  9. 根据权利要求8所述的一种新型轴向柱塞泵，其特征在于，所述压出阀组包括若干个径向放置的压出单向阀，所述压出单向阀内嵌于缸体阀孔。
  10. 根据权利要求9所述的一种新型轴向柱塞泵，其特征在于，所述缸体包括进液口和排液口，所述阀孔与柱塞孔相连通，吸入阀组位于阀孔内靠近进液口设置，压出阀组位于阀孔内靠近排液口设置。
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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108035857A (zh) * 2018-01-05 2018-05-15 燕山大学 一种轴向柱塞式泵/马达及海水淡化液压系统
CN108050029A (zh) * 2017-12-05 2018-05-18 宁波市奉化溪口威尔特制泵厂 一种节能高效斜盘式高压柱塞泵
CN109058462A (zh) * 2018-09-10 2018-12-21 内蒙古鄂尔多斯电力冶金集团股份有限公司 内压式水封接头
CN110107447A (zh) * 2019-06-24 2019-08-09 杭州力龙液压有限公司 高低速切换装置、液压马达和挖掘机
CN110632280A (zh) * 2018-06-22 2019-12-31 浙江师范大学 一种柱塞副360度油膜形貌测试装置
CN113008718A (zh) * 2021-03-23 2021-06-22 太原科技大学 一种轴向柱塞泵配流副试验装置及方法
CN113446178A (zh) * 2021-06-21 2021-09-28 北京华德液压工业集团有限责任公司 一种轴向柱塞泵柱塞及轴向柱塞泵
CN113669318A (zh) * 2021-08-03 2021-11-19 华侨大学 转轴控制的液控单向阀配流径向柱塞液压装置
CN115182876A (zh) * 2022-07-18 2022-10-14 江苏可奈力机械制造有限公司 一种具有杂质过滤功能的柱塞泵
CN115507011A (zh) * 2022-09-13 2022-12-23 厦门大学 带双弹簧-质量-液阻的柱塞机器斜盘二维摆振抑制装置
CN115655542A (zh) * 2022-06-30 2023-01-31 潍柴动力股份有限公司 滑靴拉脱力的检测方法、检测装置和检测系统
CN108422173B (zh) * 2018-05-08 2023-07-18 武汉泛洲中越合金有限公司 一种滑靴扣压工装
CN118148873A (zh) * 2024-05-10 2024-06-07 沈阳格鲁克自动化设备有限公司 一种柱塞泵

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09209918A (ja) * 1996-02-08 1997-08-12 Mitsubishi Heavy Ind Ltd 流体機械
CN2328811Y (zh) * 1997-09-23 1999-07-14 阎学富 电磁控制变量轴向柱塞泵
JP2005133647A (ja) * 2003-10-30 2005-05-26 Ebara Corp アキシアルピストンポンプ又はモータ
CN103184990A (zh) * 2013-03-14 2013-07-03 北京工业大学 倾斜柱塞式纯水液压斜盘泵
DE102013204861A1 (de) * 2013-03-20 2014-09-25 Robert Bosch Gmbh Hydraulisches Gerät, insbesondere hydrostatische Verdrängereinheit oder hydraulisches Ventil
CN204082514U (zh) * 2014-07-21 2015-01-07 浙江沃尔液压科技有限公司 抗磨损的轴向柱塞式液压泵
CN105090008A (zh) * 2015-07-24 2015-11-25 杭州绿聚科技有限公司 一种新型轴向柱塞泵

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09209918A (ja) * 1996-02-08 1997-08-12 Mitsubishi Heavy Ind Ltd 流体機械
CN2328811Y (zh) * 1997-09-23 1999-07-14 阎学富 电磁控制变量轴向柱塞泵
JP2005133647A (ja) * 2003-10-30 2005-05-26 Ebara Corp アキシアルピストンポンプ又はモータ
CN103184990A (zh) * 2013-03-14 2013-07-03 北京工业大学 倾斜柱塞式纯水液压斜盘泵
DE102013204861A1 (de) * 2013-03-20 2014-09-25 Robert Bosch Gmbh Hydraulisches Gerät, insbesondere hydrostatische Verdrängereinheit oder hydraulisches Ventil
CN204082514U (zh) * 2014-07-21 2015-01-07 浙江沃尔液压科技有限公司 抗磨损的轴向柱塞式液压泵
CN105090008A (zh) * 2015-07-24 2015-11-25 杭州绿聚科技有限公司 一种新型轴向柱塞泵

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108050029A (zh) * 2017-12-05 2018-05-18 宁波市奉化溪口威尔特制泵厂 一种节能高效斜盘式高压柱塞泵
CN108035857A (zh) * 2018-01-05 2018-05-15 燕山大学 一种轴向柱塞式泵/马达及海水淡化液压系统
CN108035857B (zh) * 2018-01-05 2023-05-30 燕山大学 一种轴向柱塞式泵/马达及海水淡化液压系统
CN108422173B (zh) * 2018-05-08 2023-07-18 武汉泛洲中越合金有限公司 一种滑靴扣压工装
CN110632280A (zh) * 2018-06-22 2019-12-31 浙江师范大学 一种柱塞副360度油膜形貌测试装置
CN109058462A (zh) * 2018-09-10 2018-12-21 内蒙古鄂尔多斯电力冶金集团股份有限公司 内压式水封接头
CN110107447B (zh) * 2019-06-24 2024-03-26 杭州力龙液压有限公司 高低速切换装置、液压马达和挖掘机
CN110107447A (zh) * 2019-06-24 2019-08-09 杭州力龙液压有限公司 高低速切换装置、液压马达和挖掘机
CN113008718A (zh) * 2021-03-23 2021-06-22 太原科技大学 一种轴向柱塞泵配流副试验装置及方法
CN113446178A (zh) * 2021-06-21 2021-09-28 北京华德液压工业集团有限责任公司 一种轴向柱塞泵柱塞及轴向柱塞泵
CN113669318A (zh) * 2021-08-03 2021-11-19 华侨大学 转轴控制的液控单向阀配流径向柱塞液压装置
CN113669318B (zh) * 2021-08-03 2023-05-05 华侨大学 转轴控制的液控单向阀配流径向柱塞液压装置
CN115655542A (zh) * 2022-06-30 2023-01-31 潍柴动力股份有限公司 滑靴拉脱力的检测方法、检测装置和检测系统
CN115182876A (zh) * 2022-07-18 2022-10-14 江苏可奈力机械制造有限公司 一种具有杂质过滤功能的柱塞泵
CN115182876B (zh) * 2022-07-18 2023-09-08 江苏可奈力机械制造有限公司 一种具有杂质过滤功能的柱塞泵
CN115507011A (zh) * 2022-09-13 2022-12-23 厦门大学 带双弹簧-质量-液阻的柱塞机器斜盘二维摆振抑制装置
CN115507011B (zh) * 2022-09-13 2024-04-30 厦门大学 带双弹簧-质量-液阻的柱塞机器斜盘二维摆振抑制装置
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