WO2015074440A1 - 一种摆线液压马达输出轴及轴阀配流摆线液压马达 - Google Patents

一种摆线液压马达输出轴及轴阀配流摆线液压马达 Download PDF

Info

Publication number
WO2015074440A1
WO2015074440A1 PCT/CN2014/083430 CN2014083430W WO2015074440A1 WO 2015074440 A1 WO2015074440 A1 WO 2015074440A1 CN 2014083430 W CN2014083430 W CN 2014083430W WO 2015074440 A1 WO2015074440 A1 WO 2015074440A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic motor
shaft
output shaft
radius
diameter section
Prior art date
Application number
PCT/CN2014/083430
Other languages
English (en)
French (fr)
Inventor
王志生
张智敏
张常青
盛玉川
周峰
Original Assignee
镇江大力液压马达股份有限公司
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
Priority claimed from CN201310584115.5A external-priority patent/CN103629042B/zh
Priority claimed from CN201310584259.0A external-priority patent/CN103671465B/zh
Application filed by 镇江大力液压马达股份有限公司 filed Critical 镇江大力液压马达股份有限公司
Priority to EP14863301.9A priority Critical patent/EP3073133B8/en
Publication of WO2015074440A1 publication Critical patent/WO2015074440A1/zh

Links

Classifications

    • 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
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/104—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F01C1/105—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement and having an articulated driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/105—Details concerning timing or distribution valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the invention relates to a cycloidal hydraulic motor output shaft, and to a shaft valve distribution cycloidal hydraulic motor using the cycloid hydraulic motor output shaft, belonging to the technical field of hydraulic transmission.
  • the cycloidal hydraulic motor is a low-speed high-torque motor with the advantages of small size, high unit power density, high efficiency, wide speed range, etc., and thus has been widely used, especially for shaft-distributing hydraulic motors, due to the structural unit and low cost. It is very suitable for occasions with low pressure level and high cost performance.
  • the output shaft is provided with a circumferential annular oil groove, but the oil groove of this structure is not conducive to the radial bearing capacity of the output shaft.
  • the basic structure of the cycloidal hydraulic motor is that the body casing or the rear cover is provided with a liquid inlet and a return port, and one end is provided with a cycloidal pinion engagement pair and a flow distribution mechanism, and the flow distribution mechanism can be placed before or after the cycloidal pinion engagement pair
  • the front part is assigned to the shaft valve, the latter is the plane distribution, and the other end is equipped with the output shaft.
  • the rotor of the cycloidal pinion pair is engaged with the external gear of one end of the linkage shaft through the internal spline, and the other end of the linkage shaft is coupled with the output shaft.
  • the flow distribution mechanism communicates the inlet port with the extended engagement cavity of the cycloidal pin wheel pair, and the contraction chamber of the cycloidal pin wheel pair communicates with the return port.
  • the pressurized liquid enters the body shell or the back cover from the liquid inlet, it enters the extended engagement cavity formed by the meshing pin engagement pair, so that its volume is continuously expanded, and the liquid in the contraction engagement cavity formed by the cycloidal pinion pair is Returning from the return port; during this process, the rotor of the cycloidal pinion pair is driven to rotate by the pressure difference between the extended meshing cavity and the contraction meshing cavity, and the rotation is transmitted to the output shaft output through the linkage shaft, thereby realizing the hydraulic energy direction. Conversion of mechanical energy.
  • the distribution mechanism also called the shaft valve
  • the switching state is continuously switched continuously, so that the conversion process can continue, and the motor continuously outputs torque.
  • the existing compact shaft valve distribution cycloidal hydraulic motor has developed rapidly (such as the BM1, BMP, BMR products produced by the applicant), although the sliding bearing of the distribution mechanism in the prior art hydraulic motor can withstand a certain diameter. Force, but due to its structural limitations, it is not suitable for driving external gears, sprocket or direct drive large radial force, even if increased Set radial needle roller bearings or ball bearings (such as Chinese patent CN200720041824.9 ⁇ with radial needle bearing support with inconsistent front and rear mounting dimensions, CN201220454428.X ⁇ use the front end of the output shaft to install radial bearing ball bearings), withstand The ability of large radial forces is still difficult to achieve significant improvements and may also result in increased leakage. Summary of the invention
  • the primary object of the present invention is to provide a line hydraulic motor output shaft which is advantageous for ensuring radial load carrying capacity, and has a good process of sealing and lubricating effects, and at the same time, aiming at the problems existing in the prior art described above. Out of its processing methods.
  • the cycloid hydraulic motor output shaft of the present invention comprises a main shaft body, and the main shaft body is composed of a large diameter section which is assembled in the body of the cycloidal hydraulic motor and a small diameter section which protrudes outside the body casing;
  • the inner hole of the large diameter section has a transmission structure with the hydraulic motor linkage shaft, and the outer circular surface has a dynamic matching portion with the inner hole of the body casing, and the movable matching portion has at least two circumferential intermittent oil grooves;
  • the groove bottom of the intermittent oil sump is composed of an eccentric arc segment whose center is offset from the center of the outer circle of the movable matching portion by a process eccentricity, and the radius of the eccentric arc segment is larger than the radius of the outer circle of the movable matching portion.
  • the process eccentricity is determined according to the set eccentric arc radius, the maximum depth of the intermittent oil groove, and the radius of the moving fit portion, as follows:
  • R the radius of the eccentric arc (hidden)
  • r The radius of the moving part (mm).
  • the eccentricity e of the above process and the radius R of the eccentric arc segment are not difficult to be established according to the corresponding geometric relationship according to the maximum depth h of the intermittent oil groove and the outer arc length 1 or the arc center angle and the radius r of the moving joint portion. Find the simultaneous equation.
  • the outer diameter surface of the large diameter section has front and rear neck sections respectively for mounting the front and rear needle bearings, and the front and rear neck sections are adjacent to the front neck section and the body shell The inner hole is moved to the joint.
  • section of the intermittent oil groove is a dovetail shape having a narrow bottom and a wide bottom.
  • the interrupted oil tank can be processed as follows:
  • the spindle body is clamped on the vehicle or the grinding rotating fixture with the axis offset from the center of the vehicle or the grinding center of the rotating rotating fixture;
  • the second step is to drive the car or the grinding rotary clamp to rotate;
  • the third step after the turning tool or the grinding wheel contacts the main shaft body, according to the maximum oil groove depth, the required first section of the intermittent oil groove is processed;
  • the angular position of the main shaft body relative to the rotating jig is rotated according to the angular position of the adjacent intermittent oil groove, and then clamped according to the second step and the third step above. Operation, processing the subsequent intermittent oil sump.
  • the output shaft of the line hydraulic motor of the invention is used, the output shaft is prevented from being surrounded by the annular oil groove, so that the radial bearing capacity is enhanced, and the conventional fixture (or special process equipment) such as a four-jaw chuck can be used.
  • the oil sump required for the vehicle does not need to be cumbersomely milled like a deep oil sump such as a circumferential discontinuity, which helps to significantly improve work efficiency and reduce manufacturing costs, and replaces the eccentric arc bottom oil sump with a decreasing depth at both ends in the middle.
  • the equal depth oil groove with the low concentric arc is more beneficial to the outer circle of the oil groove in the oil groove from the two ends of the oil groove to the outer groove between the adjacent oil grooves of the main body of the main shaft body, and then spread to both sides. , to better form the oil film, to ensure lubrication and sealing.
  • oil tanks that have been processed after heat treatment they are ground on a grinding machine with a four-claw chuck.
  • a further object of the present invention is to provide a shaft valve distribution cycloidal hydraulic motor with improved radial bearing capacity, improved sealing performance, and good processability while maintaining a compact structure.
  • the shaft valve distribution cycloid hydraulic motor of the present invention comprises a front cover and a body case fixed to each other, and a stator and a rotor whose one end is fixed to the body case through the spacer and the other end is fixed to the back cover.
  • the body casing is provided with an output shaft extending from the outer end, and the output shaft is connected to the rotor through the linkage shaft; wherein the inner hole of the body casing is a through hole of the same inner diameter, A front needle bearing and a rear needle bearing having the same outer diameter are respectively mounted on the front end and the rear end of the output shaft, wherein the length of the front needle bearing is greater than the length of the rear needle bearing, and the output shaft corresponds to the front needle bearing
  • the shoulder of the front end abuts against the rear stop of the planar thrust bearing;
  • the rear end of the output needle mounted front needle bearing is a dynamic matching portion with the inner hole of the body casing, and the movable matching portion has at least two sections of circumferential direction Intermittent oil sump;
  • the bottom of the interrupted oil groove is composed of an eccentric arc segment whose center is offset from the center of the outer circle of the moving mating portion by a process eccentricity, and the radius of the eccentric arc segment is larger than the outer circle of the
  • the front dam of the planar thrust bearing is mounted and abuts against the end surface of the stepped hole in the front cover, and the shaft seal is installed in the stepped hole before the front dam.
  • the output shaft is composed of a large diameter section located in the body shell and a small diameter section outside the body shell, and the outer diameter surfaces of the large diameter section have front and rear front and rear needle bearings respectively installed
  • the neck portion has a movable matching portion with the inner hole of the body shell adjacent to the front neck portion, and the movable portion has three intermittent oil grooves intermittently distributed.
  • the shaft seal is made of a metal skeleton having an L-shaped cross section, a rectangular cross-section polytetrafluoroethylene damper which is in close contact with the inner end surface of the metal skeleton and has a sealing mating surface with the outer surface of the output shaft, and a metal skeleton and a polytetra
  • the vinyl fluoride barrier forms a semi-enclosed rubber sealing lip.
  • the rubber sealing lip has a sealing contact surface with the inner surface of the front cover stepped hole and the outer surface of the output shaft.
  • the outer circumference of the polytetrafluoroethylene barrier and the metal skeleton are filled with a rubber sealing lip.
  • the shaft valve distribution cycloidal hydraulic motor of the present invention since the inner diameter of the body shell is uniform, the processing and assembly are very convenient, and the bearing according to the front end load and the reasonable combination of the front needle roller bearing and the planar thrust bearing are further combined.
  • the bearing capacity of the front needle is enhanced, so that the radial load capacity of the hydraulic motor is improved while maintaining the compact structure, and the axial bearing capacity, processing and assembly processability are also improved compared with the prior art. it is good.
  • the rear end of the output shaft is connected to the inner hole of the body casing, and the movable matching portion has at least two circumferential intermittent oil grooves; the bottom of the intermittent oil groove is centered by the center
  • the center of the outer circle of the moving matching portion is deviated from the eccentric arc of the process eccentricity, and the radius of the eccentric arc segment is larger than the radius of the outer circle of the moving mating portion. Therefore, the present invention avoids the output shaft being surrounded by the annular oil groove, thereby facilitating the enhancement of the radial load carrying capacity, and by means of a conventional fixture (or special process equipment) such as a four-jaw chuck, the desired oil tank can be driven or ground.
  • the front dam of the planar thrust bearing is mounted and abuts against the end face of the stepped hole in the front cover, and the shaft seal is installed in the stepped hole before the front dam, thereby ensuring a reliable seal.
  • FIG. 1 is a schematic structural view of Embodiment 1 of the present invention.
  • output shaft 1 key 2
  • dust tamper 3 shaft seal 4
  • screw 5 front cover 6
  • valve body 7 seal ⁇ 8
  • valve ball 9 body shell 10
  • oil port cover 11 type 0 ⁇ 12
  • spacer 13 cycloidal pin wheel 14
  • screw plug 16 washer 17, steel washer 18, bolt 19
  • rear needle bearing 20 linkage shaft 21, front needle bearing 22, rear Block 23, 0 type ⁇ 24, plane thrust bearing 25, front dam 26.
  • FIG. 2 is a schematic structural view of an output shaft in the embodiment of FIG. 1.
  • Figure 3 is a cross-sectional view of the rotor stator pair of the embodiment of Figure 1.
  • Figure 4 is a geometrical relationship diagram of the relevant parameters of the intermediate oil sump cut along the direction indicated by the arrow in the moving part of Figure 2.
  • Fig. 5 is a schematic enlarged view showing the shaft seal of the embodiment of Fig. 1.
  • FIG. 6 is a schematic structural diagram of Embodiment 2 of the present invention.
  • Figure 7 is a cross-sectional view of the rotor stator pair of the embodiment of Figure 6. detailed description
  • the basic structure of the shaft valve distribution cycloidal hydraulic motor of the present embodiment is as shown in FIG. 1 and FIG. 3, and is basically the same as the prior art, including the front cover 6 and the body casing 10 which are fixed to each other, and one end through the partition 13 A cycloidal pin wheel 14 formed of a stator and a rotor fixed to the body casing 10 and fixed to the rear cover 15 at the other end.
  • the body casing 10 is provided with an output shaft 1 extending from the outer end, and the inner spline of the output shaft is coupled to the inner spline of the rotor via the linkage shaft 21.
  • the inner hole of the body casing 10 is a through hole of the same inner diameter, wherein the front and rear ends of the output shaft 1 are respectively provided with a front needle bearing 22 and a rear needle bearing 20 having the same outer diameter, and the length of the front needle bearing 22 is longer than The length of the needle bearing 20, the output shaft 1 corresponding to the front end of the front needle bearing 22 abuts against the rear stop 23 of the planar thrust bearing 25.
  • the output shaft 1 is formed as shown in Fig. 2, and is composed of a large diameter section 1-2 which is assembled in the cycloid hydraulic motor body casing 10 and a small diameter section 1-1 which extends outside the body casing. A keyway is formed in the small diameter section 1-1 to transmit power and motion through the key connection.
  • the inner hole of the large diameter section 1-2 has an internal spline engagement structure that is drivingly connected with the hydraulic motor linkage shaft 21, and the front and rear neck sections of the front and rear needle bearing 22, 20 are respectively installed at both ends of the outer circumference surface.
  • the front and rear neck portions are adjacent to the front neck portion and have a dynamic matching portion 1-2-1 with the inner hole of the body shell 10.
  • the movable joint portion 1-2-1 has three sections of circumferentially evenly spaced intermittent oil grooves 1-2-2. As shown in FIG. 4, the bottom of each of the intermittent oil sumpes 1-2-2 is composed of a center 0, and an eccentric arc of the center eccentricity of the outer circumference of the movable matching portion 1-2-1, which is an eccentric arc.
  • the radius R is greater than the radius r of the outer circumference of the movable mating portion 1-2-1.
  • e R + hr; e process eccentricity (mm); R eccentric arc radius (mm); h interrupted oil groove maximum depth (mm), usually 0.3mm to 1.0mm; r - dynamic fit part radius ( Mm ), the radius of the distribution shaft of different series of hydraulic motors is different, for example, the BMP and BMR series are set to 21mm to 21.5mm.
  • the radius r of the moving part, the outer arc length of the intermittent oil groove 1 (or its central angle A, usually between 30 and 65), and the maximum depth h are circumferentially spaced from the existing design. Concentric arc bottom is the same as the deep oil groove. According to the common knowledge of cosine theorem, it is not difficult to find the geometric relationship between them by Fig. 3, and establish the simultaneous equation to solve the eccentricity e and radius of the eccentric arc.
  • the front dam 26 of the planar thrust bearing 25 is mounted and abuts against the end face of the stepped hole in the front cover 6, and the shaft seal 4 is mounted in the stepped hole before the front dam 26.
  • the specific structure of the shaft seal is as shown in FIG. 5, a metal skeleton 4-1 having an L-shaped cross section, a rectangular cross-section poly 4 which is in close contact with the inner end surface of the metal skeleton 4-1 and has a sealing mating surface with the outer circular surface of the output shaft 1.
  • the body casing 10 is provided with a circulating oil return passage communicating with the internal cavity, and two check valves composed of the valve body 7, the sealing port 8, and the valve ball 9 are installed in the oil return passage, and one end of the two one-way valves Connected to the oil inlet and return port respectively, and the other end Do not communicate with the internal cavity of the motor through the internal drain valve check port between the front cover 6 and the body casing 10. This helps protect the shaft seal.
  • the inner hole of the same size of the body shell 10 is a straight hole, and the machining is performed once in the process of turning, grinding, etc., and the processing is very convenient, and the dimensional accuracy and the shape and position accuracy are easily ensured.
  • the interrupted oil groove on the output shaft is carried out as follows: In the first step, the basic shape-processed output shaft is clamped on the indexing chuck, and is clamped at a position offset from the center of the turning center of the turning rotating fixture. On the four-claw chuck of the lathe; the second step is to start the lathe to drive the four-jaw chuck to rotate; the third step is to use the turning tool that matches the shape of the interrupted oil groove and the shape of the intermittent oil groove.
  • the fourth step is to rotate the output shaft relative to the angular position of the four-jaw chuck while maintaining the process eccentricity. 120. , 240. After the clamping, according to the same operation in the second step and the third step above, the second and third intermittent oil grooves are machined before and after.
  • the basic structure of the shaft valve distribution cycloidal hydraulic motor of the present embodiment is as shown in FIG. 6 and FIG. 7, and the basic structure thereof is the same as that of the first embodiment.
  • the main difference is that: the cycloidal pin wheel pair is a column type rotation.
  • the stator pair is different from the integral rotary stator pair of the first embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Details Of Gearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Hydraulic Motors (AREA)

Abstract

一种摆线液压马达输出轴（1）以及采用该摆线液压马达输出轴（1）的轴阀配流摆线液压马达，属于机械传动技术领域。所述输出轴（1）的本体由组装后位于摆线液压马达体壳（10）内的大径段（1-2）和伸出体壳外的小径段（1-1）构成；大径段（1-2）的内孔具有与液压马达联动轴（21）传动啮合结构，且其外圆表面具有与体壳（10）内孔动配合部位（1-2-1），动配合部位（1-2-1）具有至少二段周向间断油槽（1-2-2）；间断油槽（1-2-2）的槽底由圆心O'与动配合部位外圆的圆心O偏离工艺偏心距e的偏心弧段构成，偏心弧段的半径R大于动配合部位外圆的半径r。该输出轴和液压马达可以提高工效、降低制造成本，而且可以更好地形成油膜，增强径向受力支撑能力，并可保证润滑和密封。

Description

一种摆线 ¾J£马达输出轴及轴阀配流摆线 ¾ ^马达
相关申请
本专利申请要求 201 3年 11月 20日申请的, 申请号为 201 310584115. 5 , 名称为 "轴 阀配流摆线液压马达" 的中国专利申请， 以及 2014 年 1 月 17 申请的， 申请号为 201 310584259. 0 , 名称为 "一种摆线液压马达输出轴及其加工方法" 的中国专利申请的优 先权， 在此将其全文引入作为参考。 技术领域
本发明涉及一种摆线液压马达输出轴， 同时还涉及釆用该摆线液压马达输出轴的轴阀 配流摆线液压马达， 属于液压传动技术领域。
背景技术
摆线液压马达是一种低速大扭矩马达， 具有体积小、 单位功率密度大、 效率高、 转速 范围宽等优点， 因而得到了广泛应用， 尤其是轴配流液压马达， 由于结构筒单、 成本低， 十分适合压力等级低、 性价比要求高的场合。 为了保证轴配流阀的润滑及形成理想的配流 油膜和可靠的密封， 其输出轴设置有周向的环形油槽， 但这种结构的油槽不利于输出轴径 向承载能力。
摆线液压马达的基本结构是体壳或后盖上制有进液口和回流口， 一端装有摆线针轮啮 合副和配流机构， 配流机构可以放置在摆线针轮啮合副前或后， 一般在前的为轴阀配流， 在后的为平面配流， 另一端装有输出轴。 摆线针轮啮合副的转子通过内花键与联动轴一端 的外齿轮啮合， 联动轴的另一端与输出轴传动衔接。
工作时， 配流机构使进液口与摆线针轮副的扩展啮合腔连通， 并使摆线针轮副的收缩 腔与回流口连通。 结果， 压力液体从进液口进入体壳或后盖后， 进入摆线针轮啮合副形成 的扩展啮合腔， 使其容积不断扩大， 同时摆线针轮啮合副形成的收缩啮合腔中液体则从回 流口回流； 在此过程中， 摆线针轮啮合副的转子被扩展啮合腔与收缩啮合腔的压力差驱动 旋转， 并将此旋转通过联动轴传递到输出轴输出， 从而实现液压能向机械能的转换。 与此 同时， 配流机构 （又称轴阀）也被联动轴带动旋转， 周而复始的不断切换连通状态， 使转 换过程得以延续下去， 马达连续的输出扭矩。
据申请人了解， 现有结构紧凑的轴阀配流摆线液压马达发展迅速 （如申请人生产的 BM1、 BMP , BMR产品）， 虽然现有技术液压马达中的配流机构滑动轴承可承受一定的径向力， 但由于其结构限制， 并不适合驱动外啮合齿轮、 链轮或直接驱动大径向力的工况， 即使增 设径向滚针轴承或球轴承（如中国专利 CN200720041824.9釆用前后安装尺寸不一致的径 向滚针轴承支撑， CN201220454428.X釆用输出轴的前端安装承受径向力的球轴承）， 承受 大径向力的能力仍难以得到显著改善， 还有可能造成泄漏增大。 发明内容
本发明的首要目的在于： 针对上述现有技术存在的问题， 通过结构改进， 提出一种有 利于保证径向承载能力， 并且加工工艺筒便、 密封润滑效果好的线液压马达输出轴， 同时 给出其加工方法。
为了达到上述首要目的， 本发明的摆线液压马达输出轴包括主轴本体， 所述主轴本体 由组装后位于摆线液压马达体壳内的大径段和伸出所述体壳外的小径段构成； 所述大径段 的内孔具有与液压马达联动轴传动啮合结构， 且其外圆表面具有与所述体壳内孔动配合部 位， 所述动配合部位具有至少二段周向间断油槽； 所述间断油槽的槽底由圆心与所述动配 合部位外圆的圆心偏离工艺偏心距的偏心弧段构成， 所述偏心弧段的半径大于所述动配合 部位外圆的半径。
所述工艺偏心距根据设定的偏心弧段半径、 间断油槽最大深度以及动配合部位半径， 按下式确定：
e=R+h-r
式中
e——工艺偏心距 ( mm )
R——偏心弧段半径（隱）
h一一间断油槽最大深度 (隱）
r——动配合部位半径（mm )。
上述工艺偏心距 e以及偏心弧段的半径 R根据设定的间断油槽最大深度 h和外弧长 1 或该弧长所对圆心角以及动配合部位半径 r , 不难根据相应的几何关系， 建立联立方程求 出。
进一步， 所述大径段的外圆表面两端具有分别安装前、 后滚针轴承的前、 后缩颈 段， 所述前、 后缩颈段之间邻近前缩颈段处具有与体壳内孔动配合部位。
更进一步， 所述间断油槽的截面为口窄底宽的燕尾形。
这样， 间断油槽的加工时可以按以下步骤进行：
第一步、 将主轴本体以其轴线偏离车或磨削旋转夹具回转中心工艺偏心距的位置夹持 在车或磨削旋转夹具上；
第二步、 驱使车或磨削旋转夹具旋转； 第三步、 车刀或砂轮接触主轴本体后， 根据最大油槽深度进刀， 加工出所需的第一段 间断油槽；
第四步、 在保持工艺偏心距的情况下， 将主轴本体相对所述旋转夹具的角向位置按相 邻间断油槽的角向位置转动后夹持， 按以上第二步和第三步相同的操作， 加工出后续的间 断油槽。
釆用本发明的线液压马达输出轴后， 避免了输出轴被环形油槽隔段， 因此有利于增强 径向承载能力， 并且借助四爪卡盘等常规工装夹具（或专用工艺装备）， 即可车出所需的 油槽， 无需像周向间断等深油槽那样需要繁瑣的铣削加工， 从而有助于显著提高工效、 降 低制造成本， 而且以中间向两端深度逐渐减小的偏心弧底油槽取代原先同心弧低的等深度 油槽， 从理论和实际上都更有利于油槽内的容油从油槽两端向主轴本体动配合部位相邻油 槽之间的外圆段渗输， 进而向两侧扩散， 从而更好地形成油膜， 保证润滑和密封。 对于热 处理后加工的油槽， 则釆用类似四爪卡盘的工位装备在磨床上进行磨削加工。
本发明的进一步的目的在于： 通过结构改进， 提出一种在保持紧凑结构前提下， 径向 承力能力得以提高、 密封效能得以增强， 并且具有良好工艺性的轴阀配流摆线液压马达。
为了达到上述进一步的目的， 本发明的轴阀配流摆线液压马达包括相互固连的前盖 和体壳， 以及一端通过隔盘与体壳固连、 另一端与后盖固连的定子和转子构成的摆线针 轮副； 所述体壳内装有外端延伸出的输出轴， 所述输出轴通过联动轴与转子传动连接； 其中， 所述体壳的内孔为同一内径的通孔， 其中的输出轴前部和后端分别安装外径相同的 前滚针轴承与后滚针轴承， 所述前滚针轴承的长度大于后滚针轴承的长度， 所述输出轴 对应前滚针轴承前端的轴肩抵靠于平面推力轴承的后挡圏； 所述输出轴安装前滚针轴承的 后端为与所述体壳内孔动配合部位， 所述动配合部位具有至少二段周向间断油槽； 所述间 断油槽的槽底由圆心与所述动配合部位外圆的圆心偏离工艺偏心距的偏心弧段构成， 所 述偏心弧段的半径大于所述动配合部位外圆的半径。
进一步地， 所述平面推力轴承的前挡圏安装并抵靠在前盖内的台阶孔端面上， 所述前 挡圏之前的台阶孔内安装轴封。
进一步地， 所述输出轴由位于体壳内的大径段和伸出体壳外的小径段构成， 所述大径 段的外圆表面两端具有分别安装前、 后滚针轴承的前、 后缩颈段， 所述前、 后缩颈段之 间邻近前缩颈段处具有与体壳内孔动配合部位， 所述动配合部位具有三段周向均布的间 断油槽。
进一步地， 所述轴封由截面为 L形的金属骨架、 紧贴金属骨架内端面且具有与输出轴 外圆表面密封配合面的矩形截面聚四氟乙烯挡圏， 以及对金属骨架和聚四氟乙烯挡圏形成 半包围的橡胶密封唇构成。 进一步地， 所述橡胶密封唇具有分别与前盖台阶孔内表面以及输出轴外圆表面的密封 贴合面。
进一步地， 所述聚四氟乙烯挡圏的外圆与金属骨架之间被橡胶密封唇填充。
根据本发明的轴阀配流摆线液压马达， 由于体壳内径一致， 因此加工和装配均十分方 便， 而根据前端载荷较大合理设置的轴承以及前滚针轴承与平面推力轴承的有机结合， 进 一步增强了前滚针的承载能力， 因此与现有技术相比， 在保持结构紧凑的前提下， 液压马 达的径向承载能力得到改善， 同时也增强了轴向承力能力， 加工和装配工艺性好。
由于所述输出轴安装前滚针轴承的后端为与所述体壳内孔动配合部位， 所述动配合部 位具有至少二段周向间断油槽； 所述间断油槽的槽底由圆心与所述动配合部位外圆的圆心 偏离工艺偏心距的偏心弧段构成， 所述偏心弧段的半径大于所述动配合部位外圆的半径。 因此， 本发明避免了输出轴被环形油槽隔段， 因此有利于增强径向承载能力， 并且借助四 爪卡盘等常规工装夹具 （或专用工艺装备）， 即可车或磨出所需的油槽， 无需像周向间断 等深油槽那样需要繁瑣的铣削加工， 从而有助于显著提高工效、 降低制造成本， 而且以中 间向两端深度逐渐减小的偏心弧底油槽取代原先同心弧低的等深度油槽， 从理论和实际上 都更有利于油槽内的容油从油槽两端向输出轴动配合部位相邻油槽之间的外圆段渗输， 进 而向两侧扩散， 从而更好地形成油膜， 保证润滑和密封。
在本发明中， 所述平面推力轴承的前挡圏安装并抵靠在前盖内的台阶孔端面上， 所述 前挡圏之前的台阶孔内安装轴封， 从而保证了可靠的密封。 附图说明
下面结合附图对本发明作进一步详细描述。
图 1为本发明实施例一的结构示意图。
图中： 输出轴 1 , 键 2, 防尘圏 3 , 轴封 4, 螺钉 5, 前盖 6, 阀体 7, 密封圏 8, 阀球 9, 体壳 10, 油口盖 11 , 0型圏 12, 隔盘 13 , 摆线针轮副 14, 后盖 15, 螺塞 16, 垫片 17, 钢垫片 18, 螺栓 19, 后滚针轴承 20, 联动轴 21 , 前滚针轴承 22, 后挡圏 23 , 0型圏 24, 平面推力轴承 25 , 前挡圏 26。
图 2为图 1实施例中输出轴的结构示意图。
图 3为图 1实施例中转定子副的剖视图。
图 4为图 2动配合部位箭头所示方向剖切的中间断油槽相关参数几何关系图。
图 5为图 1实施例中轴封的放大结构示意图。
图 6为本发明实施例二的结构示意图。
图 7为图 6实施例中转定子副的剖视图。 具体实施方式
实施例一
本实施例的轴阀配流摆线液压马达基本结构如图 1和图 3所示， 与现有技术基本相同 的是， 包括相互固连的前盖 6和体壳 10, 以及一端通过隔盘 13与体壳 10固连、 另一端与 后盖 15固连的定子和转子构成的摆线针轮副 14。 体壳 10内装有外端延伸出的输出轴 1 , 该输出轴的内花键通过联动轴 21与转子的内花键传动连接。
体壳 10的内孔为同一内径的通孔，其中的输出轴 1前部和后端分别安装外径相同的前 滚针轴承 22与后滚针轴承 20, 前滚针轴承 22的长度大于后滚针轴承 20的长度， 输出轴 1对应前滚针轴承 22前端的轴肩抵靠于平面推力轴承 25的后挡圏 23。
其中的输出轴 1如图 2所示，由组装后位于摆线液压马达体壳 10 内的大径段 1-2和伸 出体壳外的小径段 1-1构成。 小径段 1-1上制有键槽， 以便通过键连接传递动力和运动。 大径段 1-2的内孔具有与液压马达联动轴 21传动连接的内花键啮合结构，其外圆表面两端 具有分别安装前、 后滚针轴承 22、 20 的前、 后缩颈段， 前、 后缩颈段之间邻近前缩颈段 处具有与体壳 10内孔动配合部位 1-2-1 , 此外前、 后缩颈段之间还具有其它形成轴配流的 结构（与现有技术基本相同， 不另赘述）。 动配合部位 1-2-1具有三段周向均布的间断油槽 1-2-2。 如图 4所示， 各间断油槽 1-2-2的槽底由圆心 0，与动配合部位 1-2-1外圆的圆心 0 偏离工艺偏心距 e的偏心弧段构成， 该偏心弧段的半径 R大于动配合部位 1-2-1外圆的半 径 r。 显然， e=R+h-r; e 工艺偏心距 ( mm ); R 偏心弧段半径（mm ); h 间断 油槽最大深度（mm ), 通常为 0.3mm至 1.0mm; r——动配合部位半径（mm ), 不同系列 液压马达配流轴的半径有所不同，例如 BMP、 BMR系列为定值 21mm至 21.5mm。设计时， 动配合部位的半径 r、 间断油槽的外弧长 1 (或其所对圆心角 A, 通常在 30。至 65。之间）、 最大深度 h均与现有设计的周向间隔、同心弧底等深油槽一致，根据余弦定理等数学常识， 不难由图 3找出相互之间的几何关系， 建立联立方程求解出偏心弧段的工艺偏心距 e和半 径 。
平面推力轴承 25的前挡圏 26安装并抵靠在前盖 6内的台阶孔端面上，前挡圏 26之前 的台阶孔内安装轴封 4。 该轴封的具体结构如图 5所示， 由截面为 L形的金属骨架 4-1、 紧 贴金属骨架 4-1 内端面且具有与输出轴 1外圆表面密封配合面的矩形截面聚四氟乙烯挡圏 4-2, 以及对金属骨架 4-1和聚四氟乙烯挡圏 4-2形成半包围的橡胶密封唇 4-3构成， 所述 橡胶密封唇 4-3具有分别与前盖 6台阶孔内表面以及输出轴外圆表面的密封贴合面， 所述 聚四氟乙烯挡圏 4-2的外圆与金属骨架 4-1之间被橡胶密封唇 4-3填充。
此外，体壳 10制有与内部腔体连通的循环回油通道，回油通道中安装有两个由阀体 7、 密封圏 8、 阀球 9构成的单向阀， 两个单向阀一端分别与进油口和回油口相连， 另一端分 别通过前盖 6与体壳 10之间的内泄油液单向阀回油口通道与马达内部腔体连通。 这样有 利于保护轴封。
加工时，体壳 10同一尺寸的内孔为直孔，在车、磨等工序均一次走刀，加工十分方便， 尺寸精度和形位精度容易保证。 输出轴上的间断油槽则按以下步骤进行： 第一步、 将基本 形状加工好的输出轴装夹在分度卡盘上， 在以其轴线偏离车削旋转夹具回转中心工艺偏心 距的位置夹持在车床的四爪卡盘上； 第二步、 启动车床， 驱使四爪卡盘旋转； 第三步、 釆 用刀尖部位形状与间断油槽截面形状吻合的车刀， 进刀使车刀刀尖接触输出轴后， 根据最 大油槽深度进刀切削， 即可加工出第一段间断油槽； 第四步、在保持工艺偏心距的情况下， 将输出轴相对四爪卡盘的角向位置先后转动 120。、 240。后夹持， 按以上第二步和第三步相 同的操作， 前后加工出第二段、 第三段间断油槽。
实施例二
本实施例的轴阀配流摆线液压马达基本结构如图 6和图 7所示， 其基本结构与实施例 一相同， 主要的不同之处在于： 其中的摆线针轮副是镶柱式转定子副， 而不同于实施例一 的整体式转定子副。
试验证明， 由于上述实施例釆取了一系列看似细微、 实则有效的完善改进措施， 因此 将液压马达的径向力承受能力提高了近 40%, 同时也提高了轴向承力能力， 其结构紧凑、 外形小巧， 零件加工、 装配的工艺好， 从而使传统产品的性价比得到进一步提高。

Claims

权利要求
1. 一种摆线液压马达输出轴， 包括主轴本体， 所述主轴本体由组装后位于摆线液压 马达体壳内的大径段和伸出所述体壳外的 、径段构成； 所述大径段的内孔具有与液压马 达联动轴传动啮合结构， 且其外圆表面具有与所述体壳内孔动配合部位， 所述动配合部 位具有至少二段周向间断油槽； 其特征在于： 所述间断油槽的槽底由圆心与所述动配合 部位外圆的圆心偏离工艺偏心距的偏心弧段构成， 所述偏心弧段的半径大于所述动配合 部位外圆的半径。
2. 根据权利要求 1所述的摆线液压马达输出轴， 其特征在于： 所述工艺偏心距根据设 定的偏心弧段半径、 间断油槽最大深度以及动配合部位半径， 按下式确定：
e=R+h-r
式中
e 工艺偏心距 ( mm )
R——偏心弧段半径（mm )
h——间断油槽最大深度（mm )
r 动配合部位半径（mm )。
3. 根据权利要求 1或 2所述的摆线液压马达输出轴， 其特征在于： 所述大径段的外 圆表面两端具有分别安装前、 后滚针轴承的前、 后缩颈段， 所述前、 后缩颈段之间邻近 前缩颈段处具有与体壳内孔动配合部位。
4. 根据权利要求 3 所述的摆线液压马达输出轴， 其特征在于： 所述间断油槽的截面 为口窄底宽的燕尾形。
5. 一种轴阀配流摆线液压马达， 包括相互固连的前盖和体壳， 以及一端通过隔盘与 体壳固连、 另一端与后盖固连的定子和转子构成的摆线针轮副； 所述体壳内装有外端延 伸出的输出轴， 所述输出轴通过联动轴与转子传动连接； 其特征在于： 所述体壳的内孔 为同一内径的通孔， 其中的输出轴前部和后端分别安装外径相同的前滚针轴承与后滚针 轴承， 所述前滚针轴承的长度大于后滚针轴承的长度， 所述输出轴对应前滚针轴承前端 的轴肩抵靠于平面推力轴承的后挡圏； 所述输出轴安装前滚针轴承的后端为与所述体壳内 孔动配合部位， 所述动配合部位具有至少二段周向间断油槽； 所述间断油槽的槽底由圆心 与所述动配合部位外圆的圆心偏离工艺偏心距的偏心弧段构成， 所述偏心弧段的半径大 于所述动配合部位外圆的半径。
6. 根据权利要求 5 所述的轴阀配流摆线液压马达， 其特征在于： 所述平面推力轴承 的前挡圏安装并抵靠在前盖内的台阶孔端面上， 所述前挡圏之前的台阶孔内安装轴封。
7. 根据权利要求 6 所述的轴阀配流摆线液压马达， 其特征在于： 所述输出轴由位于 体壳内的大径段和伸出体壳外的小径段构成， 所述大径段的外圆表面两端具有分别安装 前、 后滚针轴承的前、 后缩颈段， 所述前、 后缩颈段之间邻近前缩颈段处具有与体壳内 孔动配合部位， 所述动配合部位具有三段周向均布的间断油槽。
8. 根据权利要求 7所述的轴阀配流摆线液压马达， 其特征在于： 所述轴封由截面为 L 形的金属骨架、 紧贴金属骨架内端面且具有与输出轴外圆表面密封配合面的矩形截面聚四 氟乙烯挡圏， 以及对金属骨架和聚四氟乙烯挡圏形成半包围的橡胶密封唇构成。
9. 根据权利要求 8 所述的轴阀配流摆线液压马达， 其特征在于： 所述橡胶密封唇具 有分别与前盖台阶孔内表面以及输出轴外圆表面的密封贴合面。
10. 根据权利要求 9所述的轴阀配流摆线液压马达， 其特征在于： 所述聚四氟乙烯挡 圏的外圆与金属骨架之间被橡胶密封唇填充。
PCT/CN2014/083430 2013-11-20 2014-07-31 一种摆线液压马达输出轴及轴阀配流摆线液压马达 WO2015074440A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14863301.9A EP3073133B8 (en) 2013-11-20 2014-07-31 Output shaft of cycloid hydraulic motor and shaft valve flow-distribution cycloid hydraulic motor

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201310584115.5A CN103629042B (zh) 2013-11-20 2013-11-20 轴阀配流摆线液压马达
CN201310584115.5 2013-11-20
CN201310584259.0A CN103671465B (zh) 2014-01-17 2014-01-17 一种摆线液压马达输出轴及其加工方法
CN201310584259.0 2014-01-17

Publications (1)

Publication Number Publication Date
WO2015074440A1 true WO2015074440A1 (zh) 2015-05-28

Family

ID=53179099

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/083430 WO2015074440A1 (zh) 2013-11-20 2014-07-31 一种摆线液压马达输出轴及轴阀配流摆线液压马达

Country Status (2)

Country Link
EP (1) EP3073133B8 (zh)
WO (1) WO2015074440A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108506156A (zh) * 2018-04-13 2018-09-07 杭州宇控机电工程有限公司 一种全海深液压机械手用肘关节摆动液压马达
WO2023014536A1 (en) * 2021-08-04 2023-02-09 Caterpillar Inc. Axial piston pump mounting flange configuration

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10920758B2 (en) 2018-06-29 2021-02-16 Bendix Commercial Vehicle Systems Llc Hypocycloid compressor
WO2024082032A1 (en) * 2022-10-21 2024-04-25 "M + S Hydraulic" Plc. Planetary hydraulic motor

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2545386Y (zh) * 2002-05-31 2003-04-16 宁波中意液压马达有限公司 轴向配油摆线液压马达
CN2760279Y (zh) * 2004-08-26 2006-02-22 伊顿流体动力（济宁）有限公司 低噪音轴配流摆线液压马达
CN201121555Y (zh) * 2007-11-26 2008-09-24 镇江大力液压马达有限责任公司 双轴输出轴阀配流摆线液压马达
CN201650916U (zh) * 2010-04-27 2010-11-24 怀特(中国)驱动产品有限公司 轴配流摆线液压马达
CN102588203A (zh) * 2011-12-22 2012-07-18 镇江大力液压马达有限责任公司 多外泄流道多油口摆线液压马达
CN103629402A (zh) * 2012-08-21 2014-03-12 江苏嘉亦特液压件有限公司 S30p板式单向阀
CN103671465A (zh) * 2014-01-17 2014-03-26 镇江大力液压马达股份有限公司 一种摆线液压马达输出轴及其加工方法
CN203584678U (zh) * 2013-11-20 2014-05-07 镇江大力液压马达股份有限公司 轴阀配流摆线液压马达
CN203627077U (zh) * 2013-12-13 2014-06-04 镇江大力液压马达股份有限公司 一种摆线液压马达体壳孔
CN203670433U (zh) * 2014-01-19 2014-06-25 镇江大力液压马达股份有限公司 一种摆线液压马达输出轴

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3572983A (en) * 1969-11-07 1971-03-30 Germane Corp Fluid-operated motor
DE10200968C1 (de) * 2002-01-12 2003-10-23 Sauer Danfoss Nordborg As Nord Hydraulikmotor
ITBO20020757A1 (it) * 2002-12-03 2004-06-04 Sam Hydraulik Spa Motore idrostatico con distribuzione radiale.
DE102007017652A1 (de) * 2007-04-12 2008-10-16 Sauer-Danfoss Aps Rotationskolbenmaschine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2545386Y (zh) * 2002-05-31 2003-04-16 宁波中意液压马达有限公司 轴向配油摆线液压马达
CN2760279Y (zh) * 2004-08-26 2006-02-22 伊顿流体动力（济宁）有限公司 低噪音轴配流摆线液压马达
CN201121555Y (zh) * 2007-11-26 2008-09-24 镇江大力液压马达有限责任公司 双轴输出轴阀配流摆线液压马达
CN201650916U (zh) * 2010-04-27 2010-11-24 怀特(中国)驱动产品有限公司 轴配流摆线液压马达
CN102588203A (zh) * 2011-12-22 2012-07-18 镇江大力液压马达有限责任公司 多外泄流道多油口摆线液压马达
CN103629402A (zh) * 2012-08-21 2014-03-12 江苏嘉亦特液压件有限公司 S30p板式单向阀
CN203584678U (zh) * 2013-11-20 2014-05-07 镇江大力液压马达股份有限公司 轴阀配流摆线液压马达
CN203627077U (zh) * 2013-12-13 2014-06-04 镇江大力液压马达股份有限公司 一种摆线液压马达体壳孔
CN103671465A (zh) * 2014-01-17 2014-03-26 镇江大力液压马达股份有限公司 一种摆线液压马达输出轴及其加工方法
CN203670433U (zh) * 2014-01-19 2014-06-25 镇江大力液压马达股份有限公司 一种摆线液压马达输出轴

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3073133A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108506156A (zh) * 2018-04-13 2018-09-07 杭州宇控机电工程有限公司 一种全海深液压机械手用肘关节摆动液压马达
CN108506156B (zh) * 2018-04-13 2023-12-05 杭州宇控机电工程有限公司 一种全海深液压机械手用肘关节摆动液压马达
WO2023014536A1 (en) * 2021-08-04 2023-02-09 Caterpillar Inc. Axial piston pump mounting flange configuration
US12006924B2 (en) 2021-08-04 2024-06-11 Caterpillar Inc. Axial piston pump mounting flange configuration

Also Published As

Publication number Publication date
EP3073133B1 (en) 2019-03-06
EP3073133A4 (en) 2017-02-22
EP3073133A1 (en) 2016-09-28
EP3073133B8 (en) 2019-06-05

Similar Documents

Publication Publication Date Title
CN203584678U (zh) 轴阀配流摆线液压马达
CN103629042B (zh) 轴阀配流摆线液压马达
WO2015074440A1 (zh) 一种摆线液压马达输出轴及轴阀配流摆线液压马达
CN104791208B (zh) 二维等加等减速导轨轴向活塞泵
CN104791209B (zh) 二维圆柱导轨轴向活塞泵
CN105484962A (zh) 二维双联轴向活塞泵
US3270681A (en) Rotary fluid pressure device
CA2642987A1 (en) An electric motor having an inner rotor and an outer rotor
CN103534485A (zh) 具有加压辊穴的流体装置
US2132813A (en) Rotary engine
US2985110A (en) Pump construction
CN102434382B (zh) 径向活塞滚球式端面配流低速大扭矩水压马达
CN100430191C (zh) 一种强作业水下机器人用水下机械手腕部结构
CN108105084A (zh) 一种双向摆线油泵
CN204591607U (zh) 二维圆柱导轨轴向活塞泵
CN204327396U (zh) 短壳体紧凑型轴配流摆线液压马达
CN107339192A (zh) 一种大径向力支撑轴配流摆线液压马达
US3623829A (en) Internal gear set
US3723032A (en) Anti-friction orbital and rotary device
CN103671465A (zh) 一种摆线液压马达输出轴及其加工方法
CN207750229U (zh) 一种双向摆线油泵
CN207945041U (zh) 一种改进结构的摆线液压马达
US3784336A (en) Power transmission
CN207297226U (zh) 一种大径向力支撑轴配流摆线液压马达
RU2667568C2 (ru) Усовершенствованная система для центрирования гидромашины на элементе транспортного средства

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14863301

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2014863301

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE