WO2017177936A1 - 轴向柱塞泵 - Google Patents

轴向柱塞泵 Download PDF

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Publication number
WO2017177936A1
WO2017177936A1 PCT/CN2017/080380 CN2017080380W WO2017177936A1 WO 2017177936 A1 WO2017177936 A1 WO 2017177936A1 CN 2017080380 W CN2017080380 W CN 2017080380W WO 2017177936 A1 WO2017177936 A1 WO 2017177936A1
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WO
WIPO (PCT)
Prior art keywords
swash plate
piston pump
axial piston
housing
ball head
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Application number
PCT/CN2017/080380
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English (en)
French (fr)
Inventor
朱焱炜
Original Assignee
武汉钜威天数字化机械制造有限公司
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Publication of WO2017177936A1 publication Critical patent/WO2017177936A1/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
    • 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
    • F04B1/148—Bearings therefor
    • 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
    • F04B1/16—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 two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B53/001—Noise damping
    • 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
    • F04B53/006—Crankshafts
    • 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
    • F04B53/102—Disc 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
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/108—Valves characterised by the material
    • 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 axial piston pumps and, more particularly, to an axial piston pump suitable for pumping low viscosity liquids such as fresh water or sea water.
  • a plunger pump is an important device for pumping fluid. It relies on the plunger to reciprocate in the cylinder bore of the cylinder to change the volume of the sealed working chamber to achieve suction and discharge.
  • the plunger pump has the advantages of high rated pressure, compact structure, high efficiency and convenient flow adjustment. It is widely used in high pressure, large flow and flow adjustment situations, such as hydraulic machines, construction machinery and ships.
  • the plunger pump includes two representative forms of an axial piston pump and a radial piston pump, and the axial piston pump is widely used due to its small size and the like.
  • a conventional axial piston pump includes a cylinder, a plunger that reciprocates within the cylinder, and a swashplate.
  • One end of the plunger reciprocates within the cylinder to draw or discharge fluid, and the other end abuts against the swash plate, for example, by a shoe and slides along the circumferential direction of the swash plate on the swash plate as the cylinder rotates.
  • a pump that achieves varying displacements and pressures can be achieved by adjusting the angle of inclination of the swashplate.
  • This structure is effective for use in a fluid having a high viscosity, but when the fluid to be pressurized is a fluid such as water, lubrication between the shoe and the swash plate is low due to low viscosity of water, poor lubricity, and the like.
  • the poor performance limits the angle of inclination of the swashplate, which in turn limits the pump displacement and pressure.
  • an axial piston pump suitable for pumping a low viscosity fluid is proposed.
  • the cylinder is opposite to the cylinder.
  • the housing is fixed, the plunger is mounted on the swash plate through the ball head, and the swash plate is rotatably mounted on the crank of the rotating main shaft, whereby the swash plate drives the plunger to swing, thereby avoiding the swash plate and the plunger Friction between the shoes.
  • the problem with this solution is that the rotating main shaft is a cantilever support, resulting in a large unbalanced torque, so that the oscillation stability of the swash plate is poor during operation, and the vibration of the entire pump is large. Cause noise, friction and other issues.
  • the above axial piston pump is improved, that is, the rotating main shaft is supported at both ends, and is adopted near the input end of the main shaft.
  • Two sets of bearings are used to enhance the support of the main shaft, and a guide slider is disposed on a radially outer side of the swash plate, and the guide slide is engaged with a guide chute formed on a corresponding portion of the housing to guide the swing of the swash plate.
  • this solution still fails to completely solve the problems of large vibration, poor rotational stability, large noise and friction of the plunger pump, and also increases the friction between the guide slider and the guide chute, thereby reducing the overall pump. life.
  • the main shaft is supported by two sets of bearings at its input end, and a set of bearing supports is additionally used at the opposite ends of the main shaft, the main shaft has a problem of over-constraint, thereby causing excessive stress in the main shaft and reducing the main shaft. And the life of the entire pump.
  • the present invention has been made. It is an object of the present invention to provide an axial piston pump which is particularly suitable for pumping low viscosity fluids such as sea water or fresh water and which has good balance characteristics and reduces pump vibration and noise. And increase the life of the pump.
  • an axial piston pump comprising a housing, an input spindle rotatably mounted within the housing and including a middle beveled section, rotatably mounted a swash plate on the middle obliquely curved section, a plurality of connecting rods whose one end is hinged to the swash plate by a ball head and provided with a plunger at the other end, and a cylinder body having a cylinder bore into which the plunger is reciprocally inserted
  • the cylinder is fixed relative to the housing, the swash plate is spatially spherically oscillated as the input spindle rotates, and wherein the input spindle further includes a first straight line segment, the first straight line segment A bearing is rotatably supported on the housing, and a balance ring is further disposed on the first straight line segment, the balance ring being eccentric and rotating together with the input spindle.
  • the unbalance moment of the swash plate can be further offset, and the vibration and noise of the entire axial piston pump can be further reduced.
  • the intersection of the axis of the first straight line segment of the input spindle with the axis of the intermediate oblique segment, the spherical oscillation center of the swash plate, and the center of the ball head of the plurality of links coincides at the coincidence point (A).
  • the unbalance moment of the swash plate when the space spherical surface is swung can be offset, and the vibration and noise of the entire axial piston pump can be reduced.
  • a swash plate limiting ring is also provided, said swash plate limiting ring being rotatably connected to said swash plate on the one hand by a connecting shaft, and said swash plate limiting ring on the other hand is diametrically opposed
  • a pin disposed is coupled to the housing such that the swash plate retaining ring is swingable relative to the housing about the pin.
  • valve valve comprising a valve seat and a suction valve spool and a discharge valve spool mounted in the valve seat, the suction valve spool and the discharge valve spool being respectively biased To the valve seat, wherein the valve core is made of a corrosion-resistant, high-strength lightweight material such as a titanium alloy.
  • the spool can resist corrosion such as seawater, and its weight can be reduced, thereby reducing the movement inertia of the spool.
  • annular gap is formed between the outer peripheral surface of each of the valve bodies and the corresponding mating surface of the valve seat, the annular gap being, for example, not less than 0.5 mm.
  • a second gap is formed between the valve seat and the mating component, the second gap being, for example, 0.3 to 0.4 mm.
  • the impact inertia at the time of reciprocation of the spool can be reduced. This improves the operational reliability, corrosion resistance, media adaptability of the valve, and reduces vibration and noise during operation of the valve and the axial piston pump.
  • FIG. 1 is a front sectional view showing an axial piston pump according to an embodiment of the present invention
  • Figure 2 is a partial cross-sectional view showing a swash plate portion of the axial piston pump shown in Figure 1;
  • Figure 3 is a cross-sectional view showing a swash plate limiting ring
  • Figure 4 is a cross-sectional view showing the structure of the valve train
  • Figure 5 is a perspective view showing the input spindle and the balance ring mounted thereon;
  • Figure 6 is a cross-sectional view of Figure 5.
  • an axial piston pump (hereinafter simply referred to as a pump) includes a housing 1 on which an input spindle 2 is rotatably supported by bearings 31 and 32.
  • the input spindle 2 includes a first straight section 21, a middle inclined section 22, and a second straight section 23, and the first straight section 21 and the second straight section 23 are in a straight line.
  • the intermediate oblique section 22 is integrally provided between the first straight section 21 and the second straight section 23.
  • the axis of the intermediate oblique section 22 is at an angle of 15 to 40 degrees with the axes of the first and second straight sections 21 and 22, which angle may vary depending on the desired flow rate and pressure of the pump.
  • the first straight section 21 of the input spindle 2 is supported on the housing 1 by bearings 31, for example on an end cap 11 of the housing 1, which is for example a ball bearing.
  • bearings 31 for example on an end cap 11 of the housing 1, which is for example a ball bearing.
  • the invention is not limited thereto, and other types of bearings may be employed.
  • the second straight section 23 of the input spindle 2 is also supported on the housing 1 by means of a further bearing 32 (also for example a ball bearing).
  • the intermediate beveled section 22 may, for example, comprise two different diameter sections, the swash plate 5 being rotatably mounted in the intermediate beveled section 22, for example by two differently sized tapered roller bearings 33. on.
  • a balance ring 25 is mounted, so that the input spindle 2 and the balance ring 25 can rotate together.
  • the balance ring 25 includes an axial portion 251 and a radial portion 252 that fit over the first straight section 21 of the input spindle 2, and the inner race of the first bearing 3 can fit over the axial portion 251 On the circumference.
  • the radial portion 252 of the gimbal 25 is eccentric in shape to counteract the imbalance caused by the intermediate beveled section 22 on the input spindle 2 and the swashplate mounted on the intermediate beveled section 22 during rotation of the input spindle 2.
  • the swash plate 5 of the axial piston pump will be described below with reference to Figs. 2 and 3.
  • the swash plate 5 is supported by the two tapered roller bearings 33 on the intermediate inclined section 22 of the input spindle 2 such that the swash plate 5 is inclined at an angle of 15 to 40 degrees with respect to the axis of the input spindle 2.
  • the swash plate 5 includes a swash plate body 51 and a swash plate gland 52, and the swash plate body 51 and the swash plate gland 52 are joined together by screws, for example.
  • the swash plate body 51 and the swash plate gland 52 are respectively formed with a plurality of cavities at equal intervals in the circumferential direction, so that when the swash plate body 51 and the swash plate gland 52 are assembled together, the corresponding cavities are combined into a ball.
  • the head cavity, the ball head 71 of the connecting rod is housed in each ball head cavity.
  • the cavity formed in the swash plate body 51 is a recessed cavity
  • the cavity formed in the swash plate gland 52 is a through cavity, which A through opening 512 is formed in the through cavity at one end facing the cylinder.
  • the recessed cavity and the through cavity are combined into a ball head cavity.
  • spacers 513 and 523 made of, for example, copper or the like are respectively lined in the recessed cavity and the through cavity, and the spacers 513 and 523 are fitted to form a spherical shape of the ball head 71 closely surrounding the link.
  • the cavity forms a ball joint with the ball head 71 to allow the ball head 71 to perform a spherical rotational motion.
  • the ball head 71 can be reduced in friction compared to the ball head 71 directly forming a ball joint fit with the swash plate material, and in the block It can be easily replaced when worn, reducing maintenance costs.
  • a swash plate limiting ring 8 is provided on the outer circumferential side of the swash plate 5, which swash plate limiting ring 8 is on the one hand, for example, via the connecting shaft 81 and the swash plate 5
  • the connection is such that the swash plate limiting ring 8 and the swash plate 5 are relatively rotatable about the axis of the connecting shaft 81.
  • the swash plate limiting ring 8 passes through two opposite directions.
  • the pin 82 is rotatably coupled to the housing 1 of the plunger pump.
  • the pin shaft 82 and the connecting shaft 81 are substantially different by 90 degrees in the circumferential direction.
  • the specific structure of the swash plate limiting ring 8 is described in the Chinese utility model patent CN201739163U, which is hereby incorporated by reference in its entirety.
  • the input spindle 2, the swash plate 5, and the swash plate limitation ring 8 are further configured such that the input spindle 2 passes through the first straight line segment 21 and the second The intersection of the axis of the straight line segment 23 with the axis of the intermediate oblique section 22, the center of the swash plate for spherical oscillation, the center of the circle formed by the center of each plunger ball head 71, the pin 82 of the swash plate limitation ring 8 and The intersection point of the swash plate limiting ring and the connecting shaft 81 connected to the swash plate coincides at one point, and is denoted by A in the figure and is referred to as a coincident point, hereinafter referred to as a quadruple coincidence.
  • an axial piston pump in accordance with the present invention includes a plurality of links 7, one end of each of which is hingedly coupled to the swash plate 5 by a ball 71 and the other end of which is coupled to the plunger 4. .
  • the plunger 4 is inserted into a corresponding cylinder bore 101 in the cylinder block 10 to reciprocate within the cylinder bore 101 by the drive of the link 7.
  • the cylinder 10 is fixed relative to the housing.
  • a fitting valve 9 is further provided in the casing 1, and the fitting valve 9 selectively connects the orifice passage leading to the cylinder bore 101 of the cylinder to the suction passage and the discharge passage of the plunger pump.
  • the valve valve includes a valve seat 91, a suction valve spool 92, a suction valve spring 93, a discharge valve spool 94, and a discharge valve spring 95.
  • the suction valve spring 93 biases the suction valve spool 92 against the valve seat 91 to close the suction passage 96 of the pump
  • the discharge valve spring 95 biases the discharge valve spool 94 against the valve seat 91 to close the discharge passage 97 of the pump.
  • the suction valve spool and the discharge valve spool may be made of a corrosion-resistant high-strength lightweight material such as a titanium alloy to reduce the weight thereof, thereby reducing the movement inertia of the spool.
  • the suction valve spool 92 and the discharge valve spool 94 are respectively mounted such that the annular gap G1 between the outer peripheral surface of the spool and the inner peripheral surface of the mating part is, for example, not less than 0.5 mm, so that the reduction is made Frictional resistance of the spool during rapid motion.
  • the valve seat 91 and the housing are sealed by a sealing ring.
  • a gap G2 is formed between the valve seat and the mating component, which may include a housing or a valve sleeve.
  • the gap G2 is, for example, between 0.3 and 0.4 mm, for reducing the moment of inertia when the spool reciprocates, thereby reducing noise.
  • a power source such as a motor (not shown), is activated to cause rotation to the axial piston pump input.
  • the input spindle 2 of the axial piston pump rotates relative to the housing 1, and is installed in the middle under the joint action of the input spindle and the support bearing, the swash plate and the swash plate support bearing, and the swash plate limit ring.
  • the swash plate 5 on the obliquely curved section 22 does not rotate, but is spatially oscillated around the coincidence point A.
  • the oscillating imbalance of the swash plate is effectively offset.
  • the spherical oscillating motion of the swash plate 5 drives the connecting rod and the plunger 4 to reciprocate in the cylinder bore 101 of the cylinder block 10. It is to be noted that, due to the presence of the flare 512, the swash plate during the spherical oscillation of the swash plate 5 can be avoided. The ball head cavity interferes with the ball head and the connecting rod.
  • the axial piston pump works more smoothly, reduces operating noise and reduces equipment wear. Therefore, the need to provide two sets of bearings on the first straight line segment of the input spindle in the prior art is eliminated, and the problem of over-constraint of the input spindle is overcome.
  • the valve seat and the pump body retain the gap, the impact inertia of the spool reciprocating is reduced, so that the valve is reliable, the medium is adaptable, and the noise and vibration during operation are small.

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

Abstract

一种轴向柱塞泵，该轴向柱塞泵包括壳体（1）、可转动地安装在壳体（1）内并包括中间斜弯段（22）的输入主轴（2）、可转动地安装在中间斜弯段（22）上的斜盘（5）、一端通过球头（71）铰接到斜盘（5）上并且另一端设置有柱塞（4）的多个连杆（7）、以及具有柱塞（4）可往复运动地插入其中的缸孔（101）的缸体（10），其中缸体（10）相对于壳体（1）固定，随着输入主轴（2）的旋转斜盘（5）做空间球面摆动，且其中输入主轴（2）还包括第一直线段（21），第一直线段（21）通过轴承（31）可旋转地支撑在壳体（1）上，并且在第一直线段（21）上还设置有平衡环（25），平衡环（25）为偏心结构并且与输入主轴（2）一起旋转。通过设置偏心结构的平衡环（25），可以进一步抵消斜盘（5）的不平衡力矩，进一步降低整个轴向柱塞泵的振动和噪声。

Description

轴向柱塞泵 技术领域
本发明涉及轴向柱塞泵的领域，并尤其涉及一种适于泵送低粘度液体，如淡水或海水的轴向柱塞泵。
背景技术
柱塞泵是用于泵送流体的重要装置。它依靠柱塞在缸体的缸孔中往复运动，使密封工作容腔的容积发生变化来实现吸入和喷出。柱塞泵具有额定压力高、结构紧凑、效率高和流量调节方便等优点，被广泛应用于高压、大流量和流量需要调节的场合，诸如液压机、工程机械和船舶中。
柱塞泵包括轴向柱塞泵和径向柱塞泵两种代表性形式，并且轴向柱塞泵由于体积小等优点，而得到广泛应用。
传统的轴向柱塞泵包括缸体、在缸体内往复运动的柱塞以及斜盘。柱塞的一端在缸体内往复运动以吸入或喷出流体，而另一端例如通过滑靴抵靠在斜盘上并随着缸体转动而在斜盘上沿斜盘的圆周方向滑动。并且，可以通过调节斜盘的倾斜角度来实现变化的排量和压力的泵。
这种结构在用于具有高粘度的流体方面是有效的，但是，在要加压的流体为例如水的流体时，由于水的粘度低，润滑性差等，滑靴和斜盘之间的润滑性能差，由此限制了斜盘的倾斜角度，进而限制了泵的排量和压力的提高。
为了克服这个问题，在转让给本申请人的中国发明专利CN100362232C中，提出了一种适用于泵送低粘度流体的轴向柱塞泵，在这种轴向柱塞泵中，缸体相对于壳体保持固定，柱塞通过球头安装在斜盘上，斜盘可旋转地安装在旋转主轴的曲拐上，由此斜盘带动柱塞球面摆动，由此避免了斜盘和柱塞的滑靴之间的摩擦问题。但是，这个方案存在的问题在于旋转主轴为悬臂支撑，导致很大的不平衡力矩，使得在运行过程中，斜盘的摆动稳定性差，整个泵的振动大，导 致噪声、摩擦等问题。
为了克服这种不平衡力矩，在转让给本申请人的中国实用新型专利CN201739111U中，对上述轴向柱塞泵进行了改进，即，使得旋转主轴为两端支撑，在主轴的输入端附近采用两组轴承以增强对主轴的支撑，并且在斜盘的径向外侧设置有导向滑块，该导向滑块在壳体的相应部分上形成的导向滑槽配合，以导引斜盘的摆动。但是，这种方案仍没有无法彻底解决柱塞泵振动大、转动稳定性差、噪声和摩擦大等的问题，并且还带来导向滑块与导向滑槽的摩擦增大，进而降低了整个泵的寿命。另外，由于主轴在其输入端由两组轴承支撑，并且在主轴的相对端另外采用一组轴承支撑，使得主轴存在过约束的问题，由此，导致主轴中的应力过大，降低了主轴并进而整个泵的寿命。
上述两个专利通过引用整体结合于此。
因此，仍存在对这种轴向柱塞泵进一步改进的需要。
发明内容
为了解决上述问题，提出了本发明。本发明的一个目的在于提供一种轴向柱塞泵，该轴向柱塞泵特别适于泵送低粘度流体，如海水或淡水，并且可以具有良好的平衡特性，降低了泵的振动和噪声，并提高了泵的寿命。
根据本发明的一个方面，提供了一种轴向柱塞泵，该轴向柱塞泵包括壳体、可转动地安装在壳体内并包括中间斜弯段的输入主轴、可转动地安装在所述中间斜弯段上的斜盘、一端通过球头铰接到所述斜盘上并且另一端设置有柱塞的多个连杆、以及具有柱塞可往复运动地插入其中的缸孔的缸体，其中所述缸体相对于所述壳体固定，随着所述输入主轴的旋转所述斜盘做空间球面摆动，且其中所述输入主轴还包括第一直线段，所述第一直线段通过轴承可旋转地支撑在所述壳体上，并且在所述第一直线段上还设置有平衡环，所述平衡环为偏心结构并且与所述输入主轴一起旋转。
通过设置偏心结构的平衡环，可以进一步抵消所述斜盘的不平衡力矩，进一步降低整个轴向柱塞泵的振动和噪声。
有利地是，所述输入主轴的第一直线段的轴线与所述中间斜弯段的轴线的交点、所述斜盘的球面摆动中心以及所述多个连杆的球头的中心构成的圆的圆心重合在重合点(A)。
通过使得上述交点、摆动中心和圆心重合，可以抵消所述斜盘做空间球面摆动时的不平衡力矩，降低整个轴向柱塞泵的振动和噪声。
有利地是，还包括斜盘限转环，所述斜盘限转环一方面通过连接轴与所述斜盘可相对转动地连接，且所述斜盘限转环另一方面通过径向相对设置的销轴与所述壳体相连接使得所述斜盘限转环围绕所述销轴相对于所述壳体可摆动。
其中所述斜盘限转环的连接轴的轴线与所述销轴的轴线的交点与所述重合点重合。
通过使得斜盘限转环的交点与上述重合点重合，可以进一步抵消所述斜盘的不平衡力矩，进一步降低整个轴向柱塞泵的振动和噪声。
有利地是，还包括配流阀，所述配流阀包括阀座和安装在阀座内的吸入阀阀芯和排出阀阀芯，所述吸入阀阀芯和所述排出阀阀芯分别被偏压向所述阀座，其中，所述阀芯由耐腐蚀的高强度轻质材料制成，该材料例如为钛合金。
通过采用耐腐蚀和高强度轻质材料，使得阀芯可以抵抗诸如海水的腐蚀，并且可以减轻其重量，由此降低阀芯的运动惯量。
有利地是，每个所述阀芯的外周表面与所述阀座的相应配合表面之间形成有环状间隙，该环状间隙例如不小于0.5毫米。另外，所述阀座与相配合元件之间形成第二间隙，该第二间隙例如在0.3至0.4毫米。
通过设置上述环状间隙和第二间隙，可以降低阀芯往复运动时的冲击惯量。由此提高配流阀的工作可靠性，耐腐蚀性，介质适应性，并降低配流阀以及轴向柱塞泵工作时的振动和噪声。
附图说明
本发明的上述和其他特征、优点和技术优越性可以通过下面参照附图对本发明的优选实施方式的详细描述中理解到，图中：
图1是示出根据本发明的实施方式的轴向柱塞泵的主剖面图；
图2是示出图1所示的轴向柱塞泵的斜盘部分的部分剖面图；
图3是示出斜盘限转环的横截面图；
图4是示出配流阀组结构的剖面图；
图5是示出输入主轴及其上安装的平衡环的透视图；
图6是图5的剖面图。
具体实施方式
下面参照附图详细描述根据本发明的优选实施方式。要指出的是，该描述仅仅出于举例说明的目的而非限制，并且，本领域技术人员将明白本发明可以以多种方式来实施，而不应局限于在此描述的优选实施方式。
在下面的描述中，要指出的是，关于方向的描述，如外侧、内侧、上侧或下侧是参照附图中所示的方向来做出的，以便于解释和说明，但是本发明并不局限于此，而是可以根据所描述的部件或装置的具体应用情况或安装位置有所变化。
图1示出了根据本发明的实施方式的轴向柱塞泵的主剖面图。如图1所示，轴向柱塞泵(以下简称为泵)包括壳体1，输入主轴2通过轴承31和32可旋转地支撑在该壳体1上。具体地说，如图2和图3所示，输入主轴2包括第一直线段21、中间斜弯段22和第二直线段23，第一直线段21和第二直线段23成一条直线，且中间斜弯段22一体地设置在第一直线段21和第二直线段23之间。如图3所示，中间斜弯段22的轴线与第一和第二直线段21和22的轴线成15至40度的角度，该角度可以根据泵的期望流量和压力来改变。
输入主轴2的第一直线段21通过轴承31支撑在壳体1上，例如支撑在壳体1的端盖11上，该轴承31例如为滚珠轴承。但本发明并不局限于此，也可以采用其他类型的轴承。同时，输入主轴2的第二直线段23通过另一轴承32(也例如为滚珠轴承)也支撑在壳体1上。
中间斜弯段22例如可以包括两个不同直径部分，斜盘5例如通过两个不同规格的圆锥滚子轴承33可旋转地安装在中间斜弯段22 上。
如图5和图6所示，在所述输入主轴2的第一直线段21上，例如通过键24，安装有平衡环25，使得输入主轴2和平衡环25可以共同旋转。平衡环25包括轴向部分251和径向部分252，该轴向部分251套在输入主轴2的第一直线段21上，并且第一轴承3的内圈可以套在该轴向部分251的外圆周上。平衡环25的径向部分252为偏心形状，以在输入主轴2旋转过程中，抵消输入主轴2上的中间斜弯段22以及安装于中间斜弯段22上的斜盘带来的不平衡。
下面参照图2和图3描述轴向柱塞泵的斜盘5。如上面描述的，斜盘5通过两个圆锥滚子轴承33支撑在输入主轴2的中间斜弯段22上，使得斜盘5相对于输入主轴2的轴线倾斜15至40度的角度。斜盘5包括斜盘本体51和斜盘压盖52，斜盘本体51和斜盘压盖52例如通过螺钉连接到一起。斜盘本体51和斜盘压盖52分别在圆周方向上等间隔地形成有多个空腔，使得在斜盘本体51和斜盘压盖52组装到一起时，相对应的空腔拼合成球头腔，连杆的球头71容纳在每个球头腔中。
对于每个球头腔而言，如图2所示，例如，形成在斜盘本体51内的空腔为凹陷空腔，并且形成在斜盘压盖52内的空腔为贯通空腔，该贯通空腔在朝向缸体的一端上形成有扩口512。该凹陷空腔与贯通空腔拼合成球头腔。另外，在上述凹陷空腔和贯通空腔内分别内衬有例如由铜等制成的垫块513和523，所述垫块513和523配合，形成紧密包绕连杆的球头71的球形空腔，与球头71形成球铰配合，以允许球头71在内作球面旋转运动。
通过在球头腔内设置单独的垫块来与球头71形成球铰配合，与球头71直接与斜盘材料形成球铰配合相比，可以减小球头71的摩擦，并且在垫块被磨损时可以容易更换，降低了维护成本。
此外，为了平衡斜盘5在工作过程中的不平衡力矩，在斜盘5的外周侧设置有斜盘限转环8，该斜盘限转环8一方面例如通过连接轴81与斜盘5连接，使得斜盘限转环8和斜盘5可以围绕连接轴81的轴线相对转动，另一方面，如图3所示，斜盘限转环8通过两个相对 的销轴82与柱塞泵的壳体1可转动连接。销轴82与连接轴81在圆周方向上大致相差90度。该斜盘限转环8的具体结构在中国实用新型专利CN201739163U中描述，该专利因此通过引用整体结合于此。
另外，为了进一步消除斜盘5在转动过程中导致的不平衡力矩，输入主轴2、斜盘5、斜盘限转环8进一步构造成使得输入主轴2的穿过第一直线段21和第二直线段23的轴线与中间斜弯段22的轴线的交点、斜盘作球面摆动的中心、每个柱塞球头71的中心构成的圆的圆心、斜盘限转环8的销轴82和斜盘限转环与斜盘连接的连接轴81的相交点重合在一点，在图中以A标识并称作重合点，以下简称为四心重合。
继续参照图1，根据本发明的轴向柱塞泵包括多个连杆7，每个连杆7的一端通过球头71与斜盘5球铰接合，并且其另一端与柱塞4相连接。该柱塞4插入缸体10内的相应缸孔中101，以在连杆7的带动下在缸孔101内作往复运动。缸体10相对于壳体固定。
参照图4，在壳体1内还设置有配流阀9，该配流阀9选择性地将通向缸体的缸孔101的配流盘通道与柱塞泵的吸入通道和排出通道相连通。该配流阀包括阀座91、吸入阀阀芯92、吸入阀弹簧93、排出阀阀芯94、排出阀弹簧95。吸入阀弹簧93将吸入阀阀芯92偏压在阀座91上，以封闭泵的吸入通道96，排出阀弹簧95将排出阀阀芯94偏压在阀座91上以封闭泵的排出通道97。
上述吸入阀阀芯和排出阀阀芯可以采用耐腐蚀的高强度轻质材料，例如钛合金，制成，以减轻其重量，由此降低了阀芯的运动惯量。
如图4所示，吸入阀阀芯92和排出阀阀芯94分别安装成使得阀芯的外周面与相配合零件的内周面之间的环状缝隙G1例如不小于0.5毫米，使得减小阀芯在快速运动时的摩擦阻力。另外，阀座91和壳体之间通过密封圈密封。在配流阀装配到壳体中之后，阀座和相配合元件之间形成间隙G2，所述相配合元件可以包括壳体或阀套。该间隙G2例如在0.3至0.4毫米之间，用于降低阀芯往复运动时的冲击惯量，进而降低噪声。
下面简要描述根据本发明的轴向柱塞泵的工作方式。
在根据本发明的轴向柱塞泵工作时，动力源，例如电机(未示出)被启动，使得向轴向柱塞泵输入转动。
在电机的带动下，轴向柱塞泵的输入主轴2相对于壳体1转动，在输入主轴以及支撑轴承、斜盘和斜盘支撑轴承、斜盘限转环的共同作用下，安装在中间斜弯段22上的斜盘5不转动，而是绕重合点A做空间球面摆动。并且由于安装在输入主轴2的第一直线段21上的平衡环以及斜盘限转环的作用并且由于上面描述的四心重合，斜盘的摆动不平衡被有效抵消。
斜盘5的球面摆动带动连杆以及柱塞4在缸体10的缸孔101内往复运动，要指出的是，由于扩口512的存在，可以避免在斜盘5的球面摆动过程中斜盘的球头腔与球头和连杆干涉。
进一步如图4所示，当柱塞不动时，由于吸入阀弹簧和排出阀弹簧的偏压作用，在缸孔和柱塞前端与吸入阀之间形成密封空间。当柱塞向上运动时，在该密封空间内形成真空，当吸入阀阀芯92两侧的压力差大于吸入阀弹簧93的偏压力时，吸入阀阀芯92被克服吸入阀弹簧93的力向右移动，由此，打开吸入通道，吸入工作介质，例如水。当柱塞向下运动时，密封空间内的压力增大，使得吸入阀阀芯92被快速关闭，此时，该增大的压力克服排出阀弹簧94的偏压力而将排出阀阀芯93打开，由此将缸孔内的介质排出。如此往复，使得轴向柱塞泵吸入介质并将该介质加压后排出。
在本发明中，通过在输入主轴的第一直线段上设置平衡环，并且通过将斜盘等构件配置成四心重合，可以抵消在斜盘运动过程中的不平衡力矩，使得根据本发明的轴向柱塞泵更平稳地工作、降低了工作噪声并减小了设备的磨损。并由此消除了现有技术中在输入主轴的第一直线段上设置两组轴承的需要，克服了输入主轴的过约束的问题。
在本发明中，通过使得阀座和泵体保留间隙，降低了阀芯往复运动时的冲击惯量，使得配流阀工作可靠、介质适应性强、工作时的噪声和振动小。
尽管上面对本发明的优选实施方式进行的详细描述，但是鉴于上面的描述，本领域技术人员可以构想到各种改进和变型。因此，本发 明不应局限于上述具体的实施方式，本发明的保护范围仅由所附的权利要求及其等价物限定。

Claims (22)

  1. 一种轴向柱塞泵，该轴向柱塞泵包括壳体、可转动地安装在壳体内并包括中间斜弯段的输入主轴、可转动地安装在所述中间斜弯段上的斜盘、一端通过球头铰接到所述斜盘上并且另一端设置有柱塞的多个连杆、以及具有柱塞可往复运动地插入其中的缸孔的缸体，其中所述缸体相对于所述壳体固定，随着所述输入主轴的旋转所述斜盘做空间球面摆动，其中，所述输入主轴的主轴线与所述中间斜弯段的轴线的交点、所述斜盘的球面摆动中心、以及所述多个连杆的球头的中心构成的圆的圆心重合在重合点(A)。
  2. 如权利要求1所述的轴向柱塞泵，还包括斜盘限转环，所述斜盘限转环一方面通过连接轴与所述斜盘可相对转动地连接，且所述斜盘限转环另一方面通过径向相对设置的销轴与所述壳体相连接使得所述斜盘限转环围绕所述销轴相对于所述壳体可摆动。
  3. 如权利要求2所述的轴向柱塞泵，其中，所述斜盘限转环的连接轴的轴线与所述销轴的轴线的交点与所述重合点(A)重合。
  4. 如权利要求1所述的轴向柱塞泵，其中，所述斜盘形成有球头腔，每个所述连杆的球头容纳在所述球头腔内，以形成球铰连接。
  5. 如权利要求4所述的轴向柱塞泵，其中，所述球头腔的开口形成有扩口。
  6. 如权利要求5所述的轴向柱塞泵，其中，所述斜盘包括斜盘本体和斜盘压盖，所述斜盘本体内形成有多个凹陷空腔，而所述斜盘压盖内形成有相应的多个贯通空腔，使得在所述斜盘本体与所述斜盘压盖配合时，每个所述凹陷空腔与相对应的一个贯通空腔形成所述球头腔。
  7. 如权利要求6所述的轴向柱塞泵，其中，所述扩口形成在所述贯通空腔的一端。
  8. 如权利要求6所述的轴向柱塞泵，其中，在所述球头腔内容纳有垫块，所述垫块与所述球头紧密配合，以形成球铰连接。
  9. 如权利要求8所述的轴向柱塞泵，其中，所述垫块由铜制成。
  10. 如权利要求1所述的轴向柱塞泵，其中，所述输入主轴还包括第一直线段，所述第一直线段通过轴承可旋转地支撑在所述壳体上，并且在所述第一直线段上还设置有平衡环，所述平衡环为偏心结构并且与所述输入主轴一起旋转。
  11. 如权利要求10所述的轴向柱塞泵，其中，所述平衡环包括轴向部分和径向部分，所述轴向部分不可旋转地安装在所述第一直线段上使得所述平衡环与所述输入主轴一同旋转，所述径向部分为偏心形状。
  12. 如权利要求11所述的轴向柱塞泵，其中，所述输入主轴的第一直线段和所述第一平衡环通过第一轴承可旋转地支撑在所述壳体上。
  13. 如权利要求12所述的轴向柱塞泵，其中，所述输入主轴还包括与所述第一直线段成一条直线的第二直线段，所述中间斜弯段设置于所述第一直线段和所述第二直线段之间。
  14. 如权利要求13所述的轴向柱塞泵，其中，所述中间斜弯段的轴线相对于所述第一直线段和第二直线段的轴线倾斜15至40度。
  15. 如权利要求14所述的轴向柱塞泵，其中，在所述第二直线段设置有第二轴承，所述输入主轴通过该第二轴承可旋转地支撑在所述壳体上。
  16. 如权利要求1所述的轴向柱塞泵，还包括配流阀，所述配流阀包括阀座和安装在阀座内的吸入阀阀芯和排出阀阀芯，所述吸入阀阀芯和所述排出阀阀芯分别被偏压向所述阀座。
  17. 如权利要求16所述的轴向柱塞泵，其中，所述阀芯由耐腐蚀的高强度轻质材料制成。
  18. 如权利要求17所述的轴向柱塞泵，其中，所述高强度轻质材料是钛合金。
  19. 如权利要求16所述的轴向柱塞泵，其中，每个所述阀芯的外周表面与所述阀座的相应配合表面之间形成有环状间隙。
  20. 如权利要求19所述的轴向柱塞泵，其中，所述环状间隙不小于0.5毫米。
  21. 如权利要求16所述的轴向柱塞泵，其中，所述阀座与相配合元件之间形成第二间隙。
  22. 如权利要求21所述的轴向柱塞泵，其中，所述第二间隙在0.3至0.4毫米。
PCT/CN2017/080380 2016-04-13 2017-04-13 轴向柱塞泵 WO2017177936A1 (zh)

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CN109926801A (zh) * 2019-04-16 2019-06-25 四川坤成润科技有限公司 一种空芯柱塞的加工方法

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CN107989579A (zh) * 2017-12-27 2018-05-04 宁波合力机泵股份有限公司 一种潜井式多缸立式柱塞抽油泵动力端
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