WO2012152058A1 - 双缸柱塞泵 - Google Patents

双缸柱塞泵 Download PDF

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Publication number
WO2012152058A1
WO2012152058A1 PCT/CN2012/000598 CN2012000598W WO2012152058A1 WO 2012152058 A1 WO2012152058 A1 WO 2012152058A1 CN 2012000598 W CN2012000598 W CN 2012000598W WO 2012152058 A1 WO2012152058 A1 WO 2012152058A1
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WO
WIPO (PCT)
Prior art keywords
cylinder
plunger
pump
pump body
cylinders
Prior art date
Application number
PCT/CN2012/000598
Other languages
English (en)
French (fr)
Inventor
庄森
庄晨
禹茜
Original Assignee
Zhuang Sen
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zhuang Sen filed Critical Zhuang Sen
Publication of WO2012152058A1 publication Critical patent/WO2012152058A1/zh

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Classifications

    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—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
    • F04B53/14—Pistons, piston-rods or piston-rod connections

Definitions

  • the invention relates to a hydraulic drive, and more particularly to a two-cylinder plunger pump.
  • the hydraulic oil pumps visible on the market mainly include gear type, vane type and plunger type.
  • the gear pump has good self-priming ability, strong anti-pollution ability, simple structure, but the contact ratio of the meshing tooth surface is very large;
  • the vane pump has the advantages of long life, low noise, small flow and small volume.
  • the plunger pump is characterized by its compact structure, light weight and high working pressure. A wide range of applications.
  • the most widely used piston pumps on the market are mainly inclined and swashplate.
  • the swash plate type plunger pump mostly includes an outer pump body, a transmission shaft, a distribution plate, a cylinder block, a swash plate and a sliding shoe, wherein the cylinder body is non-rotatingly mounted on the transmission shaft, and the transmission shaft is used for the cylinder
  • the body is drivingly coupled to the driving device, the plunger is slidably inserted into the cylinder bore of the cylinder body at one end thereof, and the other end of the plunger has a ball head, and the sliding shoe is disposed on a side of the swash plate close to the cylinder body, on the sliding shoe Having a ball socket corresponding to the ball head on the plunger, the plunger is coupled with the corresponding ball socket through its ball head to be connected with the swash plate, and the ball head cooperates with the ball socket to form a universal joint, and the cylinder body and the distribution plate pass The spring is tightly fitted; when working, the driving device drives the cylinder to rotate through the transmission shaft.
  • the distribution plate has two circular arc-shaped through holes, and the two circular arc-shaped through holes are separated by a partition wall, and respectively communicate with the oil inlet and the oil outlet of the pump, and the plunger enters from the oil pump during the rotation of the cylinder. Inhalation of the transmission medium at the port, from the oil outlet of the oil pump A high pressure liquid is produced.
  • the oblique-axis type plunger pump is different from the swash plate type plunger pump only in that the swash plate is mounted on the transmission shaft, and an angle is formed between the transmission shaft and the axis of the cylinder block, and the transmission shaft drives the swash plate during operation. Movement, thereby realizing the telescopic movement of the plunger in the corresponding cylinder bore, thereby completing the pumping and draining process; the axial piston pump is widely used for its advantages of high efficiency, small radial size, compact structure, small size and light weight. It is widely used in hydraulic transmission systems for machine tools, metallurgy, forging and mining cranes. It is especially widely used in high-power hydraulic transmission systems.
  • the contact portion between the plunger and the shoe that is, the joint portion
  • the joint portion tends to be a weak link, which is extremely vulnerable and seriously restricts
  • the service life of the plunger pump since the driving device only drives one cylinder to rotate to cooperate with the plunger to complete the pumping action, the existing axial piston pump has a small flow rate and limited efficiency, which makes the present Some axial piston pumps are not suitable for applications where space is small and flow rates are high.
  • the two-cylinder plunger pump of the present invention adopts the following technical solutions: including a first cylinder body and a second cylinder block, the axis of the first cylinder body intersecting the axis of the second cylinder block at the first, the first Outside the two cylinders and forming a first angle, the plane in which the axes of the first and second cylinders are common is the first plane; the angle bisector of the first angle is the second plane; Having a first cylinder bore extending along an axial direction thereof, the second cylinder block has a second cylinder bore corresponding to the first cylinder bore, and the centerlines of each of the first cylinder bores and the corresponding second cylinder bore intersect a second plane, the first and second cylinders are drivingly connected by a plunger assembly, the plunger assembly includes two plungers, the adjacent ends of the two plungers are connected, and the other ends of the two plungers are respectively slidably inserted In the corresponding first and second cylinder bores.
  • the two-cylinder plunger pump further includes a first outer pump body and a second outer pump body, wherein the first cylinder body is coaxially coupled with a transmission shaft for driving connection with the driving device, and the first cylinder body passes through the
  • the transmission shaft is rotatably mounted on the first outer pump body
  • the second cylinder body is coaxially mounted with a rotating shaft
  • the second cylinder block is rotatably assembled to the second outer pump body through the rotating shaft.
  • the rotating shaft is screw-fitted with the second cylinder body, and the rotating shaft is rotatably assembled on the second outer pump body, and the corresponding end of the driving shaft and the rotating shaft is synchronously driven and connected by the reversing mechanism.
  • An adjacent end of the two plungers of the plunger assembly is hinged by a pin or connected by a ball joint, the axes of the pins being perpendicular to the first plane.
  • first cylinder away from the first outer pump body and one end of the second cylinder away from the second outer pump body are rotatably assembled with connecting rods, and the two connecting rods are respectively along the first and second cylinders
  • An axis is movably engaged with the first and second cylinders, and an adjacent end of the two connecting rods is hinged by an articulated shaft, an axis of the hinge shaft is perpendicular to the first plane, and the second cylinder is rotatably assembled
  • the two connecting rods are respectively provided with a supporting spring between the first and second cylinders;
  • the first outer pump body is fixedly equipped with a fixed distribution plate on a side close to the first cylinder body, and the second outer pump body is adjacent to the first
  • One side of the two-cylinder body is equipped with a movable distribution plate, and the movable distribution plate is mounted on the rotating shaft and is movably engaged with the second outer pump body around the hinge shaft, and the second outer pump body is adjacent to the side of the movable distribution plate and
  • the two-cylinder plunger pump further includes a pump cover, the pump cover is disposed outside the first and second cylinders and the plunger assembly and is fixedly sealed corresponding to the first and second outer pump bodies Cooperate.
  • An end of the pump cover adjacent to the second outer pump body is circumferentially disposed with a top screw for axially positioning the movable distribution plate.
  • the pump cover has an oil drain hole.
  • An adjacent end of the two plungers of the plunger assembly is connected by an angled connecting member having a joint respectively connected to the two plungers, the two joints having an angle between the two joints The included angle is equal to the first angle.
  • a two-cylinder plunger pump according to the present invention has the first and second cylinders, and the first and second cylinders have the first angle between the axes thereof, and the two cylinders pass The corresponding plunger assembly is connected, and the two plungers of the plunger assembly are respectively slidably inserted into the corresponding cylinder bores of the two cylinders, so when one of the first and second cylinders is driven, the other cylinder follows Rotation, ⁇ in the presence of the first angle, the distance between the corresponding cylinder bores on the two cylinders constantly changes, as the distance between the corresponding cylinder bores of the two cylinders constantly changes, the two plungers of the plunger assembly
  • the piston movement is performed in the corresponding cylinder bore to complete the pumping and draining operation; it can be seen that the double-cylinder plunger pump of the present invention can fully drive the two cylinders simultaneously by one drive during operation, thereby greatly increasing the flow rate thereof.
  • the work efficiency is improved, and the problem of
  • Figure 1 is a schematic view showing the structure of an embodiment of a two-cylinder plunger pump of the present invention
  • Figure 2 is a left side view of Figure 1;
  • Figure 3 is a cross-sectional view taken along line ⁇ - ⁇ of Figure 2;
  • Figure 4 is a schematic view of the structure of Figure 1 after removing the pump cover
  • Figure 5 is a schematic structural view of the first cylinder block of Figure 2;
  • Figure 6 is a left side view of Figure 5;
  • Figure 7 is a right side view of Figure 5;
  • Figure 8 is a perspective view of Figure 5;
  • Figure 9 is a schematic structural view of the plunger assembly of Figure 2.
  • Figure 10 is a schematic structural view of the distribution plate of Figure 2;
  • Figure 11 is a schematic structural view of the first outer pump body of Figure 2;
  • Figure 12 is a cross-sectional view taken along line ⁇ - ⁇ of Figure 11;
  • Figure 13 is a perspective view of Figure 11;
  • Figure 14 is a schematic structural view of the second outer pump body of Figure 2;
  • Figure 15 is a perspective view of Figure 14;
  • Figure 16 is a schematic structural view of the pump cover of Figure 1;
  • Figure 17 is a schematic view showing the structure of a second embodiment of the two-cylinder plunger pump of the present invention.
  • Figure 18 is a schematic view showing the structure of a third embodiment of the two-cylinder plunger pump of the present invention.
  • Figure 19 is a right side view of Figure 18;
  • Figure 20 is a cross-sectional view taken along line C-C of Figure 19;
  • Figure 21 is a schematic structural view of the movable distribution tray of Figure 20;
  • Figure 22 is a rear elevational view of Figure 21;
  • Figure 23 is a perspective view of the movable distribution tray of Figure 20;
  • Figure 24 is a schematic view showing the structure of the second outer pump body of Figure 20;
  • Figure 25 is a schematic view showing the structure of a fourth embodiment of the two-cylinder plunger pump of the present invention.
  • Figure 26 is a schematic view showing the structure of a fifth embodiment of the two-cylinder plunger pump of the present invention.
  • the first embodiment of the two-cylinder plunger pump of the present invention has a first cylinder block 101 and a second cylinder block 102.
  • the axis of the first cylinder block 101 and the axis of the second cylinder block 102 are The first and second cylinders intersect outside and form a first angle 103 (see FIG. 3), the first angle is 90 degrees; the axis of the first and second cylinders is the first angle 103
  • the two axes define a plane, that is, the two axes are on the same plane, and the plane is the first plane; the first cylinder 101 and the second cylinder 102 have the same structure and are all commercially available products.
  • a first cylinder bore 104 is circumferentially arranged on the first cylinder block 101.
  • the first cylinder bore 104 extends in the axial direction of the first cylinder block 101, and the second cylinder block 102 has a corresponding corresponding to the first cylinder bore 104.
  • the second cylinder bore is also uniformly distributed on the second cylinder block 102 in the circumferential direction, and the first cylinder bore 104 intersects the center line of the corresponding second cylinder bore in the second plane, that is, the first angle An angle bisector, the second plane comprising an angle bisector of the first angle 103 (ie, the angle bisector of the first angle 103 is on the second plane) and Vertically, the first cylinder block 101 and the second cylinder block 102 are drivingly coupled by a set of (9) plunger assemblies 105; each of the plunger assemblies 105 includes a plunger 106 at both ends and a connection between the two plungers 106.
  • the connecting member adopts an angular connecting member 107.
  • One of the two plungers of each plunger assembly 105 is slidably inserted into one first cylinder bore of the first cylinder block 101, and the other sliding member is inserted into the second cylinder block 102.
  • 101 is axially (coaxially) non-rotatingly equipped with a transmission shaft 108 for driving the first cylinder block 101 to the driving device;
  • the second cylinder block 102 is axially coupled with a rotating shaft 109, the first cylinder block
  • the first outer pump body 110 has a bearing housing 111.
  • the end surface of the bearing housing 111 has a flange connecting hole 112, and the outer peripheral surface of the bearing housing 111 has a method.
  • the blue plate 113 and the flange 113 are used for fixing the double cylinder plunger pump of the embodiment to the whole.
  • the inner hole of the bearing housing 111 is provided with a distribution plate 114, an inner circlip 115, a first bearing 116, a bearing spacer 117, and a first end from the inner end (the end close to the first cylinder 101) to the outer end.
  • the arc-shaped long hole, one of the two long holes is the oil pumping hole 124, and the other is the oil filling hole 125, the oil pumping hole 124 is electrically connected with the oil inlet hole 122, and the oil filling hole 125 is electrically connected with the oil outlet hole 123;
  • Each of the first cylinder bores 104 has a constricted structure at one end of the first outer pump body 110 (the prior art is not described again); the second cylinder block 102 is rotatably mounted on the second outer pump body 126 by the rotating shaft 109, The second outer pump body 126 is different from the first outer pump body 110 only in that the side of the first outer pump body 110 away from the distribution plate 114 is a transparent cover 120.
  • the outer cover of the body and the plunger assembly 105 is provided with a pump cover 128.
  • the shape of the pump cover 128 is adapted to the overall shape formed by the cooperation of the above-mentioned components.
  • the two ends of the pump cover 128 respectively have the first and second outer pumps.
  • the transmission shaft 108 is connected to the driving device, and the first cylinder block 101 is driven to rotate by the driving device, and the first cylinder block 101 is driven by the plunger assembly 105 to rotate the second cylinder 101.
  • the cylinder block 102 rotates, and the distance between the corresponding first cylinder bore and the second cylinder bore is constantly changed during the rotation of the first and second cylinder blocks, so that the plunger 106 of each plunger assembly 105 is in the corresponding cylinder bore.
  • the piston movement is carried out in order to realize the process of pumping oil and pumping oil in cooperation with the corresponding distribution plate.
  • the angle value of the first angle 103 may be greater than zero degrees less than 18 degrees; the plunger assembly 105 may be more than one, with an odd number between 5-9
  • the transmission shaft 108 and the corresponding end of the rotating shaft 109 are synchronously connected by a reversing mechanism, and the reversing mechanism can adopt a bevel gear or a worm gear device, and can also use the rotating shaft and the transmission shaft in use.
  • the rotating shaft 109 can also be rotatably mounted on the second cylinder block 102, in this case, the rotating shaft 109 is non-rotatingly assembled on the second outer pump body 126;
  • the plunger 106 of the 105 can also be rotatably mounted on the angular connecting member 107 by a bearing; an oil drain hole can also be formed in the pump cover 128 for discharging the leaked oil from the fitting of the plunger assembly 105 and the corresponding cylinder block.
  • the outer pump bodies are all commercially available, and can be additionally configured when used;
  • the connecting end of the two plungers of the plunger assembly 105 can also be a ball joint, which is worth noting,
  • the two plungers of the plunger assembly 105 The universal joint is used, but the movement of the universal joint during the operation of the pump is a perfect circle, and the force is stable, which still solves the problem of uneven force and easy damage of the universal joint of the conventional axial piston pump;
  • the connection between the two plungers of the plunger assembly can also be a hinged head, i.e., the two plungers of the plunger assembly are hingedly connected.
  • the second embodiment of the two-cylinder plunger pump of the present invention is different from the first embodiment in that the angle between the axes of the first and second cylinders is the first clamp.
  • the angle of the corner 103 is 120°.
  • the third embodiment of the present invention differs from the first embodiment in that: the first cylinder 101 is away from the first outer pump body 110 and the second cylinder 102 is away from the first One end of the outer pump body 126 is rotatably mounted with a connecting rod through a sliding bearing 132.
  • the connecting rod that is rotatably mounted on the first cylinder block 101 is a first connecting rod 133
  • the connecting rod mounted on the second cylinder block 102 is The second connecting rod 134
  • the first connecting rod 133 is movably engaged with the first cylinder block 101 in the axial direction of the first cylinder block 101
  • the second connecting rod 134 is movable along the axial direction of the second cylinder block 102 and the second cylinder block 102.
  • an adjacent end of the first and second connecting rods is hinged by an hinge shaft 135, an axis of the hinge shaft 135 and the first plane Vertically, the adjacent ends of the plungers of the plunger assembly 105 are hinged by the pin 136, and the axis of the pin 136 is parallel to the axis of the hinge shaft 135; the other ends of the first and second connecting rods respectively away from the connecting ends thereof correspond to 1.
  • a support spring 137 is mounted between the second cylinders.
  • the support spring 137 is used for tightening the first and second cylinders so that the two cylinders are in close contact with the corresponding distribution plates, and the second outer pump body 126
  • the inner side surface is a curved surface centered on the axis of the hinge shaft 135
  • the distribution plate mounted on the second cylinder block 102 is a movable distribution plate 138
  • the side of the movable distribution plate 138 near the second outer pump body 126 has an arc.
  • the movable distribution plate 138 can be sealingly engaged with the inner wall surface of the second outer pump body 126, and on the other hand, can be engaged with the second outer pump body 126 with the axis of the hinge shaft 135 as the rotation axis.
  • the movable distribution plate 138 has a central hole 139 and is sleeved on the rotating shaft 109 through the central hole 139.
  • the inner surface of the second outer pump body 126 has a guiding hole 140 for guiding cooperation with the rotating shaft 109.
  • the guiding direction and the rotating shaft 109 are close to the second outer pump
  • One end of the body 126 is in the same direction of movement of the hinge shaft 135.
  • the pump cover 128 has a space for the second cylinder 102 to move around the hinge shaft 135 and is used to limit the movable distribution plate by pressing the movable distribution plate.
  • the position of the bit tightens the screw 141.
  • the rotating shaft is rotatable about the axis of the hinge shaft, thereby driving the corresponding movement of the second cylinder, changing the angle between the first and second cylinders, thereby changing the first and second cylinders.
  • the distance between the corresponding two cylinder bores changes the movable stroke of the two plungers of the plunger assembly in the corresponding cylinder bores, and finally achieves the purpose of adjusting the flow rate of the double cylinder plunger pump of the present invention; wherein the support spring is The first angle is also changed to compensate for the relative displacement between the drive shaft and the shaft.
  • the adjacent ends of the two plungers of the plunger assembly may also be connected by a ball joint; the support spring may also be a gas spring or a hydraulic spring.
  • the fourth embodiment of the two-cylinder plunger pump of the present invention is different from the third embodiment in that the second outer pump body 126 has no curved surface and a guide hole structure. 1.
  • the angle between the axes of the second cylinders is 120°, and the flow rate of the two-cylinder plunger pump of the embodiment is not adjustable.
  • Embodiment 4 of the two-cylinder plunger pump of the present invention differs from Embodiment 3 only in that the two plungers of the plunger assembly and the first and second connecting rods are Connected by ball joints 131.
  • the double-cylinder plunger pump of the present invention can also drive the plunger assembly to move by supplying liquid to the cylinder bore of the cylinder to drive the drive shaft and the shaft to rotate.
  • the double cylinder plunger of the present invention The pump is used as a hydraulic motor; in addition, the double-cylinder plunger pump of the present invention can also be used as a compressor of a refrigerator, and since the double-cylinder plunger pump portion of the present invention has the hinge structure of the existing refrigerator compressor, it can be greatly reduced. The vibration and noise during small work greatly improve the working performance of the refrigerator; the double cylinder plunger pump of the present invention can also be used as a gas pump.

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

Description

双缸柱塞泵 技术领域
本发明涉及液压驱动装置， 尤其是一种双缸柱塞泵。
背景技术
目前， 市场上可见的液压油泵主要有齿轮式、 叶片式和柱塞式三种。 一般来说， 齿轮泵 的自吸能力好， 抗污染能力强， 结构简单， 但是其啮合齿面的接触比功很大； 叶片泵具有寿 命长、 噪音低、 流量均勾及体积小等优点， 但对介质的污染较为敏感， 又因叶片甩出力、 吸 入速度和磨损等因素的影响， 其转速受到限制且密封效果较差； 柱塞泵则因为其结构紧凑、 重量轻、 工作压力高等特点得到了广泛的应用。 目前市场上应用最为广泛的柱塞泵主要有斜 轴式和斜盘式两种。 斜盘式柱塞泵大都包括外泵体、 传动轴、 配流盘、 缸体、 斜盘和滑靴， 其中所述缸体止旋装配于所述传动轴上， 传动轴用于将所述缸体与驱动装置传动连接， 柱塞 以其一端滑动插装于缸体的缸孔中， 柱塞另一端具有球头， 滑靴设置于所述斜盘靠近缸体的 一侧上， 滑靴上具有与柱塞上的球头对应的球窝， 柱塞通过其球头与对应的球窝配合从而与 斜盘连接， 所述球头与球窝配合形成万向节， 缸体与配流盘通过弹簧顶紧配合； 工作时， 驱 动装置通过传动轴带动缸体转动， 由于斜盘的盘面相对于缸体端面是倾斜的， 所以柱塞在对 应缸孔中做往复运动， 由配流盘配液， 配流盘上具有两个圆弧形的通孔， 两圆弧形通孔由隔 墙隔开， 分别与泵的进油口、 出油口连通， 缸体转动的过程中柱塞从油泵的进油口处吸入传 输介质， 从油泵的出油口输出高压液体。 斜轴式柱塞泵与斜盘式柱塞泵的区别仅在于所述斜 盘是装配于所述传动轴上，传动轴与缸体的轴线之间具有夹角，工作时传动轴带动斜盘运动， 从而实现柱塞在对应缸孔中的伸縮运动， 进而完成抽、 排油过程； 轴向柱塞泵以其效率高、 径向尺寸小、 结构紧凑、 体积小、 重量轻等优点而广泛应用于机床、 冶金、 锻压、 矿山起重 机的液压传动系统中， 特别广泛的应用于大功率的液压传动系统中； 但是， 我们不难看出， 不论是斜轴式柱塞泵还是斜盘式柱塞泵， 其柱塞与滑靴的连接处形成的万向节的运动轨迹均 为椭圆形， 其运行不平稳， 具体的说， 即当所述万向节运动至所述其椭圆形轨迹的长轴的两 端时， 万向节处受到的阻力急剧增加， 因此在实际生产中， 柱塞与滑靴的接触部， 即万向节 处往往成为薄弱环节， 极易损坏， 严重制约着轴向柱塞泵的使用寿命;另外， 由于是一个驱动 装置只带动一个缸体旋转来与柱塞配合完成抽油动作， 因此现有轴向柱塞泵的流量较小， 效 率有限， 这使得现有的轴向柱塞泵在一些空间较小且所需流量较大的场合不能适用。
发明内容
1
确认本 本发明的目的在于提供一种双缸柱塞泵， 以解决现有轴向柱塞泵流量小的问题。
为了解决上述问题，本发明的双缸柱塞泵采用以下技术方案： 包括第一缸体和第二缸体, 所述第一缸体的轴线与第二缸体的轴线相交于第一、 第二缸体之外且构成第一夹角， 第一、 第二缸体的轴线共同所在的平面为第一平面； 所述第一夹角的角平分面为第二平面； 第一缸 体上具有沿其轴线方向延伸的第一缸孔， 第二缸体上具有与所述第一缸孔对应的第二缸孔， 各第一缸孔与对应的第二缸孔的中心线均相交于第二平面， 第一、 第二缸体通过柱塞组件传 动连接， 所述柱塞组件包括两柱塞， 所述两柱塞相邻的一端连接， 两柱塞各自的另一端分别 滑动插装于对应的第一、 第二缸孔中。
所述双缸柱塞泵还包括第一外泵体和第二外泵体， 所述第一缸体上同轴止旋装配有用于 与驱动装置传动连接的传动轴， 第一缸体通过所述传动轴转动装配于第一外泵体上， 所述第 二缸体同轴装配有转轴， 第二缸体通过所述转轴转动装配于所述第二外泵体上。
所述的转轴与所述的第二缸体止旋配合， 转轴转动装配于第二外泵体上， 所述传动轴与 转轴的对应端通过换向机构同步传动连接。
所述柱塞组件的两柱塞相邻的一端通过销轴铰接或通过球头万向节连接， 所述各销轴的 轴线与所述第一平面垂直。
所述第一缸体远离所述第一外泵体的一端和第二缸体远离所述第二外泵体的一端均转动 装配有连接杆， 两连接杆分别沿第一、 第二缸体的轴线与第一、 第二缸体活动配合， 所述两 连接杆相邻的一端通过铰接轴铰接， 所述铰接轴的轴线与所述第一平面垂直， 所述第二缸体 转动装配于转轴上， 两连接杆分别与第一、 第二缸体之间顶装有支撑弹簧； 第一外泵体靠近 第一缸体的一侧固定装配有固定配流盘， 第二外泵体靠近第二缸体的一侧止旋装配有活动配 流盘， 活动配流盘装配于转轴上且绕所述铰接轴与第二外泵体活动配合， 第二外泵体靠近活 动配流盘的一侧与配流盘的对应端面滑动密封配合。
所述双缸柱塞泵还包括泵罩， 所述泵罩罩设于所述第一、 第二缸体及柱塞组件的外部并 与所述的第一、 第二外泵体对应固定密封配合。
所述泵罩靠近所述第二外泵体的一端于周向上设置有用于将所述活动配流盘顶紧定位的 顶紧丝杆。
所述的泵罩上具有放油孔。
所述柱塞组件的两柱塞相邻的一端通过一角形连接件连接， 所述角形连接件具有分别与 两柱塞连接的接头， 所述两接头之间具有夹角， 两接头之间的夹角与所述第一夹角相等。
所述的柱塞组件的个数为奇数。 ώ于本发明的双缸柱塞泵具有所述第一、 第二缸体， 且所述第一、 第二缸体的轴线之间 具有所述第一夹角， 所述的两缸体通过对应的柱塞组件传动连接， 柱塞组件的两柱塞分别滑 动插装于两缸体对应的缸孔中， 因此当驱动第一、 第二缸体中的一个时， 另一个缸体随之转 动， ώ于第一夹角的存在， 两缸体上对应的缸孔之间的距离不断变化， 随着两缸体相应的缸 孔之间的距离的不断变化， 柱塞组件的两柱塞在对应的缸孔中做活塞运动， 从而完成抽、 排 油动作； 可见， 本发明的双缸柱塞泵在工作时完全可通过一个驱动带动两缸体同时做功， 大 大的增加了其流量， 提高了工作效率， 解决了现有的轴向柱塞泵的流量小、 效率低的问题。 附图说明
图 1是本发明的双缸柱塞泵的一种实施例的结构示意图；
图 2是图 1的左视图；
图 3是图 2的 Α-Α剖视图；
图 4是图 1中去除泵罩后的结构示意图；
图 5是图 2中第一缸体的结构示意图；
图 6是图 5的左视图；
图 7是图 5的右视图；
图 8是图 5的立体图；
图 9是图 2中柱塞组件的结构示意图；
图 10是图 2中配流盘的结构示意图；
图 11是图 2中第一外泵体的结构示意图；
图 12是图 11的 Β-Β剖视图；
图 13是图 11的立体图；
图 14是图 2中第二外泵体的结构示意图；
图 15是图 14中的立体图；
图 16是图 1中泵罩的结构示意图；
图 17是本发明的双缸柱塞泵的实施例 2的结构示意图；
图 18是本发明的双缸柱塞泵的实施例 3的结构示意图；
图 19是图 18的右视图；
图 20是图 19的 C-C剖视图；
图 21是图 20中的活动配流盘的结构示意图；
图 22是图 21的后视图； 图 23是图 20中的活动配流盘的立体图；
图 24是图 20中的第二外泵体的结构示意图；
图 25是本发明的双缸柱塞泵的实施例 4的结构示意图；
图 26是本发明的双缸柱塞泵的实施例 5的结构示意图。
具体实施方式
本发明的双缸柱塞泵的实施例 1， 如图 1-16所示， 具有第一缸体 101及第二缸体 102， 第一缸体 101的轴线与第二缸体 102的轴线在第一、 第二缸体之外相交并构成第一夹角 103 (见图 3 )， 第一夹角为 90度； 第一、 第二缸体的轴线即为所述第一夹角 103的边， 同时所 述两轴线确定一平面， 即所述两轴线在同一个平面上， 所述平面为第一平面； 第一缸体 101 与第二缸体 102的结构相同且均为市购品； 第一缸体 101上沿圆周方向均布有第一缸孔 104， 第一缸孔 104沿第一缸体 101的轴线方向延伸， 第二缸体 102上具有与第一缸孔 104对应的 第二缸孔， 第二缸孔同样沿圆周方向均布于第二缸体 102上， 第一缸孔 104与对应的第二缸 孔的中心线相交于第二平面， 即第一夹角的角平分面， 所述第二平面包含第一夹角 103的角 平分线 （即第一夹角 103的角平分线在第二平面上） 且与第一平面垂直， 第一缸体 101与第 二缸体 102通过一组（9个）柱塞组件 105传动连接； 各柱塞组件 105均包括两端的柱塞 106 及两柱塞 106之间的连接件， 所述连接件采用角形连接件 107， 各柱塞组件 105的两柱塞中 的一个滑动插装于第一缸体 101的一个第一缸孔中， 另一个滑动插装于第二缸体 102与该第 一缸孔对应的第二缸孔中； 柱塞组件 105的两柱塞在第一、 第二缸体的转动过程中分别在对 应缸体的缸孔做活塞运动； 第一缸体 101沿轴线（同轴）止旋装配有传动轴 108， 传动轴 108 用于将第一缸体 101与驱动装置传动连接； 第二缸体 102沿轴线止旋装配有转轴 109， 第一 缸体 101通过传动轴 108转动装配于第一外泵体 110上，第一外泵体 110具有轴承座 111，轴 承座 111的端面上具有法兰连接孔 112，轴承座 111的外周面上还具有法兰盘 113，法兰盘 113 用于将本实施例的双缸柱塞泵整体固定于使用设备上， 轴承座 111 的内孔中从内端 （靠近第 一缸体 101的一端） 至外端依次设置有配流盘 114、 内弹性挡圈 115、 第一轴承 116、 轴承隔 套 117、 第二轴承 118、 油封 119、 透盖 120及外弹性挡圈 121 ; 轴承座 111的外周还分别具 有进油孔 122和出油孔 123， 配流盘 114 (市购品）上具有互相隔开的两圆弧形长孔， 两长孔 中的一个为抽油孔 124， 另一个为注油孔 125， 抽油孔 124与进油孔 122导通连接， 注油孔 125与出油孔 123导通连接； 各第一缸孔 104靠进第一外泵体 110的一端具有缩口结构 （现 有技术， 不再赘述）； 第二缸体 102通过转轴 109转动装配于第二外泵体 126上， 第二外泵体 126与第一外泵体 110的区别仅在于第一外泵体 110远离配流盘 114的一侧为透盖 120，透盖 120上具有用于供传动轴 108通过的通孔， 而第二外泵体 126远离对应配流盘的一侧通过一 闷盖 127密封； 传动轴和转轴各自互相靠近的一端均设置有弹性卡簧 150， 弹性卡簧 150— 方面用于防止第一、 第二缸体从传动轴、 转轴上脱落， 另一方面用于将两缸体压紧于对应的 配流盘上， 第一、 第二缸体及柱塞组件 105的外部罩设有泵罩 128， 泵罩 128的形状与上述 各部件配合后形成的整体的形状适配， 泵罩 128的两端分别具有与第一、 第二外泵体上的法 兰连接孔对应的螺纹孔 129， 泵罩 128与第一、 第二外泵体 126通过螺钉连接并压装有密封 圈 130。 本实施例的双缸柱塞泵工作时， 将传动轴 108与驱动装置连接， 通过驱动装置驱动 第一缸体 101做旋转运动， 第一缸体 101转动过程中通过柱塞组件 105带动第二缸体 102转 动， 对应的第一缸孔与第二缸孔之间的距离在第一、 第二缸体的转动过程中不断变化， 因此 各柱塞组件 105的柱塞 106在对应的缸孔中做活塞运动， 以此在对应配流盘的配合下来实现 抽油和泵油的过程。该实施例中，所述的第一夹角 103的角度数值在大于零度小于 18度的范 围内皆可； 所述的柱塞组件 105为一个以上皆可， 以 5-9之间的奇数个为最优； 还可以将传 动轴 108与转轴 109的对应端通过换向机构同步传动连接， 所述换向机构可以采用锥齿轮或 涡轮蜗杆装置， 还可以在使用时将转轴与传动轴均与对应驱动装置同步传动连接； 所述转轴 109还可以转动装配于所述第二缸体 102上， 此种情况下将转轴 109止旋装配于第二外泵体 126上； 所述各柱塞组件 105的柱塞 106还可以通过轴承转动装配于角形连接件 107上； 还 可以在泵罩 128上开设放油孔，用以将从柱塞组件 105与对应缸体配合处的漏出的积油放出； 所述的各外泵体均为市购品， 使用时均可另外配置； 所述柱塞组件 105的两柱塞的邻端的连 接件还可以是球头万向节， 值得注意的是， 此处虽然柱塞组件 105的两柱塞是采用万向节连 接， 但是万向节在泵运转时的运动轨迹是正圆形， 受力平稳， 仍然解决了传统轴向柱塞泵的 万向节的受力不均、 易损坏的问题； 当然， 在其它实施例中， 柱塞组件的两柱塞之间的连接 件还可以是铰接头， 即柱塞组件的两柱塞以铰接的方式连接。
本发明的双缸柱塞泵的实施例 2， 如图 17所示， 本实施例与实施例 1的区别仅在于， 所 述第一、 第二缸体的轴线的夹角， 即第一夹角 103的角度为 120° 。
本发明的实施例 3， 如图 18-24所示， 本实施例与实施例 1 的区别在于： 所述第一缸体 101远离第一外泵体 110的一端和第二缸体 102远离第二外泵体 126的一端均通过滑动轴承 132转动装配有连接杆， 其中转动装配于第一缸体 101上的连接杆为第一连接杆 133， 装配于 第二缸体 102上的连接杆为第二连接杆 134， 第一连接杆 133沿第一缸体 101的轴线方向与 第一缸体 101活动配合， 第二连接杆 134沿第二缸体 102的轴线方向与第二缸体 102活动配 合； 第一、 第二连接杆相邻的一端通过铰接轴 135铰接， 铰接轴 135的轴线与所述第一平面 垂直， 柱塞组件 105的两柱塞的邻端通过销轴 136铰接， 销轴 136的轴线与铰接轴 135的轴 线平行； 第一、 第二连接杆各自远离二者连接端的另一端对应与第一、 第二缸体之间顶装有 支撑弹簧 137， 支撑弹簧 137用于顶紧第一、 第二缸体， 以使得两缸体与对应的配流盘紧贴 配合，第二外泵体 126的内侧面为以铰接轴 135的轴线为中心线的弧面，装配于第二缸体 102 上的配流盘为活动配流盘 138， 活动配流盘 138靠近第二外泵体 126的一侧具有弧面， 活动 配流盘 138通过其弧面一方面可与第二外泵体 126的内壁面密封配合， 另一方面可以以铰接 轴 135的轴线为转动轴线与第二外泵体 126之间活动配合，活动配流盘 138上具有中心孔 139 并通过其中心孔 139套设于转轴 109上， 第二外泵体 126的内侧面上具有用于与转轴 109导 向配合的导向孔 140， 导向孔 140的导向方向与转轴 109靠近第二外泵体 126的一端绕铰接 轴 135的活动方向相同， 泵罩 128内具有用于供第二缸体 102绕铰接轴 135活动的空间及用 于通过顶压活动配流盘来对第活动配流盘进行限位的顶紧丝杆 141。 本实施例中， 所述的转 轴可绕铰接轴的轴线转动， 从而带动第二缸体相应的移动， 改变第一、第二缸体之间的夹角， 进而改变第一、 第二缸体上对应的两缸孔之间的距离， 改变柱塞组件的两柱塞在对应缸孔中 的活动行程， 最终达到调节本发明的双缸柱塞泵的流量的目的； 其中所述支撑弹簧在改变第 一夹角时还起到补偿传动轴和转轴之间的相对位移量的作用。 本实施例中， 所述的柱塞组件 的两柱塞的邻端还可以通过球头万向节连接；所述的支撑弹簧还可以采用气弹簧或液压弹簧。
本发明的双缸柱塞泵的实施例 4， 如图 25所示， 本实施例与实施例 3的区别仅在于， 所 述的第二外泵体 126上没有弧面及导向孔结构， 第一、 第二缸体的轴线之间的夹角 （第一夹 角） 为 120° ， 本实施例的双缸柱塞泵的流量不可调节。
本发明的双缸柱塞泵的实施例 4， 如图 26所示， 本实施例与实施例 3的区别仅在于， 所 述柱塞组件的两柱塞之间及第一、 第二连接杆之间通过球头万向节 131连接。
本发明的双缸柱塞泵在使用时还可通过向缸体的缸孔中供液来驱动柱塞组件活动， 从而 驱动传动轴和转轴转动， 此种情况下， 本发明的双缸柱塞泵作为液压马达使用； 另外， 本发 明的双缸柱塞泵还可用作冰箱的压缩机， 由于本发明的双缸柱塞泵部具有现有冰箱压缩机的 铰链结构， 因此可大大的减小工作时的震动及噪音， 大大的改善冰箱的工作性能； 本发明的 双缸柱塞泵还可以作为气泵来使用。

Claims

WO 2012/152058 权 利 要 求 书 PCT/CN2012/000598
1. 双缸柱塞泵， 包括第一缸体、 第二缸体和分别与所述第一、 第二缸体对应的配流盘， 其特 征在于： 所述第一缸体的轴线与第二缸体的轴线相交于第一、第二缸体之外且构成第一夹角， 第一、 第二缸体的轴线共同所在的平面为第一平面； 所述第一夹角的角平分面为第二平面； 第一缸体上具有沿其旋转轴线方向延伸的第一缸孔， 第二缸体上具有与所述第一缸孔一一对 应的第二缸孔， 所述相对应的第一缸孔与第二缸孔的中心线的交点均位于第二平面上， 第一、 第二缸体通过柱塞组件传动连接， 所述柱塞组件包括滑动插装于对应的第一、 第二缸孔中的 两柱塞， 所述两柱塞相邻的一端伸出各自所在的缸孔， 两柱塞伸出对应缸孔的一端通过一个 用于在两缸体的转动过程中使该两柱塞于各自所在的缸孔中做伸缩运动的连接件传动连接。
2. 根据权利要求 1所述的双缸柱塞泵， 其特征在于： 还包括第一外泵体和第二外泵体， 所述 第一缸体上同轴止旋装配有用于与驱动装置传动连接的传动轴， 第一缸体通过所述传动轴转 动装配于第一外泵体上， 所述第二缸体同轴装配有转轴， 第二缸体通过所述转轴转动装配于 所述第二外泵体上。
3. 根据权利要求 2所述的双缸柱塞泵，其特征在于：所述的转轴与所述的第二缸体止旋配合， 转轴转动装配于第二外泵体上， 所述传动轴与转轴的对应端通过换向机构同步传动连接。
4. 根据权利要求 2所述的双缸柱塞泵， 其特征在于： 所述柱塞组件的两柱塞相邻的一端通过 销轴铰接或通过球头万向节连接， 所述各销轴的轴线与所述第一平面垂直。
5. 根据权利要求 4所述的双缸柱塞泵， 其特征在于： 所述第一缸体远离所述第一外泵体的一 端和第二缸体远离所述第二外泵体的一端均转动装配有连接杆， 两连接杆分别沿第一、 第二 缸体的轴线与第一、 第二缸体活动配合， 所述两连接杆相邻的一端通过铰接轴铰接， 所述铰 接轴的轴线与所述第一平面垂直， 所述第二缸体转动装配于转轴上， 两连接杆分别与第一、 第二缸体之间顶装有支撑弹簧； 第一外泵体靠近第一缸体的一侧固定装配有固定配流盘， 第 二外泵体靠近第二缸体的一侧止旋装配有活动配流盘， 活动配流盘装配于转轴上且绕所述铰 接轴与第二外泵体活动配合， 第二外泵体靠近活动配流盘的一侧与配流盘的对应端面滑动密 封配合。
6. 根据权利要求 5所述的双缸柱塞泵，其特征在于：还包括泵罩，所述泵罩罩设于所述第一、 第二缸体及柱塞组件的外部并与所述的第一、 第二外泵体对应固定密封配合。
7. 根据权利要求 6所述的双缸柱塞泵， 其特征在于： 所述泵罩靠近所述第二外泵体的一端于 周向上设置有用于将所述活动配流盘顶紧定位的顶紧丝杆。
8. 根据权利要求 6所述的双缸柱塞泵， 其特征在于： 所述的泵罩上具有放油孔。
9. 根据权利要求 1所述的双缸柱塞泵， 其特征在于： 所述柱塞组件的两柱塞相邻的一端通过 一角形连接件连接， 所述角形连接件具有分别与两柱塞连接的接头， 所述两接头之间具有夹 角， 两接头之间的夹角与所述第一夹角相等。
10. 根据权利要求 1所述的双缸柱塞泵， 其特征在于： 所述的柱塞组件的个数为奇数。
PCT/CN2012/000598 2011-05-06 2012-05-03 双缸柱塞泵 WO2012152058A1 (zh)

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CN102162434B (zh) * 2011-05-06 2014-03-26 庄森 双缸柱塞泵
CN103061876B (zh) * 2013-01-25 2015-05-20 庄森 内燃机
CN109026379B (zh) * 2018-08-01 2019-10-29 重庆交通大学 双转子变循环稳燃活塞发动机
CN108979996B (zh) * 2018-08-01 2019-12-03 重庆交通大学 液压型双转子活塞驱动装置
CN109057961B (zh) * 2018-08-01 2019-12-20 重庆交通大学 双转子变循环爆燃活塞发动机
CN108979856B (zh) * 2018-08-01 2020-06-12 重庆交通大学 双转子活塞驱动装置
CN108979995B (zh) * 2018-08-01 2019-12-03 重庆交通大学 气动型双转子活塞驱动装置
CN109667740B (zh) * 2018-11-20 2021-03-02 重庆交通大学 双转子双向变量泵或马达
CN109630646B (zh) * 2018-11-20 2021-02-23 重庆交通大学 无级液压变速器
CN117823380B (zh) * 2023-12-19 2024-05-28 宁波钱湖石油设备有限公司 一种高寿命的智能化柱塞泵

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