WO2013152568A1 - 柱塞泵 - Google Patents

柱塞泵 Download PDF

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Publication number
WO2013152568A1
WO2013152568A1 PCT/CN2012/079099 CN2012079099W WO2013152568A1 WO 2013152568 A1 WO2013152568 A1 WO 2013152568A1 CN 2012079099 W CN2012079099 W CN 2012079099W WO 2013152568 A1 WO2013152568 A1 WO 2013152568A1
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WO
WIPO (PCT)
Prior art keywords
cylinder
piston
crankshaft
plunger pump
connecting rod
Prior art date
Application number
PCT/CN2012/079099
Other languages
English (en)
French (fr)
Inventor
胡传术
Original Assignee
Hu Chuanshu
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 Hu Chuanshu filed Critical Hu Chuanshu
Publication of WO2013152568A1 publication Critical patent/WO2013152568A1/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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical

Definitions

  • the invention relates to the field of hydraulic devices.
  • the drainage pumps used in large coal mines, iron ore mines, gold mines, etc. at home and abroad are all above 200 m3/hr. Therefore, the requirements for flow, head and motor power of large displacement pumps are high, and the drainage flow is large.
  • the demand for energy-saving pumps with high lift and low motor power is huge.
  • the V-type plunger pump announced in the announcement although it can meet the market demand for high flow, high lift and small motor requirements.
  • the V-shaped structure of the pump makes the pump symmetrical two rows increase the number of plungers to achieve
  • the technical problem solved by the present invention is to provide a plunger pump which has a smaller footprint and is more flexible in use.
  • the technical solution adopted by the invention is a plunger pump, wherein at least two cranks are arranged on the crankshaft, a connecting rod is connected to the crank, and the other end of the connecting rod drives a piston to move up and down in the piston cylinder, wherein:
  • the connecting rod, the piston and the piston cylinder are at least two groups, each group consisting of three, and each of the three links is set on the same crank, and the axes of the three piston cylinders of each group are not in the same plane.
  • Each set of piston cylinders includes a first cylinder block, a second cylinder block and a third cylinder block, the angle between the axis of the first cylinder block and the second cylinder block and the vertical direction is an acute angle, and the second cylinder block is located at the first cylinder block Between the second cylinder and the second cylinder, the second cylinder axis remains vertical.
  • the angle between the axes of the first cylinder and the second cylinder and the vertical direction is not more than 40°, and the three piston cylinders are spirally arranged along the crankshaft axis.
  • the crank is 3 to 6.
  • Each cylinder is provided with a suction chamber and a drainage chamber.
  • a main shaft supporting journal is disposed between each of the cranks of the crankshaft, and an outer diameter of the main shaft supporting journal is not less than a crankshaft diameter.
  • the utility model has the advantages that the utility model has the advantages of small occupied area and is suitable for use in a small space; the strength of the crankshaft is larger and the service life is longer; the high hardness, high wear resistance and hydrolysis resistance of the sealing member are better; The savings in pump transportation, installation, and motor power have also resulted in significant reductions in pumping costs, directly saving users a significant amount of additional expense.
  • Figure 1 is a perspective view of the present invention.
  • Figure 2 is a top plan view of the plunger pump of the present invention.
  • Figure 3 is a left side view corresponding to Figure 1.
  • Figure 4 is a cross-sectional view taken along line A-A of Figure 2;
  • Figure 5 is a cross-sectional view taken along line B-B of Figure 2;
  • Figure 6 is a partial enlarged view of the C area of Figure 4.
  • the figures are marked as: 1-first cylinder, 2-second cylinder, 3-third cylinder, 4-crankshaft, 5-bend, 6-link, 7-axis support shaft diameter.
  • the piston cylinder of the plunger pump of the present invention is divided into three groups, three cylinders each, which are a first cylinder 1, a second cylinder 2 and a third cylinder 3, respectively.
  • the axis of the cylinder 2 is a vertical direction, and the moving reciprocating members in the piston cylinder are driven by the connecting rod 6, each cylinder corresponding to one connecting rod 6, and the three connecting rods 6 are simultaneously mounted on a crank 5
  • the first cylinder block 1 and the third cylinder block 3 are respectively located on two sides of the second cylinder block 2, and the angle between the axis and the vertical direction is an acute angle, preferably less than 40°, and the optimization scheme is 20° to 30°.
  • the angle is too large, the partial wear of the piston will be reduced, and the continuous service life of the piston will be reduced. If the angle is too small, space interference will occur, affecting the installation of the three cylinders on the components, and the three cylinders need to be elongated along the crankshaft 4
  • the length of the axis can be distributed to avoid spatial interference.
  • the offset friction is reduced by 30° angle than 40° angle, and the average service life is increased by 26%.
  • the effect of reducing the same angle on the partial friction is reduced, but the same angle is reduced.
  • the lengthening of the distribution length of the three piston cylinders along the axis of the crankshaft 4 becomes larger. At less than 30°, the opposite is true, and an optimum combination of compactness and reduced friction can be achieved in the range of 30° ⁇ 3°.
  • the following is a structural comparison between the inventive plunger pump and the V-type plunger pump.
  • the displacement is 270 m 3 / hour
  • the head is 400 m
  • the water injection plunger diameter is ⁇ 125
  • the number of cylinders of the plunger pump of the present invention is 9.
  • the V-type plunger pump has a cylinder number of 10.
  • the two connecting rods 6 of the V-type plunger pump are 30 mm larger than the center distance of the three connecting rods 6 of the W-type pump. Since the length of the crankshaft 4 exceeds 1 m, an additional length is required to increase the strength of the crankshaft 4. At the same time, the width of the plunger pump of the present invention in the left-right direction is not wider than that of the V-type plunger pump. It can be seen that the plunger pump of the present invention has a strong advantage in terms of a small footprint.
  • the direction of the axis of the crankshaft 4 of the plunger pump is the front and rear, and the vertical direction is the up and down, and the vertical direction is the left and right.
  • the crankshaft 4 is provided with three cranks 5 corresponding to the three sets of links 6, and each set of links 6 is three, then the three links 6 One end is set on the same crank 5, the front and rear positions of the connecting rod 6 are different, then the front and rear positions of the corresponding piston and the piston cylinder are also different, and the spacing between the adjacent two piston axes in the front and rear direction is adjacent
  • the spacing of the centers of the connecting rods 6 and the staggering of the front and rear can make the arrangement of the three piston cylinders along the radial direction of the crankshaft 4 more space-width, thus making the structure more compact and more space-saving.
  • Each piston corresponds to a connecting rod 6, and the structure of the connecting rod 6 is simpler than the connecting rod 6 of the V-type plunger pump, and the shape of the inner cavity of the piston cylinder at the connecting rod 6 does not have to be specifically designed to avoid the connecting rod 6. Since the three piston cylinders are distributed to the left and right, when the crank 5 is at the same position, that is, at the same time, the three pistons are in different stroke states, avoiding the concentration of the load at a certain moment, and reducing the maximum torque that the crank 5 is subjected to.
  • Each of the piston cylinders is independently provided with a suction chamber and a drainage chamber.
  • the suction chambers of the first cylinder block 1 and the third cylinder block 3 are located on both sides of the plunger pump, and the suction chamber of the second cylinder block 2 is located. Piston pump front end.
  • the first cylinder block 1 of each group of piston cylinders is arranged in an integral structure, and is consistent in front and rear.
  • the three first cylinders 1 can also be staggered in the left and right direction. .
  • the three second cylinders 2 and the three third cylinders 3 can adopt the same structure as the first cylinder block 1.
  • the suction chambers of the three first cylinders 1 are connected together and are located on the side of the plunger pump.
  • the structure of the three suction chambers and the drainage chamber effectively reduces the suction and drainage resistance of the pump, improves the drainage efficiency of the pump, thereby reducing the power of the distribution, and also reducing the requirements of the pump for the equipment during the processing.
  • a spindle support shaft diameter 7 is arranged between two adjacent cranks 5 to ensure sufficient strength of the crankshaft 4 and to improve the fracture resistance of the crankshaft 4.
  • the spindle support shaft diameter 7 is matched with the housing bush. At the same time, since the length of the crankshaft 4 is shortened, the torque is greater, and the diameter of the crankshaft 4 can be appropriately increased.
  • crankshaft 4 Because the shorter the crankshaft 4 is, the smaller the axial torsion force is, and the longer the crankshaft 4 is, the greater the torque per unit area is, and the better the fracture resistance of the crankshaft 4.
  • the W-type plunger pump of the present invention is 300 mm higher than the V-type pump, and does not cause transportation and installation difficulties.
  • Efficiency Since the W-type occlusion pump is shortened to about 60% of the total length of the V-type pump, and one-third of the cylinders are placed at a position 90° perpendicular to the crankshaft 4, this not only reduces the length of the drainage chamber of the pump cover.
  • the utility model effectively reduces the resistance of the drainage, improves the smoothness of the water outlet, and reduces the abnormal frictional force of the surface of the 30% reciprocating member in the pump to zero, thereby effectively improving the service life of the pump and prolonging the use time.
  • Pump drainage efficiency increased from 75%-83% to 83%-92%
  • the total length of the crankshaft 4 is 1070 mm, the main diameter of the crankshaft is ⁇ 100 mm, and the diameter of the support shaft is 100 ⁇ .
  • the number of cranks 5 is 3, the number of spindle support shaft diameters is 7 , the diameter of the spindle support shafts is 45 mm, and the maximum torque of curved bearings is 6500 N. m.
  • the outer diameter of the piston cylinder is ⁇ 125, the angle is 30° to 40°, the width of one link is 46, and the three links need to have a certain gap. Then the width of one crank 5 is 150.
  • the maximum outer circle of the crankshaft 4 is ⁇ . 215
  • the wear resistance and hydrolysis resistance of the sealing material in the plunger pump are the main components to ensure the normal operation of the pump.
  • the sealing materials used in the plunger pump are mostly rubber and polyurethane rubber. Although these two materials can seal, the plunger and the rod diameter in the high-flow, high-lift plunger pump are increased. As a result, the hardness and wear resistance of the seal increase. Therefore, the two materials are not resistant to high wear resistance, and the high hydrolysis resistance cannot ensure the normal use of the pump for a long time, resulting in a short service life.
  • the sealing member of the plunger pump of the invention adopts high wear-resistance and hydrolysis-resistant polyether and ether polyurethane as the sealing material, and the material itself has three characteristics of high hardness, high wear resistance and high hydrolysis resistance, and is used for the plunger pump.
  • the high strength and high reciprocating operation have better adaptability.
  • This material greatly improves the hardness and wear resistance inside and outside the seal, which increases the service life of the pump by more than 5 times, enabling the pump to maintain continuous operation for a long time.
  • the use of polyether polyurethane materials can increase the life of seals by an average of 17%.

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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

公开了一种柱塞泵，曲轴（4）上设有至少两个曲拐（5），曲拐（5）上连接有连杆（6），连杆（6）另一端带动一个活塞在活塞缸体内上下往复运动，所述连杆（6）、活塞和活塞缸体为至少两组，每组包括三个，每组的三个连杆（6）套装于同一个曲拐（5）之上，每组的三个活塞缸体的轴线不在同一平面上。每组活塞缸体包括第一缸体（1）、第二缸体（2）和第三缸体（3），第一缸体（1）和第三缸体（3）轴线与竖直方向的夹角为锐角，第二缸体（2）位于第一缸体（1）和第三缸体（3）中间，第二缸体（2）轴线保持竖直。曲轴（4）的每个曲拐（5）之间设置有主轴支撑轴径（7），主轴支撑轴径（7）的外径不小于曲轴（4）直径。该柱塞泵占地面积更小、使用场合更灵活，曲轴的强度更大，使用寿命长。

Description

柱塞泵 技术领域
本发明涉及液压装置领域。
背景技术
现今，国内外的大型煤矿、 铁矿、 金矿等等所用的排水泵， 均在 200米 3/小时以上， 所 以对大排水量水泵的流量、 扬程、 电机功率的要求很高， 对排水流量大、 扬程高、 电机功率 小的节能水泵需求巨大， 此前， 公告中公布的 V型柱塞泵， 虽然能满足市场需求的流量大、 扬程高、 电机小的要求。 但是， 此泵的 V型结构， 使水泵左右对称两排增加柱塞数量以达到 说
大流量， 所占空间大、 上下矿井、 运输难度大， 并且对井下安装空间也得充足； 并且泵重量 大， 对运输安装要求难度很高； 而且， 泵总长过长， 达到接近 2000mm左右， 对泵加工精度要 书
求也高， 由此， 对加工泵设备的长度， 精度要求很高， 造成几方面成本加大， 给用户增加额 外负担。
发明内容
本发明所解决的技术问题是提供一种占地面积更小、 使用场合更灵活的柱塞泵。
本发明采用的技术方案是柱塞泵， 曲轴上设有至少两个曲拐， 曲拐上连接有连杆， 连杆 另一端带动一个活塞在活塞缸体内上下运动， 其特征在于： 所述连杆、 活塞和活塞缸体为至 少两组， 每组包括三个， 每组的三个连杆套装于同一个曲拐之上， 每组的三个活塞缸体的轴 线不在同一平面上。
每组活塞缸体包括第一缸体、 第二缸体和第三缸体， 第一缸体和第二缸体轴线与竖直方 向的夹角为锐角， 第二缸体位于第一缸体和第二缸体中间， 第二缸体轴线保持竖直。
第一缸体和第二缸体轴线与竖直方向的夹角不大于 40° ， 三个活塞缸体沿曲轴轴线螺旋 状排列。
所述曲拐为 3至 6个。
每个缸体上设有一个吸水腔和一个排水腔。
所述曲轴的每个曲拐之间设置有主轴支撑轴颈， 主轴支撑轴颈的外径不小于曲轴直径。 本发明的有益效果是， 占地面积小， 适用于空间狭小的使用场合； 曲轴的强度更大， 使 用寿命长； 密封件的高硬度、 高耐磨、 抗水解性能更好； 给用户节省了泵运输、 安装、 电机 功率三方面的节省， 也使泵加工成本大幅下降， 直接给用户节省了大量的额外的开支。 附图说明
图 1为本发明立体图。 图 2为本发明柱塞泵的俯视图。
图 3为图 1对应的左视图。
图 4为图 2中沿 A-A方向的剖视图。
图 5为图 2中沿 B-B方向的剖视图。
图 6为图 4中 C区域局部放大图。
图中标记为： 1-第一缸体， 2-第二缸体， 3-第三缸体， 4-曲轴， 5-曲拐， 6-连杆， 7-主 轴支撑轴径。
具体实施方式
如图 1所示， 本发明的柱塞泵的活塞缸体分为 3组， 每组 3个缸体， 分别为第一缸体 1、 第二缸体 2和第三缸体 3， 第二缸体 2的轴线为竖直方向， 活塞缸体内的运动往复件由连杆 6 带动， 每个缸体对应于一个连杆 6， 三个连杆 6同时安装于一个曲拐 5之上， 曲拐 5有三个， 对应三组连杆 6、 活塞。 第一缸体 1和第三缸体 3分别位于第二缸体 2的两侧， 其轴线与竖 直方向的夹角为锐角， 最好小于 40° ， 最优化方案为 20° 到 30° ， 角度过大会带来活塞的 偏量磨损， 降低活塞的连续使用寿命， 角度过小会造成空间上的干涉， 影响三个缸体在零部 件上的安装， 需拉长三个缸体沿曲轴 4轴线的分布长度才能避免空间干涉。 经过试验测试， 采用 30° 角比 40° 角的偏量摩擦减少， 平均使用寿命提高 26%， 小于 30° 角后每縮减相同角 度对偏量摩擦的影响幅度降低， 但是减小相同角度而使三个活塞缸体沿曲轴 4轴线的分布长 度的加长幅度变得更大。 在小于 30° 的时候， 情况刚好相反， 在 30° ± 3° 的范围都可以取 得结构紧凑和摩擦减小的最优化组合。
下面是发明的柱塞泵和 V型柱塞泵在结构上的对比， 排水量为 270米 3/小时， 扬程 400 米， 注水柱塞直径为 Φ 125， 本发明的柱塞泵的缸数为 9， V型柱塞泵的缸数为 10。
一、 总长： （1 ) V型柱塞泵为 5个曲拐 5， 4个两缸中心距共为 300 X 4= 1200隱。 加上曲 轴 4两端 220+310 = 530, 总长为 530+1200= 1730隱。
( 2 ) 本发明 W型的柱塞泵为 3个曲拐 5， 2个两缸中心距共为 270 X 2 = 540隱， 加上曲 轴 4两端 530+540= 1070mm， 1730— 1070 = 660隱。 所以， 本发明的柱塞泵比 V型泵的总长度 约短 660mm。
V型柱塞泵中的 2个连杆 6比 W型泵中的 3个连杆 6的中心距还大 30mm， 因为曲轴 4长 度超过 1米后， 需要附加的长度用来增加曲轴 4的强度， 同时本发明的柱塞泵左右方向的宽 度没有比 V型柱塞泵加宽。 由此可见本发明的柱塞泵在占地面积小这一方面具有很强优势。
下面叙述中以柱塞泵的曲轴 4轴线的方向为前后， 竖直方向为上下， 与前两者垂直的为 左右。 曲轴 4上设有三个曲拐 5对应于三组连杆 6， 每组连杆 6为三个， 那么这三个连杆 6 的一端都套装于同一个曲拐 5上， 连杆 6的前后位置不同， 那么对应的活塞及活塞缸体的前 后位置也是不同的， 相邻两个活塞轴线在前后方向的间距就是相邻两个连杆 6中心的间距， 前后的错落， 可以使三个活塞缸体沿曲轴 4径向的排布更有空间宽裕度， 因此使结构更加紧 凑， 更节省空间。 每个活塞对应一个连杆 6， 连杆 6结构就比 V型柱塞泵的连杆 6更简单， 连杆 6处的活塞缸体的内腔形状不必为避让连杆 6而特定设计。由于三个活塞缸体左右分布， 曲拐 5处于同一位置时， 也即同一时刻， 三个活塞处于不同的行程状态， 避免载荷在某一时 刻的集中， 减低曲拐 5承受的最大扭矩。
每个活塞缸体各自独立的设有一个吸水腔和一个排水腔， 第一缸体 1和第三缸体 3的吸 水腔壳体位于柱塞泵两侧， 第二缸体 2的吸水腔位于柱塞泵前端。 为了结构紧凑和加工、 安 装方便方面的考虑， 各组活塞缸体的中第一缸体 1设置为一体式结构， 并且前后一致， 当然 三个第一缸体 1也可以左右方向有一定的交错。 同理三个第二缸体 2、 三个第三缸体 3都可 以采用与第一缸体 1相同的结构。三个第一缸体 1的吸水腔连通在一起， 位于柱塞泵的侧面。 这样三个吸水腔、 排水腔的结构有效降低了泵的吸排水阻力， 提高了泵的排水效率， 从而使 配用功率减小，也减小了泵在加工过程对设备的要求。
相邻两个曲拐 5之间设置有主轴支撑轴径 7，用以保证曲轴 4有足够的强度和提高曲轴 4 的抗折断性， 泵的流量越大， 扬程越高， 对于泵中曲轴 4强度要求就越高， 本发明中主轴支 撑轴径 7的增加， 有效保证了大型流量泵在高强度、 运转、 使用过程中始终保持正常工作， 延长了泵的使用寿命。 主轴支撑轴径 7与壳体轴瓦配合。 同时由于曲轴 4长度縮短， 承受扭 力更大， 同时还可以适当增加曲轴 4直径。
因为曲轴 4越短， 承受的轴向扭力就越小， 反之曲轴 4越长， 每单位面积承受的扭力就 越大， 更能提高曲轴 4的抗折断性。
本发明 W型的柱塞泵比 V型泵高 300mm， 不会造成运送、 安装困难。 效率： 由于 W型的 阻塞泵比 V型泵的总长縮短至 60%左右，并且，把其中 1/3缸放置与曲轴 4保持垂直 90°位置， 这样不但使泵盖的排水室长度尺寸减小， 有效减少了排水的阻力， 提高了出水的顺畅性， 还 使泵中的 30%往复件的表面非正常磨擦力减少至零， 这样就有效提高了泵的使用寿命， 延长 了使用时间， 使泵的排水效率由此前的 75%-83%提升至 83%-92%
本发明的实施方式之一： 曲轴 4总长度为 1070mm， 曲轴主轴径为 Φ 100mm, 支撑轴径为 100 。 曲拐 5数量为 3， 主轴支撑轴径 7数量为 2， 主轴支撑轴径 7宽度为 45mm， 曲轴承 受最大扭矩为 6500N. m。 活塞缸的外径为 Φ 125， 夹角为为 30°至 40°， 一个连杆宽 46， 三个连 杆需要留有一定间隙， 那么一个曲拐 5宽度为 150 曲轴 4最大外圆为 Φ 215
另一方面， 柱塞泵中的密封材质的耐磨， 耐水解性是保证泵运转正常的主要部件， 传统 柱塞泵中使用的密封材质多是橡胶和聚氨脂橡胶。 此两种材质虽能起到密封作用， 但是， 大 流量、 高扬程柱塞泵中的柱塞、 拉杆直径都加大。 从而使密封的硬度、 耐磨度都随之增加。 所以， 此两种材质由于自身的不抗高耐磨， 不高抗水解性无法保证泵长时间正常使用， 造成 使用寿命短。本发明中柱塞泵的密封件采用具有高耐磨抗水解性聚， 醚聚氨脂作为密封材质， 此材质自身具有高硬度、 高耐磨、 高抗水解三种特点， 对柱塞泵使用的大强度、 高往复运转 具有更好的适应性。 此材质大大提高密封件内外部的硬度和耐磨度， 使泵的使用寿命提高 5 倍以上， 使泵能保持长时间的连续运转。 根据实验证明， 采用聚醚聚氨脂的材料可使密封件 的寿命平均提高 17%。

Claims

权 利 要 求 书
1、柱塞泵， 曲轴（4)上设有至少两个曲拐（5)， 曲拐（5)上连接有连杆（6)， 连杆（6) 另一端带动一个活塞在活塞缸体内上下往复运动， 其特征在于： 所述连杆 （6)、 活塞和活塞 缸体为至少两组， 每组包括三个， 每组的三个连杆 （6) 套装于同一个曲拐 （5) 之上， 每组 的三个活塞缸体的轴线不在同一平面上。
2、 如权利要求 1所述的柱塞泵， 其特征在于： 每组活塞缸体包括第一缸体（1 )、 第二缸 体 （2)和第三缸体 （3)， 第一缸体 （1 )和第二缸体 （2)轴线与竖直方向的夹角为锐角， 第 二缸体 （2) 位于第一缸体 （1 ) 和第三缸体 （3) 中间， 第二缸体 （2) 轴线保持竖直。
3、 如权利要求 2所述的柱塞泵， 其特征在于： 所述第一缸体 （1 )和第二缸体（2)轴线 与竖直方向的夹角不大于 40° ， 三个活塞缸体沿曲轴 （4) 轴线螺旋状排列。
4、 如权利要求 1所述的柱塞泵， 其特征在于： 所述曲拐 （5) 为 3至 6个。
5、 如权利要求 1所述的柱塞泵， 其特征在于： 每个活塞缸体上设有一个吸水腔和一个排 水腔。
6、 如权利要求 1所述的柱塞泵， 其特征在于： 所述曲轴 （4) 的每个曲拐 （5)之间设置 有主轴支撑轴径 （7)， 主轴支撑轴径 （7) 的外径不小于曲轴 （4) 直径。
7、 如权利要求 1所述的柱塞泵， 其特征在于： 所述柱塞泵中设有密封件， 密封件采用聚 醚聚氨脂材料。
PCT/CN2012/079099 2012-04-09 2012-07-24 柱塞泵 WO2013152568A1 (zh)

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