WO2020211083A1 - 一种超大功率五缸柱塞泵 - Google Patents

一种超大功率五缸柱塞泵 Download PDF

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Publication number
WO2020211083A1
WO2020211083A1 PCT/CN2019/083493 CN2019083493W WO2020211083A1 WO 2020211083 A1 WO2020211083 A1 WO 2020211083A1 CN 2019083493 W CN2019083493 W CN 2019083493W WO 2020211083 A1 WO2020211083 A1 WO 2020211083A1
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Prior art keywords
connecting rod
power
crankcase
gear
assembly
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PCT/CN2019/083493
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English (en)
French (fr)
Inventor
崔海萍
刘红
王继鑫
崔文平
魏小淞
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烟台杰瑞石油装备技术有限公司
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Priority to PCT/CN2019/083493 priority Critical patent/WO2020211083A1/zh
Publication of WO2020211083A1 publication Critical patent/WO2020211083A1/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
    • 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
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • 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

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  • the invention relates to the field of oil and gas drilling equipment, in particular to an ultra-high-power five-cylinder plunger pump.
  • the current market The common fracturing pumps above mainly include 2800HP five-cylinder plunger pump, 3000HP three-cylinder plunger pump, 3300HP five-cylinder plunger pump, 4000HP three-cylinder plunger pump; 2800HP five-cylinder plunger pump is mainly configured in 2500 fracturing truck
  • the current 2500 fracturing truck is the most commonly used fracturing equipment in fracturing operations; its disadvantage is that under high pressure operations, the displacement of a single unit is low; in shale gas operations, more than a dozen fracturing equipment are required.
  • the simultaneous operation of vehicles can meet the requirements of the total displacement in the operation process. The simultaneous operation of so many vehicles will occupy a large area of the well site.
  • the 4000HP triplex plunger pump is It is configured on a 3100HP fracturing truck, but the 4000HP plunger pump is a three-cylinder pump whose displacement is much lower than that of the 2800HP five-cylinder pump. Under the same plunger specifications and the same sprint, its displacement is only 82.54% of the 2800HP five-cylinder pump; if Deploying the 2800HP plunger pump and 4000HP plunger pump to the electric drive fracturing equipment does not reflect the advantages of electric drive fracturing, which is equivalent to a large horse-drawn cart. Therefore, it is urgent to develop a high-power plunger pump to match emerging Electric drive fracturing equipment.
  • the purpose of the present invention overcomes the shortcomings of the prior art and provides an ultra-high-power five-cylinder plunger pump with a rated input power of 5000hp to solve the problem that the high-power motor cannot match the plunger pump of the corresponding specification in electric fracturing. It also solves the contradiction between limited oil and gas field wellsite conditions and multiple matching of fracturing equipment.
  • a super-power five-cylinder plunger pump including a power end assembly, a hydraulic end assembly and a reduction box assembly
  • the power end assembly adopts a segmented structure
  • the design includes a crankcase, a crosshead box, and a spacer.
  • One end of the crosshead is connected with the crankcase by bolts, and the other end of the crosshead is connected with the spacer by bolts.
  • the hydraulic end The assembly is located at one end of the spacer frame, which is connected to the crankcase body by bolts passing through the spacer frame, the crosshead box and the crankcase body.
  • the reduction gearbox assembly is connected with the crankcase body by bolts.
  • the crankshaft in the crankcase body is forged from alloy steel. It includes six journals and five crankshafts. A crank is arranged between two adjacent journals. The distance between the crankshaft and the center of rotation of the crankshaft is 110 to 160 mm.
  • the input angle of the reduction box assembly can be adjusted according to input requirements.
  • the reduction gearbox assembly includes a planetary reduction gearbox and a parallel stage reduction gearbox; both the parallel stage reduction gearbox and the planetary stage reduction gearbox are driven by helical gears;
  • the planetary reduction gearbox includes a sun gear and four planetary gearboxes. Gears and a gear ring, four planetary gears form a planetary gear mechanism, the sun gear is located in the center of the planetary gear mechanism, the planetary gears and the adjacent sun gear and gear ring are in a constant meshing state;
  • the parallel-stage reduction box includes a pinion and a large gear The gear and the small gear are connected with the input end, and the large gear is coaxial with the sun gear of the planetary reduction box, and its transmission ratio is 6.5:1-15:1.
  • an arch structure support column is provided on the spacer.
  • a crosshead mechanism is provided in the crosshead box, a connecting rod mechanism is arranged in the crankshaft case and the crosshead box, one end of the connecting rod mechanism is connected with the crankshaft, and the other end of the connecting rod mechanism is connected with the crosshead mechanism
  • the connecting rod mechanism includes a connecting rod cover, a connecting rod bearing bush and a connecting rod body.
  • the connecting rod cover and the connecting rod body are connected by bolts.
  • the connecting rod bearing bush is located in the cylindrical space formed by the connecting rod cover and the connecting rod body. Both sides are flanging structure, wide-side structure has a large width to diameter ratio.
  • a super-high-power five-cylinder plunger pump has a braking power of 5000hp and a maximum output power of 4500hp, which is equivalent to the sum of two 2500 pumps. It has a high-power and large-displacement design and is suitable for various complex operations. It can reduce the equipment required for on-site operations, save on-site operation sites, and reduce equipment costs.
  • the segmented design makes the overall structure of the power end assembly compact, easier to manufacture, and more convenient for assembly and later maintenance of the entire pump; the selection of high-strength steel plates and reasonable structural design ensure the strength and Rigidity requirements.
  • the support column of the spacer frame is designed as an arched structure to improve the support strength and meet the requirements of the power end assembly under high load strength and stiffness.
  • the segmented structure design facilitates later assembly and maintenance, and also reduces The processing cost reduces the weight of the crankcase.
  • 10in long stroke design and five-cylinder structure design it has the following design advantages: 10in long stroke design can realize large displacement operation requirements, while reducing pump strokes and increasing the service life of various parts; adopting five-cylinder structure The design increases the output displacement of the plunger pump. Compared with the three-cylinder pump, the five-cylinder pump works smoothly without vibration, which can reduce the vibration of the whole pump and prolong its service life.
  • the gearbox assembly adopts planetary gearboxes and parallel-stage gearboxes to be used together, which is conducive to obtaining a large transmission ratio.
  • the transmission ratio can reach 6.5:1-15:1.
  • the large speed ratio can reduce the input torque and increase the gearbox.
  • the service life of the turbine engine provides an effective guarantee for the matching of the turbine engine drive and the motor drive; a large reduction ratio can reduce the stroke of the plunger pump, reduce the number of fatigue cycles of each rotating component, and prolong the service life of each component ;
  • the input angle of the gearbox can be adjusted according to the input requirements, which can meet multi-angle adjustment and adapt to various installation requirements.
  • crankshaft The size of the crankshaft is increased to ensure that the plunger pump can output higher pressure.
  • Both sides of the connecting rod bearing bush are flanging structure, the flanging structure has a large width-to-diameter ratio, which can achieve high load-bearing capacity and good positioning effect.
  • Figure 1 is a schematic diagram of the structure of the present invention.
  • Figure 2 is a schematic diagram of the structure of the power end assembly of the present invention.
  • Figure 3 is a schematic diagram of the gearbox assembly of the present invention.
  • Figure 4 is a cross-sectional view of the present invention.
  • Figure 5 is a schematic diagram of the connecting structure of the link mechanism and the crosshead mechanism of the present invention.
  • Figure 6 is a schematic diagram of the crankshaft structure of the present invention.
  • Figure 7 is a schematic diagram of the connecting rod bearing structure of the present invention.
  • Fig. 8 is a schematic diagram of the structure of the parallel-stage reduction box of the present invention.
  • Figure 9 is a schematic diagram of the structure of the planetary gearbox of the present invention.
  • 1 power end assembly 1 power end assembly, 2 hydraulic end assembly, 3 reduction gear box assembly, 4 crankcase, 5 crosshead box, 6 spacer, 7 crankshaft, 8 journal, 9 crank, 10 cylindrical roller Subshaft, 11 valve box, 12 plunger, 13 bearing seat, 14 front end plate, 15 cover plate, 16 legs, 17 slide rail, 18 support column, 19 connecting rod cover, 20 connecting rod bearing, 21 connecting rod body, 22 cross head, 23 cross head gland, 24 cross head connecting screw, 25 cross head guide plate, 26 guide plate bolt, 27 tie rod, 28 clamp, 29 planetary gear box, 30 parallel stage gear box, 31 flange structure, 32 large Gears, 33 pinions, 34 planetary gears, 35 gear rings, 36 sun gears.
  • an ultra-high-power five-cylinder plunger pump includes a power end assembly 1, a hydraulic end assembly 2 and a reduction box assembly 3.
  • the power end assembly 1 uses a sub-assembly
  • the segmented structure design and segmented design make the overall structure of the power end assembly 1 compact and easier to manufacture.
  • the assembly and subsequent maintenance of the whole pump are also more convenient, and the processing cost is also reduced.
  • the power end assembly 1 includes a crankcase 4, a crosshead case 5, and a spacer 6.
  • the crosshead case 5 is connected to the crankcase 4 by hexagonal head bolts, and the other of the crosshead case 5 One end is connected to the spacer frame 6 by bolts, the hydraulic end assembly 2 is arranged at one end of the spacer frame 6, and the bolts pass through the spacer frame 6, the crosshead box body 5 and the crankcase body 4 in turn, and the reduction box assembly 3 is connected by bolts Connected to the crankcase 4, the crankshaft 7 in the crankcase 4 is forged from alloy steel, including six journals 8 and five crankshafts 9, and a crankshaft is provided between two adjacent journals 8 9.
  • the five-cylinder structure design uses the five-cylinder structure design to increase the output displacement of the plunger pump.
  • the five-cylinder pump works smoothly without vibration, which can reduce the vibration of the whole pump and extend the service life;
  • the distance between the crankshaft 9 and the rotation center of the crankshaft 7 is 110 to 160mm, which ensures that the plunger pump can output a higher pressure, that is, provides technical support for long strokes, and its stroke can reach 10in, which can meet the needs of large displacement operations.
  • it reduces the number of pump strokes and increases the service life of each component.
  • the hydraulic end assembly 2 includes a valve box 11 and a plunger 12, the plunger 12 is arranged in the valve box 11, and the crankcase body 4 is welded by steel plates. It is mainly composed of six bearing seats 13 and a front end plate 14, a cover plate. 15. The legs 16 are assembled and welded together. After the welding is completed, the bearing seat 13 and the front end plate 14 are processed by finishing.
  • the crosshead box body 5 is welded by steel plates, the arc-shaped slide rail 17 is fixed on the crosshead box body 5, and the arc-shaped slide rail 17 is forged from alloy steel; the spacer 6 has an arched structural support column 18 , To improve the support strength; the crosshead box body 5 and the spacer frame 6 are left with through holes, and the hydraulic end valve box 11 passes through the spacer frame 6, the crosshead box body 5 and the crankcase body 4 by bolts.
  • a cylindrical roller shaft 10 is installed on the journal 8, and the outer ring of the cylindrical roller shaft 10 is installed on a bearing seat 13.
  • the crosshead box 5 is provided with a crosshead mechanism
  • the crankshaft case 4 and the crosshead box 5 are provided with a connecting rod mechanism
  • one end of the connecting rod mechanism is connected with the crankshaft 7, and the other end of the connecting rod mechanism is connected with the crosshead mechanism
  • the connecting rod mechanism includes a connecting rod cover 19, a connecting rod bearing 20 and a connecting rod body 21.
  • the connecting rod cover 19 and the connecting rod body 21 are connected by bolts, and the connecting rod bearing 20 is formed by connecting the connecting rod cover 19 and the connecting rod body 21
  • both sides of the connecting rod bearing bush 20 are flanged structures 31, and the wide-side structure has a large width-to-diameter ratio, which can achieve high load-bearing capacity and good positioning effect.
  • the cross head mechanism includes cross head 22, cross head gland 23, cross head connecting screw 24, cross head guide plate 25, guide plate bolt 26, connecting rod body 21, connecting rod cover 19, cross head 22 and cross head gland 23 are made of alloy It is made of steel forging.
  • One end of the connecting rod mechanism is connected to the crank 9 and the other end is connected to the cross head 22 through the cross head gland 23;
  • the cross head guide plate 25 is fixed to the cross head 22 by the guide plate bolt 26, and the cross head guide plate 25 is round It has an arc shape with an oil groove on the surface;
  • the cross head 22 is connected to the plunger 12 of the hydraulic end assembly 2 through a tie rod 27 and a clamp 28, and further, the cross head 22 and the tie rod 27 are connected by screws.
  • the output end of the reduction gearbox assembly is connected with the crankshaft 7.
  • the reduction gearbox assembly includes a planetary gearbox 29 and a parallel-stage gearbox 30.
  • the parallel-stage gearbox 30 and the planetary gearbox 29 are both helical gear transmissions.
  • the planetary reduction box 29 includes a sun gear 36, four planetary gears 34 and a gear ring 35.
  • the four planetary gears 34 form a planetary gear mechanism.
  • the sun gear 36 is located at the center of the planetary gear mechanism.
  • the gear ring 35 is in a constant meshing state;
  • the parallel-stage reduction box 30 includes a large gear 32 and a small gear 33.
  • the small gear 33 is connected to the input end, and the large gear 32 is coaxial with the planetary reduction box 29 and the sun gear 36;
  • the input speed is transmitted through the pinion 33 to the large gear 32 to achieve a one-stage reduction, through the large gear 32 to the sun gear 36, and the sun gear 36 is transmitted to the planetary gear 34 to achieve a two-stage reduction, so as to obtain a large transmission ratio, which can be Reach 6.5:1-15:1;
  • the planetary gearbox 29 uses four evenly distributed planetary gears 34 to transmit motion and power at the same time.
  • the centrifugal inertia force generated by the revolution of the four planetary gears 34 and the reaction force between the tooth profile The radial component forces are balanced and offset each other, so that the force on the main shaft is reduced and high power transmission is realized.
  • the large speed ratio can reduce the input torque, increase the service life of the gearbox, and provide an effective guarantee for the matching of the turbine engine drive and the motor drive; a large reduction ratio can reduce the stroke of the plunger pump and reduce the fatigue of the rotating parts
  • the number of cycles can extend the service life of each component; at the same time, the input angle of the gearbox assembly can be adjusted according to the input requirements, which can meet multi-angle adjustment and adapt to various installation needs.
  • the reduction box assembly 3 drives the crankshaft 7 to rotate, the crankshaft 7 rotates in the bearing supported by the bearing housing 13, the crankshaft 7 drives the connecting rod body 21, and the connecting rod body 21 drives the crosshead 22 through the crosshead 22 in the crosshead box 5.
  • the arc-shaped slide rail 17 reciprocates inside, and the crosshead 22 drives the plunger 12 through the pull rod 27 to reciprocate inside the valve box 11 of the hydraulic end assembly 2 to perform liquid suction and discharge.

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Abstract

一种超大功率五缸柱塞泵，包括动力端总成（1）、液力端总成（2）和减速箱总成（3），动力端总成（1）采用分段式结构设计，包括曲轴箱体（4）、十字头箱体（5）和间隔架（6），十字头箱体（5）的一端与曲轴箱体（4）连接，十字头箱体（5）的另一端与间隔架（6）连接，液力端总成（2）设在间隔架（6）一端，通过螺栓依次穿过间隔架（6）、十字头箱体（5）与曲轴箱体（4）连接，减速箱总成（3）与曲轴箱体（4）连接，曲轴箱体（4）内的曲轴（7）采用合金钢锻造而成，包括六个轴颈（8）和五个曲拐（9），相邻两个轴颈（8）之间设一个曲拐（9），曲拐（9）与曲轴（7）的旋转中心距离为110至160mm。这种超大功率五缸柱塞泵，其额定输入功率为5000hp，能够解决电驱压裂设备中大功率电机无法匹配相应规格柱塞泵的问题，同时也解决了油气田井场条件受限，压裂设备匹配多的问题。

Description

一种超大功率五缸柱塞泵 技术领域
本发明涉及油气钻采设备的领域，具体涉及一种超大功率五缸柱塞泵。
背景技术
随着油气田超高压、超深井、水平井的不断开发，其作业工况也越来越恶劣，要求高压力、大排量作业，因此对柱塞泵的要求也越来越高，单台压裂设备可以输出高压力、大排量，这样就要求柱塞泵可以大功率、高压力输出；特别是在非常规油气作业——页岩气作业，其作业工况恶劣，需要长时间、大排量、高压力作业，而且作业频次越频繁，因此对压裂设备要求越来越高，而柱塞泵又是压裂设备中的核心部件，因此对柱塞泵的要求也越来越高；近几年新兴电驱压裂作业，采用电机驱动，电机可以选择很大功率，例如：额定功率可以达到3000KW、4000kw、5000kw、6000kw等，但柱塞泵还没有这么大规格的，目前市场上常见的压裂泵主要有2800HP五缸柱塞泵、3000HP三缸柱塞泵、3300HP五缸柱塞泵、4000HP三缸柱塞泵；2800HP五缸柱塞泵主要配置在2500型压裂车上，目前2500型压裂车是压裂作业中最常用、做多的压裂设备；其缺点是在高压力作业下，单机设备排量低；在页岩气作业中需要十几台压裂车同时作业才能满足作业工艺中总排量的要求，这么多台车的同时作业，会占用很大的井场面积，与油气田井场条件受限的矛盾尤为突出；4000HP三缸柱塞泵是配置在3100HP压裂车上，但4000HP柱塞泵是三缸泵其排量比2800HP五缸泵低很多，在相同柱塞规格、相同冲刺下其排量只是2800HP五缸泵的82.54％；如果将2800HP 柱塞泵和4000HP柱塞泵配置到电驱压裂设备上，体现不出电驱压裂的优势，相当于大马拉小车，因此急需开发一款大功率的柱塞泵来匹配新兴的电驱压裂设备。
发明内容
本发明的目的克服现有技术的不足，提供一种超大功率五缸柱塞泵，其额定输入功率为5000hp，以解决电驱压裂中大功率电机无法匹配相应规格柱塞泵的问题，同时也解决了油气田井场条件受限，压裂设备匹配多的矛盾。
本发明的目的是通过以下技术措施达到的：一种超大功率五缸柱塞泵，包括动力端总成、液力端总成和减速箱总成，所述动力端总成采用分段式结构设计，包括曲轴箱体、十字头箱体和间隔架，所述十字头箱体的一端与曲轴箱体通过螺栓连接，所述十字头箱体的另一端与间隔架通过螺栓连接，液力端总成设在间隔架一端，通过螺栓依次穿过间隔架、十字头箱体与曲轴箱体连接，减速箱总成通过螺栓与曲轴箱体连接，所述曲轴箱体内的曲轴采用合金钢锻造而成，包括六个轴颈和五个曲拐，相邻两个轴颈之间设一个曲拐，所述曲拐与曲轴的旋转中心距离为110至160mm。
进一步地，所述减速箱总成的输入角度可以根据输入要求进行调整。
进一步地，所述减速箱总成包括行星减速箱和平行级减速箱；所述平行级减速箱和行星级减速箱均为斜齿轮传动；所述行星减速箱包括一个太阳轮、四个行星齿轮和一个齿轮圈，四个行星齿轮组成行星齿轮机构，太阳轮位于行星齿轮机构中心，行星齿轮和相邻的太阳轮、齿轮圈处于常啮合状态；所述平行级减速箱包括小齿轮和大齿轮，小齿轮与输入端相连， 大齿轮与行星减速箱太阳轮同轴，其传动比为6.5:1—15:1。
进一步地，所述间隔架上设有拱形结构支撑柱。
进一步地，所述十字头箱体内设有十字头机构，在曲轴箱体与十字头箱体内设有连杆机构，连杆机构一端与曲轴连接，连杆机构另一端与十字头机构连接，连杆机构包括连杆盖、连杆轴瓦和连杆体，连杆盖与连杆体通过螺栓连接，连杆轴瓦位于连杆盖与连杆体连接形成的圆柱形空间内，连杆轴瓦两侧为翻边结构，宽边结构宽径比大。
与现有技术相比，本发明的有益效果是：
1、一种超大功率五缸柱塞泵其制动功率为5000hp，最大输出功率可达4500hp，相当于2台2500泵的总和,大功率、大排量设计，可适用于各种复杂作业工况，并可减少现场作业所需设备，节约现场作业场地，降低设备成本。
2、分段式设计使动力端总成整体结构紧凑、加工制造更为容易，整泵的装配和后期维护也更为方便；通过选用高强度钢板和合理的结构设计保证各箱体的强度和刚度要求，如间隔架支撑柱设计为拱形结构，提高支撑强度，满足动力端总成在高负荷强度和刚度下使用要求，同时分段式结构设计方便后期的装配和维修，同时也降低了加工成本，降低了曲轴箱体的重量。
3、采用10in长冲程设计和五缸结构设计，具有如下设计优点：10in长冲程设计可实现大排量的作业需求，同时降低泵的冲次，提高各零部件的使用寿命；采用五缸结构设计增加了柱塞泵输出排量，同时与三缸泵相比，五缸泵作业平稳无振动，可以减少整泵的振动，延长使用寿命。
4、减速箱总成采用行星级减速箱和平行级减速箱配合使用，利于获得大的传动比，传动比可以达到6.5：1—15:1，大速比可以降低输入扭矩，提高减速箱的使用寿命，为满足涡轮发动机驱动和电机驱动的匹配提供了有效保障；大的减速比可以降低柱塞泵的冲次，降低各旋转零部件的疲劳循环次数，可以延长各零部件的使用寿命；同时减速箱的输入角度可以根据输入要求进行调整，可以满足多角度调整，适应多种安装需求。
5、曲轴曲拐的尺寸增大，保证柱塞泵可以输出更高的压力。
6、连杆轴瓦两侧为翻边结构，翻边结构宽径比大，能够实现较高的承载能力，而且定位效果好。
下面结合附图和具体实施方式对本发明作详细说明。
附图说明
图1为本发明结构示意图。
图2为本发明动力端总成结构示意图。
图3为本发明减速箱总成示意图。
图4为本发明剖视图。
图5为本发明连杆机构与十字头机构的连接结构示意图。
图6为本发明曲轴结构示意图。
图7为本发明连杆轴瓦结构示意图。
图8为本发明平行级减速箱结构示意图。
图9为本发明行星减速箱结构示意图。
其中，1动力端总成，2液力端总成，3减速箱总成，4曲轴箱体，5十字头箱体，6间隔架，7曲轴，8轴颈，9曲拐，10圆柱滚子轴，11阀箱，12柱塞，13轴承座，14前端板，15盖板，16支腿，17滑轨，18支撑柱， 19连杆盖，20连杆轴瓦，21连杆体，22十字头，23十字头压盖，24十字头连接螺钉，25十字头导板，26导板螺栓，27拉杆，28卡箍，29行星减速箱，30平行级减速箱，31翻边结构，32大齿轮，33小齿轮，34行星齿轮，35齿轮圈，36太阳轮。
具体实施方式
实施例，如图1至9所示，一种超大功率五缸柱塞泵，包括动力端总成1、液力端总成2和减速箱总成3，所述动力端总成1采用分段式结构设计，分段式设计使动力端总成1整体结构紧凑、加工制造更为容易，整泵的装配和后期维护也更为方便，同时也降低了加工成本。动力端总成1包括曲轴箱体4、十字头箱体5和间隔架6，所述十字头箱体5的一端与曲轴箱体4通过六角头螺栓连接，所述十字头箱体5的另一端与间隔架6通过螺栓连接，液力端总成2设在间隔架6一端，通过螺栓依次穿过间隔架6、十字头箱体5与曲轴箱体4连接，减速箱总成3通过螺栓与曲轴箱体4连接，所述曲轴箱体4内的曲轴7采用合金钢锻造而成，包括六个轴颈8和五个曲拐9，相邻两个轴颈8之间设一个曲拐9，即五缸结构设计，采用五缸结构设计增加了柱塞泵输出排量，同时与三缸泵相比，五缸泵作业平稳无振动，可以减少整泵的振动，延长使用寿命；所述曲拐9与曲轴7的旋转中心距离为110至160mm，保证柱塞泵可以输出更高的压力，即为长冲程提供技术支持，其冲程可达到10in，可实现大排量的作业需求，同时降低泵的冲次，提高各零部件的使用寿命。
液力端总成2包括阀箱11和柱塞12，柱塞12设在阀箱11内，曲轴箱体4采用钢板焊接而成，主要是将六个轴承座13和前端板14、盖板15、 支腿16等组合后焊接到一起，焊接完成后对轴承座13及前端板14进行精加工而成。十字头箱体5采用钢板焊接而成，十字头箱体5上固定有圆弧形滑轨17，圆弧形滑轨17采用合金钢锻造而成；间隔架6上具有拱形结构支撑柱18，提高支撑强度；十字头箱体5及间隔架6上留有通孔，液力端阀箱11通过螺栓依次穿过间隔架6、十字头箱体5与曲轴箱体4连接。轴颈8上安装圆柱滚子轴10，圆柱滚子轴10外圈安装在轴承座13上。
所述十字头箱体5内设有十字头机构，在曲轴箱体4与十字头箱体5内设有连杆机构，连杆机构一端与曲轴7连接，连杆机构另一端与十字头机构连接，连杆机构包括连杆盖19、连杆轴瓦20和连杆体21，连杆盖19与连杆体21通过螺栓连接，连杆轴瓦20位于连杆盖19与连杆体21连接形成的圆柱形空间内，连杆轴瓦20两侧为翻边结构31，宽边结构宽径比大，能够实现较高的承载能力，而且定位效果好。十字头机构包括十字头22、十字头压盖23、十字头连接螺钉24、十字头导板25、导板螺栓26，连杆体21、连杆盖19、十字头22和十字头压盖23采用合金钢锻造而成，连杆机构一端与曲拐9连接，另一端通过十字头压盖23与十字头22连接；十字头导板25通过导板螺栓26固定于十字头22上，十字头导板25为圆弧形，表面有油槽；十字头22通过拉杆27和卡箍28与液力端总成2的柱塞12连接，进一步的，十字头22与拉杆27之间通过螺钉连接。
所述减速箱总成输出端与曲轴7连接，减速箱总成包括行星减速箱29和平行级减速箱30，所述平行级减速箱30和行星级减速箱29均为斜齿轮传动，所述行星减速箱29包括一个太阳轮36、四个行星齿轮34和一个齿轮圈35，四个行星齿轮34组成行星齿轮机构，太阳轮36位于行星齿轮机 构中心，行星齿轮34和相邻的太阳轮36、齿轮圈35处于常啮合状态；所述平行级减速箱30包括大齿轮32和小齿轮33，小齿轮33与输入端相连，大齿轮32与行星减速箱29太阳轮36同轴；输入端输入转速，经小齿轮33传递给大齿轮32实现一级减速，通过大齿轮32传递给太阳轮36，太阳轮36传递到行星齿轮34实现二级减速，从而获得大传动比，其传动比可以达到6.5:1—15:1；行星级减速箱29采用四个均匀分布的行星齿轮34同时传递运动和动力，四个行星轮34因公转而产生的离心惯性力与齿廓间反作用力的径向分力相互平衡抵消，使主轴受力减小，实现大功率传递。大速比可以降低输入扭矩，提高减速箱的使用寿命，为满足涡轮发动机驱动和电机驱动的匹配提供了有效保障；大的减速比可以降低柱塞泵的冲次，降低各旋转零部件的疲劳循环次数，可以延长各零部件的使用寿命；同时减速箱总成的输入角度可以根据输入要求进行调整，可以满足多角度调整，适应多种安装需求。
减速箱总成3带动曲轴7转动，曲轴7在轴承座13支撑的轴承内转动，曲轴7带动连杆体21，连杆体21通过带动十字头22，十字头22在十字头箱体5的圆弧形滑轨17内部往复运动，十字头22通过拉杆27带动柱塞12在液力端总成2的阀箱11内部作往复运动，进行液体的吸入与排出工作。
本行业的技术人员应该了解，本发明不受上述实施例的限制，上述实施例和说明书中描述的只是说明本发明的原理，在不脱离本发明精神和范围的前提下，本发明还会有各种变化和改进，这些变化和改进都落入要求保护的本发明范围内。本发明要求保护范围由所附的权利要求书及其等效物界定。

Claims (5)

  1. 一种超大功率五缸柱塞泵，包括动力端总成、液力端总成和减速箱总成，其特征在于：所述动力端总成采用分段式结构设计，包括曲轴箱体、十字头箱体和间隔架，所述十字头箱体的一端与曲轴箱体通过螺栓连接，所述十字头箱体的另一端与间隔架通过螺栓连接，液力端总成设在间隔架一端，通过螺栓依次穿过间隔架、十字头箱体与曲轴箱体连接，减速箱总成通过螺栓与曲轴箱体连接，所述曲轴箱体内的曲轴采用合金钢锻造而成，包括六个轴颈和五个曲拐，相邻两个轴颈之间设一个曲拐，所述曲拐与曲轴的旋转中心距离为110至160mm。
  2. 根据权利要求1所述的超大功率五缸柱塞泵，其特征在于：所述减速箱总成的输入角度可以根据输入要求进行调整。
  3. 根据权利要求1所述的超大功率五缸柱塞泵，其特征在于：所述减速箱总成包括行星减速箱和平行级减速箱；所述平行级减速箱和行星级减速箱均为斜齿轮传动；所述行星减速箱包括一个太阳轮、四个行星齿轮和一个齿轮圈，四个行星齿轮组成行星齿轮机构，太阳轮位于行星齿轮机构中心，行星齿轮和相邻的太阳轮、齿轮圈处于常啮合状态；所述平行级减速箱包括小齿轮和大齿轮，小齿轮与输入端相连，大齿轮与行星减速箱太阳轮同轴，其传动比为6.5:1—15:1。
  4. 根据权利要求1所述的超大功率五缸柱塞泵，其特征在于：所述间隔架上设有拱形结构支撑柱。
  5. 根据权利要求1所述的超大功率五缸柱塞泵，其特征在于：所述十字头箱体内设有十字头机构，在曲轴箱体与十字头箱体内设有连杆机构，连杆机构一端与曲轴连接，连杆机构另一端与十字头机构连接，连杆机构包括连杆盖、 连杆轴瓦和连杆体，连杆盖与连杆体通过螺栓连接，连杆轴瓦位于连杆盖与连杆体连接形成的圆柱形空间内，连杆轴瓦两侧为翻边结构，宽边结构宽径比大。
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