SP-70型全液压顶驱系统动力学仿真分析
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摘要
顶部驱动钻井系统（Top Drive Drilling System，简称TDS）自1982年诞生以来，在海洋和陆地钻机上都得到了广泛的应用。与常规的钻井装置相比，顶部驱动钻井装置更加安全可靠，特别适合于在深井、超深井、水平井以及斜井等高要求和复杂工况下工作。
目前，世界上正在使用的和生产的TDS，有4种驱动形式：液压驱动形式；AC－SCR－DC电驱动形式；交流(AC)变频感应电动机驱动形式；AC变频永磁电动机驱动形式。国内外的主流产品，如Varco的TDS系列，北京石油机械厂的DQ70BS系列TDS都采取了AC变频感应电机驱动。
AC变频技术在顶驱的应用上比较成熟，然而随着电液比例控制技术的发展，将以电液比例控制技术为代表的液压技术应用于顶驱系统有着其独特的优势，必将成为顶驱未来发展的一个趋势。将电液比例技术应用于TDS系统，即设计一套全液压驱动的TDS可大幅度提高我国科学钻探的技术装备水平，并将对我国钻掘机械方面产生深远的影响，具有重要战略意义。
鉴于电液比例技术为代表的液压技术应用于顶驱的诸多优势，本课题提出设计一套与7000m交流变频顶驱性能相当的液压顶驱，并且要求其能够满足实施金刚石钻进工艺的要求。
设计具体要求如下：（1）能够适应软到硬的任何地层；（2）能够实施金刚石钻进和牙轮钻进；（3）终孔直径为Φ152；（4）孔深能够达到7000m；（5）采用直径Φ89，Φ114，Φ127的钻杆；（6）能够实现全孔连续取心和测井（7）岩心直径大于Φ90。通过参考国内外主流7000m顶驱的设备，以及岩心钻探的具体要求，确定了全液压顶驱的主要工作参数。包括：（1）回转速度为0~300rpm无级调速；（2）钻井扭矩为50kN m；（3）顶驱功率850kW。
通过研究技术较成熟交流变频TDS的结构，了解了TDS的功能以及工作原理。参考交流变频TDS的结构，对7000m全液压TDS进行了初步设计，命名为SP-70全液压顶驱，并绘制了SP-70全液压顶驱的三维实体模型，和液压回路图。
以实现顶驱的功能为目标，分别设计了水龙头－钻井马达总成、导向滑车及伸展（平行四边形）机构总成、管子处理装置和平衡系统，将各部分组装，形成了全液压顶驱的主体机械系统。
然后针对机械系统要实现的动作的控制，分别设计主轴回转系统回路、倾斜机构回路、动力旋转头液压马达控制回路、刹车回路、遥控内防喷器控制回路、背钳油缸控制回路、平衡油缸控制回路和伸展油缸控制回路。并将以上回路进行了集成。
对SP-70全液压顶驱的动作分解成9个动作，并运用Solidworks Motion软件对分解的动作进行了运动分析，得到了相关零部件的绞点反作用力曲线图。为SP-70全液压顶驱的优化设计、有限元分析以及液压油缸的选型提供了依据。通过运动分析得到的绞点反作用力曲线图及其作用列于下：
侧摆吊卡倾斜油缸绞点反作用力曲线图，可用于侧摆吊卡倾斜油缸的选型。侧摆吊卡吊环绞点力曲线图，可作为吊环强度有限元分析的载荷条件。伸展（平行四边形）机构的伸展油缸绞点反作用力曲线图，可用于伸展油缸选型。伸展机构杆件绞点反作用力曲线图，可用于伸展机构杆件的进一步设计和强度校核有限元分析。吊卡夹紧油缸绞点反作用力曲线图，这个曲线在修正后可用于吊卡夹紧油缸的选型。动力旋转头驱动马达扭矩变化曲线图，在经过实验修正后，可用于动力旋转头马达选型依据，也可以作为旋转头齿轮副强度校核的依据。
在运动分析实施过程中，体会到：动力学分析软件在使用过程中应该更加灵活。同时，应该正视其局限性，通过更多的工具实现仿真分析。
对SP-70全液压顶驱的主轴驱动系统建立了系统仿真模型，运用AMESim软件对主轴传动系统的工作过程进行了系统仿真模拟，得到以下结论：
（1）在这个模型上能够实现现有交流变频TDS普遍具备的恒扭矩和恒功率控制；
（2）对主轴系统在正常钻进和载荷突变的情况下进行了模拟，在正常钻进时，系统在保持转速不变的情况下，系统油路能够自动调节工作压力，使扭矩达到负载载荷的强度，保证系统正常运行；在载荷突变的情况下，系统驱动扭矩上升到钻杆柱能承受的最大安全扭矩后，安全阀溢流，使驱动载荷不再变大，保证钻杆柱不被扭断而出现事故。
通过有限元分析软件ANSYS，对主轴进行了有限元静态力学分析和疲劳分析，验证了主轴设计强度符合使用和设计要求。并对齿轮副进行了模态分析，得到了齿轮副低阶固有频率和对应主振型，可为齿轮的设计提供参考。
静态力学分析以所设计的主轴模型为载体，定义了材料特性、零部件之间的接触、约束，添加的载荷为TDS工作过程中最大的静力载荷和最大扭矩，分别为431.2kN和80kN m。得到的最大应力为392MPa，最大应力出现在防松机构与主轴连接处；
鉴于主轴在工作过程中，载荷并不总是静荷载，大多数情况下，主轴都是处于载荷波动的工作状态，因此对主轴进行了疲劳分析。分析过程中，对主轴载荷波动进行了处理，对材料的应力寿命曲线（S－N曲线）进行了计算和设置，得到疲劳分析的结果显示，主轴的承受的应力幅并不大，仅为39MPa，主轴寿命达到5.208×106个周期，大于设计寿命的5×104个周期（5年）；
齿轮副在工作过程中，可能受到振动的影响，因此对齿轮副进行了振动分析。得到了齿轮副前6阶振型的固有频率，以及固有频率对应的振型图。在齿轮副设计中要充分考虑齿轮固有频率和振型，使齿轮固有频率远离TDS工作频率，避免发生共振。
虚拟样机技术日益成熟，在机械设计过程中，虚拟样机技术充分体现了其低成本、高时效的优越性，在今后的设计工作中，虚拟样机技术的应用应该进一步深化和推广。同时要认识到，虚拟样机技术的应用可以减少物理样机的使用数量，降低成本，但不能完全替代物理样机。
Top Drive Drilling System (TDS), since it was born in1982, have been widelyused in marine and land rigs. Compared with conventional drilling tools, TDS ismore secure and reliable, and especially suitable for high demand and complexconditions drilling such as deep, ultra-deep wells, horizontal wells and inclinedwells.
Currently, there are4types of TDS:①type of hydraulic drive TDS;②type ofAC-SCR-DC electric drive TDS;③type of AC variable frequency inductionmotor drive TDS;④type of AC frequency permanent magnet motor drive TDS.Mainstream products at home and abroad, such as TDS series of Varco, DQ70BSseries of Beijing Petroleum Machinery Factory are using the AC variable frequencyinduction motor.
AC variable frequency technology is maturely applicated in TDS. As theproportion of electro-hydraulic control technology development, electro-hydraulicproportional control technology, as represented by hydraulic technology, applied toTDS, has its unique advantages, will be the future development trend.We believethat, make the electro-hydraulic proportional technology used in TDS, that is to saythe design of a hydraulic drive TDS can greatly improve the technical level of China's scientific drilling, and make a profound impact on China's diamond diggingmachinery, also has the important strategic sense.
Electro-hydraulic proportional control technology, as represented by hydraulictechnology, applied to TDS, has its unique advantages. The topics raised to design ahydraulic TDS that has similar performance to7000m AC variable frequency TDS,and able to meet the requirements of the implementation of the diamond drillingprocess.
TDS design based on specific requirements are as follows:(1) Formationconditions: any soft to hard strata;(2) Drilling methods and techniques: diamonddrilling, roller cone drilling;(3) Hole depth:7000m;(4) The final hole diameter: Φ152;(5) Drill pipe diameter：Φ89，Φ114，Φ127;(6) Full hole continuous coringand logging;(7) Core diameter: greater than Φ90. By reference to domestic andforeign mainstream7000m TDS equipment, And the specific requirements of coredrilling, the main working parameters of the hydraulic TDS should be determined asfollows:(1) Rotary speed is0~300rpm stepless speed regulation;(2) Drilling torqueis50kN m;(3) Power to850kW.
This article has carried on the preliminary design of hydraulical drive TDS,named for the SP-70hydraulic drive TDS. Dimensional solid model and Hydrauliccircuit diagram of SP-70hydraulic drive TDS have been built. A carrier is providedfor the TDS further design and optimization
Take realizes the function of TDS, faucet-drilling motor assembly, guide blocksand parallelogram mechanism assembly, pipe handler and balance system aredesigned. The various parts fit together and hydraulic TDS is formatted.
For controlling the motion of mechanical systems to achieve, spindle rotationsystem circuit, tilt mechanism circuit, rotary power head hydraulic motor controlcircuit, brake circuit, IBOP control circuit, back clamp cylinder control circuit,balance cylinder control circuit and stretching cylinder control circuit are designed,and the above circuits are integrated.
A decomposition of the TDS action has been conducted, and the movementanalysis to the decomposition movement has been carried on. The twisted pointforce curve of related parts is obtained. A basis for optimize design, finite elementanalysis and the selection of hydraulic cylinders have been provided.
Reaction force curves of twist points and their roles are listed in the following:(1) Reaction force curves of twist points of swing cylinders of side swing elevator.It can be used for the selection of the cylinders;(2) Reaction force curves of twistpoints of rings of side swing elevator. It can be used as load conditions for the finiteelement analysis of the rings;(3) Reaction force curves of twist points of extensioncylinders of extension mechanism(The parallelogram mechanism). It can be used forthe slection of the extension cylinders;(4) Reaction force curves of twist points ofextension rods of extension mechanism. It can be used for further design of the rod parts and strength check of the finite element analysis;(5) Reaction force curves oftwist points of clamping cylinder of elevator. It can be used for the selection of theclamping cylinder after revised;(6) Drive motor torque curve of power rotatinghead. It can be used for the slection of the drive motor and for the strength check ofrotating head gear pair.
During the implementation of the dynamics analysis, we realized: dynamicsanalysis software should be flexiblely used. At the same time, address its limitations,and use more tools for simulation analysis.
The system simulation model of spindle drive chain has been established andthe system simulation analysis has been conducted on it. Following conclusions hasbeen obtained:
Constant power control and constant torque control can be realized on thismodel;
The simulation analysis of normal drilling conditions and the conditions ofmeeting stuck drill has been conducted. During normal drilling, under the conditionof keeping rotational speed, the system oil duct automatically adjust the workingpressure to enable the torque to achieve the load intensity, to ensure the normaloperation of the system. Under the condition of load mutation, system driving torquerises to maximum safe torque of the drill pipe, then safety valve overflows, the driveload is no longer rising, ensure that the drill pipe column is not broken.
At last, we proved that the spindle drive system can meet the designrequirements with the good stability and security.
Applied the finite element analysis software ANSYS to analyze the main partsin the case of the static mechanical analysis, fatigue analysis and vibration (modal)analysis. The spindle strength has been verified. Vibration analysis of gear pair hasbeen conducted. Conclusions of FEA are listed as following:
Static mechanical analysis: use the designed spindle model for simulation; setmaterial properties, contact and constraints between the parts; the added loads aremaximum static load and maximum torque during the TDS working, they are 431.2kN and80kN m. Get a maximum stress of392MPa. Maximum stress occurs atthe connecton place of the locking bodies and spindle;
Fatigue Analysis: as load act on the spindle is not always static load duringworking, most of the time, the spindle is in the state of load fluctuation. Therefore,fatigue analysis of the spindle has been conducted. During the analysis, loadfluctuation has been settled, material stress life curve (S-N curve) were calculatedand set; results of fatigue analysis showed that spindle stress amplitude is not large,only39MPa; spindle life can reached to5.208e6cycles, greater than the designlife(5×104cycles, that is5years);
Gear pair in the course of their work, may be subject to the effects of vibration.Therefore, vibration analysis of gear pair has been conducted.The first6naturalfrequencies and mode shapes of the gear pair has been provided. Duing the design ofthe gear system, gear natural frequencies and mode shapes shouled be considered,make natural frequencies of the gear away from the operating frequency to avoidresonance.
In the present paper, the full hydraulic pressure top drive design is still stay inthe preliminary design stage, of course, there are many defects and needs the furtheroptimization design. In the course of movement analysis, the friction between theparts may influence the results of the analysis due to the limitation of my experienceand the software, adding up the lacking considering. So we should consult more dataand combine with the spot experience to amend it. During the design process, weprocceeded a large mount of simulation analysis without the support of theexperiments. In the physical prototype design process, we should add moreexperiment content. The application of virtual prototype technology can reduce theuse quantity of physical prototype and reduce the cost, but it can not fully replace thephysical prototype.
目前，世界上正在使用的和生产的TDS，有4种驱动形式：液压驱动形式；AC－SCR－DC电驱动形式；交流(AC)变频感应电动机驱动形式；AC变频永磁电动机驱动形式。国内外的主流产品，如Varco的TDS系列，北京石油机械厂的DQ70BS系列TDS都采取了AC变频感应电机驱动。
AC变频技术在顶驱的应用上比较成熟，然而随着电液比例控制技术的发展，将以电液比例控制技术为代表的液压技术应用于顶驱系统有着其独特的优势，必将成为顶驱未来发展的一个趋势。将电液比例技术应用于TDS系统，即设计一套全液压驱动的TDS可大幅度提高我国科学钻探的技术装备水平，并将对我国钻掘机械方面产生深远的影响，具有重要战略意义。
鉴于电液比例技术为代表的液压技术应用于顶驱的诸多优势，本课题提出设计一套与7000m交流变频顶驱性能相当的液压顶驱，并且要求其能够满足实施金刚石钻进工艺的要求。
设计具体要求如下：（1）能够适应软到硬的任何地层；（2）能够实施金刚石钻进和牙轮钻进；（3）终孔直径为Φ152；（4）孔深能够达到7000m；（5）采用直径Φ89，Φ114，Φ127的钻杆；（6）能够实现全孔连续取心和测井（7）岩心直径大于Φ90。通过参考国内外主流7000m顶驱的设备，以及岩心钻探的具体要求，确定了全液压顶驱的主要工作参数。包括：（1）回转速度为0~300rpm无级调速；（2）钻井扭矩为50kN m；（3）顶驱功率850kW。
通过研究技术较成熟交流变频TDS的结构，了解了TDS的功能以及工作原理。参考交流变频TDS的结构，对7000m全液压TDS进行了初步设计，命名为SP-70全液压顶驱，并绘制了SP-70全液压顶驱的三维实体模型，和液压回路图。
以实现顶驱的功能为目标，分别设计了水龙头－钻井马达总成、导向滑车及伸展（平行四边形）机构总成、管子处理装置和平衡系统，将各部分组装，形成了全液压顶驱的主体机械系统。
然后针对机械系统要实现的动作的控制，分别设计主轴回转系统回路、倾斜机构回路、动力旋转头液压马达控制回路、刹车回路、遥控内防喷器控制回路、背钳油缸控制回路、平衡油缸控制回路和伸展油缸控制回路。并将以上回路进行了集成。
对SP-70全液压顶驱的动作分解成9个动作，并运用Solidworks Motion软件对分解的动作进行了运动分析，得到了相关零部件的绞点反作用力曲线图。为SP-70全液压顶驱的优化设计、有限元分析以及液压油缸的选型提供了依据。通过运动分析得到的绞点反作用力曲线图及其作用列于下：
侧摆吊卡倾斜油缸绞点反作用力曲线图，可用于侧摆吊卡倾斜油缸的选型。侧摆吊卡吊环绞点力曲线图，可作为吊环强度有限元分析的载荷条件。伸展（平行四边形）机构的伸展油缸绞点反作用力曲线图，可用于伸展油缸选型。伸展机构杆件绞点反作用力曲线图，可用于伸展机构杆件的进一步设计和强度校核有限元分析。吊卡夹紧油缸绞点反作用力曲线图，这个曲线在修正后可用于吊卡夹紧油缸的选型。动力旋转头驱动马达扭矩变化曲线图，在经过实验修正后，可用于动力旋转头马达选型依据，也可以作为旋转头齿轮副强度校核的依据。
在运动分析实施过程中，体会到：动力学分析软件在使用过程中应该更加灵活。同时，应该正视其局限性，通过更多的工具实现仿真分析。
对SP-70全液压顶驱的主轴驱动系统建立了系统仿真模型，运用AMESim软件对主轴传动系统的工作过程进行了系统仿真模拟，得到以下结论：
（1）在这个模型上能够实现现有交流变频TDS普遍具备的恒扭矩和恒功率控制；
（2）对主轴系统在正常钻进和载荷突变的情况下进行了模拟，在正常钻进时，系统在保持转速不变的情况下，系统油路能够自动调节工作压力，使扭矩达到负载载荷的强度，保证系统正常运行；在载荷突变的情况下，系统驱动扭矩上升到钻杆柱能承受的最大安全扭矩后，安全阀溢流，使驱动载荷不再变大，保证钻杆柱不被扭断而出现事故。
通过有限元分析软件ANSYS，对主轴进行了有限元静态力学分析和疲劳分析，验证了主轴设计强度符合使用和设计要求。并对齿轮副进行了模态分析，得到了齿轮副低阶固有频率和对应主振型，可为齿轮的设计提供参考。
静态力学分析以所设计的主轴模型为载体，定义了材料特性、零部件之间的接触、约束，添加的载荷为TDS工作过程中最大的静力载荷和最大扭矩，分别为431.2kN和80kN m。得到的最大应力为392MPa，最大应力出现在防松机构与主轴连接处；
鉴于主轴在工作过程中，载荷并不总是静荷载，大多数情况下，主轴都是处于载荷波动的工作状态，因此对主轴进行了疲劳分析。分析过程中，对主轴载荷波动进行了处理，对材料的应力寿命曲线（S－N曲线）进行了计算和设置，得到疲劳分析的结果显示，主轴的承受的应力幅并不大，仅为39MPa，主轴寿命达到5.208×106个周期，大于设计寿命的5×104个周期（5年）；
齿轮副在工作过程中，可能受到振动的影响，因此对齿轮副进行了振动分析。得到了齿轮副前6阶振型的固有频率，以及固有频率对应的振型图。在齿轮副设计中要充分考虑齿轮固有频率和振型，使齿轮固有频率远离TDS工作频率，避免发生共振。
虚拟样机技术日益成熟，在机械设计过程中，虚拟样机技术充分体现了其低成本、高时效的优越性，在今后的设计工作中，虚拟样机技术的应用应该进一步深化和推广。同时要认识到，虚拟样机技术的应用可以减少物理样机的使用数量，降低成本，但不能完全替代物理样机。
Top Drive Drilling System (TDS), since it was born in1982, have been widelyused in marine and land rigs. Compared with conventional drilling tools, TDS ismore secure and reliable, and especially suitable for high demand and complexconditions drilling such as deep, ultra-deep wells, horizontal wells and inclinedwells.
Currently, there are4types of TDS:①type of hydraulic drive TDS;②type ofAC-SCR-DC electric drive TDS;③type of AC variable frequency inductionmotor drive TDS;④type of AC frequency permanent magnet motor drive TDS.Mainstream products at home and abroad, such as TDS series of Varco, DQ70BSseries of Beijing Petroleum Machinery Factory are using the AC variable frequencyinduction motor.
AC variable frequency technology is maturely applicated in TDS. As theproportion of electro-hydraulic control technology development, electro-hydraulicproportional control technology, as represented by hydraulic technology, applied toTDS, has its unique advantages, will be the future development trend.We believethat, make the electro-hydraulic proportional technology used in TDS, that is to saythe design of a hydraulic drive TDS can greatly improve the technical level of China's scientific drilling, and make a profound impact on China's diamond diggingmachinery, also has the important strategic sense.
Electro-hydraulic proportional control technology, as represented by hydraulictechnology, applied to TDS, has its unique advantages. The topics raised to design ahydraulic TDS that has similar performance to7000m AC variable frequency TDS,and able to meet the requirements of the implementation of the diamond drillingprocess.
TDS design based on specific requirements are as follows:(1) Formationconditions: any soft to hard strata;(2) Drilling methods and techniques: diamonddrilling, roller cone drilling;(3) Hole depth:7000m;(4) The final hole diameter: Φ152;(5) Drill pipe diameter：Φ89，Φ114，Φ127;(6) Full hole continuous coringand logging;(7) Core diameter: greater than Φ90. By reference to domestic andforeign mainstream7000m TDS equipment, And the specific requirements of coredrilling, the main working parameters of the hydraulic TDS should be determined asfollows:(1) Rotary speed is0~300rpm stepless speed regulation;(2) Drilling torqueis50kN m;(3) Power to850kW.
This article has carried on the preliminary design of hydraulical drive TDS,named for the SP-70hydraulic drive TDS. Dimensional solid model and Hydrauliccircuit diagram of SP-70hydraulic drive TDS have been built. A carrier is providedfor the TDS further design and optimization
Take realizes the function of TDS, faucet-drilling motor assembly, guide blocksand parallelogram mechanism assembly, pipe handler and balance system aredesigned. The various parts fit together and hydraulic TDS is formatted.
For controlling the motion of mechanical systems to achieve, spindle rotationsystem circuit, tilt mechanism circuit, rotary power head hydraulic motor controlcircuit, brake circuit, IBOP control circuit, back clamp cylinder control circuit,balance cylinder control circuit and stretching cylinder control circuit are designed,and the above circuits are integrated.
A decomposition of the TDS action has been conducted, and the movementanalysis to the decomposition movement has been carried on. The twisted pointforce curve of related parts is obtained. A basis for optimize design, finite elementanalysis and the selection of hydraulic cylinders have been provided.
Reaction force curves of twist points and their roles are listed in the following:(1) Reaction force curves of twist points of swing cylinders of side swing elevator.It can be used for the selection of the cylinders;(2) Reaction force curves of twistpoints of rings of side swing elevator. It can be used as load conditions for the finiteelement analysis of the rings;(3) Reaction force curves of twist points of extensioncylinders of extension mechanism(The parallelogram mechanism). It can be used forthe slection of the extension cylinders;(4) Reaction force curves of twist points ofextension rods of extension mechanism. It can be used for further design of the rod parts and strength check of the finite element analysis;(5) Reaction force curves oftwist points of clamping cylinder of elevator. It can be used for the selection of theclamping cylinder after revised;(6) Drive motor torque curve of power rotatinghead. It can be used for the slection of the drive motor and for the strength check ofrotating head gear pair.
During the implementation of the dynamics analysis, we realized: dynamicsanalysis software should be flexiblely used. At the same time, address its limitations,and use more tools for simulation analysis.
The system simulation model of spindle drive chain has been established andthe system simulation analysis has been conducted on it. Following conclusions hasbeen obtained:
Constant power control and constant torque control can be realized on thismodel;
The simulation analysis of normal drilling conditions and the conditions ofmeeting stuck drill has been conducted. During normal drilling, under the conditionof keeping rotational speed, the system oil duct automatically adjust the workingpressure to enable the torque to achieve the load intensity, to ensure the normaloperation of the system. Under the condition of load mutation, system driving torquerises to maximum safe torque of the drill pipe, then safety valve overflows, the driveload is no longer rising, ensure that the drill pipe column is not broken.
At last, we proved that the spindle drive system can meet the designrequirements with the good stability and security.
Applied the finite element analysis software ANSYS to analyze the main partsin the case of the static mechanical analysis, fatigue analysis and vibration (modal)analysis. The spindle strength has been verified. Vibration analysis of gear pair hasbeen conducted. Conclusions of FEA are listed as following:
Static mechanical analysis: use the designed spindle model for simulation; setmaterial properties, contact and constraints between the parts; the added loads aremaximum static load and maximum torque during the TDS working, they are 431.2kN and80kN m. Get a maximum stress of392MPa. Maximum stress occurs atthe connecton place of the locking bodies and spindle;
Fatigue Analysis: as load act on the spindle is not always static load duringworking, most of the time, the spindle is in the state of load fluctuation. Therefore,fatigue analysis of the spindle has been conducted. During the analysis, loadfluctuation has been settled, material stress life curve (S-N curve) were calculatedand set; results of fatigue analysis showed that spindle stress amplitude is not large,only39MPa; spindle life can reached to5.208e6cycles, greater than the designlife(5×104cycles, that is5years);
Gear pair in the course of their work, may be subject to the effects of vibration.Therefore, vibration analysis of gear pair has been conducted.The first6naturalfrequencies and mode shapes of the gear pair has been provided. Duing the design ofthe gear system, gear natural frequencies and mode shapes shouled be considered,make natural frequencies of the gear away from the operating frequency to avoidresonance.
In the present paper, the full hydraulic pressure top drive design is still stay inthe preliminary design stage, of course, there are many defects and needs the furtheroptimization design. In the course of movement analysis, the friction between theparts may influence the results of the analysis due to the limitation of my experienceand the software, adding up the lacking considering. So we should consult more dataand combine with the spot experience to amend it. During the design process, weprocceeded a large mount of simulation analysis without the support of theexperiments. In the physical prototype design process, we should add moreexperiment content. The application of virtual prototype technology can reduce theuse quantity of physical prototype and reduce the cost, but it can not fully replace thephysical prototype.
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