海上風(fēng)電機(jī)組齒輪傳動(dòng)系統(tǒng)設(shè)計(jì)【含CAD圖紙?jiān)次募?/h1>
海上風(fēng)電機(jī)組齒輪傳動(dòng)系統(tǒng)設(shè)計(jì)【含CAD圖紙?jiān)次募?含CAD圖紙?jiān)次募?海上,機(jī)組,齒輪,傳動(dòng)系統(tǒng),設(shè)計(jì),cad,圖紙,源文件
畢業(yè)設(shè)計(jì)（論文）任務(wù)書(shū)
機(jī)電工程 學(xué)院 機(jī)械設(shè)計(jì)制造及其自動(dòng)化 系（教研室）
系（教研室）主任: （簽名） 年 月 日
學(xué)生姓名: 專業(yè): 機(jī)械設(shè)計(jì)制造及其自動(dòng)化
1 設(shè)計(jì)（論文）題目及專題： 5MW海上風(fēng)電機(jī)組齒輪傳動(dòng)系統(tǒng)設(shè)計(jì)
2設(shè)計(jì)（論文）時(shí)間：自 2014 年 10 月 17 日開(kāi)始至 2015 年 06 月 01 日止
3 設(shè)計(jì)（論文）所用資源和參考資料：
① 5MW傳動(dòng)系統(tǒng)葉片額定轉(zhuǎn)速12.1rpm，額定發(fā)電機(jī)轉(zhuǎn)速1173.7rpm，齒輪箱傳動(dòng)比為97:1。(一級(jí)行星、二級(jí)斜齒輪)
② 國(guó)外REpower 5MW、Multibrid M5000等風(fēng)電機(jī)組齒輪傳動(dòng)系統(tǒng)的相關(guān)資料；相關(guān)教材，如《海上風(fēng)力發(fā)電機(jī)組設(shè)計(jì)》、《風(fēng)力機(jī)設(shè)計(jì)、制造與運(yùn)行)》等；圖書(shū)館電子資源數(shù)據(jù)庫(kù)搜集到的期刊論文，博士、碩士學(xué)位論文等。
4 設(shè)計(jì)（論文）應(yīng)完成的主要內(nèi)容：
1) 完成5MW海上風(fēng)電機(jī)組齒輪箱傳動(dòng)形式、傳動(dòng)比分配等設(shè)計(jì)與計(jì)算；
2) 完成傳動(dòng)軸、齒輪、軸承等關(guān)鍵傳動(dòng)零部件的選擇、設(shè)計(jì)、計(jì)算與校核；
3) 查閱相關(guān)文獻(xiàn)資料，撰寫(xiě)開(kāi)題報(bào)告；
4) 完成相關(guān)論文的翻譯(英譯中，不少于3000字)。
5 提交設(shè)計(jì)（論文）形式（設(shè)計(jì)說(shuō)明與圖紙或論文等）及要求：
1) 完成5MW海上風(fēng)電機(jī)組傳動(dòng)系統(tǒng)設(shè)計(jì)，提供傳動(dòng)系統(tǒng)3D模型，裝配圖、零件圖等共折合A0圖紙不少于2.5張；
2) 設(shè)計(jì)計(jì)算說(shuō)明書(shū)一份，畢業(yè)設(shè)計(jì)說(shuō)明書(shū)的書(shū)寫(xiě)格式和版面要求參照《湖南科技大學(xué)本科生畢業(yè)設(shè)計(jì)（論文）要求與撰寫(xiě)規(guī)范》，說(shuō)明書(shū)不少于40頁(yè)。
6 發(fā)題時(shí)間： 年 10 月 17 日
指導(dǎo)教師： （簽名）
學(xué) 生： （簽名）
畢 業(yè) 設(shè) 計(jì)（ 論 文 ）
題目
5MW海上風(fēng)電機(jī)組齒輪動(dòng)系統(tǒng)設(shè)計(jì)
作者
學(xué)院
專業(yè)
學(xué)號(hào)
指導(dǎo)教師
年五月二十一日
附件2：任務(wù)書(shū)示例
畢業(yè)設(shè)計(jì)（論文）任務(wù)書(shū)
機(jī)電工程學(xué) 院 系（教研室）
系（教研室）主任: （簽名） 年 月 日
學(xué)生姓名: 學(xué)號(hào): 專業(yè):
1 設(shè)計(jì)（論文）題目及專題：
2 學(xué)生設(shè)計(jì)（論文）時(shí)間：自 年 月 日開(kāi)始至 年 月 日止
3 設(shè)計(jì)（論文）所用資源和參考資料：
4 設(shè)計(jì)（論文）應(yīng)完成的主要內(nèi)容：
5 提交設(shè)計(jì)（論文）形式（設(shè)計(jì)說(shuō)明與圖紙或論文等）及要求：
6 發(fā)題時(shí)間： 年 月 日
指導(dǎo)教師： （簽名）
學(xué) 生： （簽名）
附件3：指導(dǎo)人評(píng)語(yǔ)示例
畢業(yè)設(shè)計(jì)（論文）指導(dǎo)人評(píng)語(yǔ)
[主要對(duì)學(xué)生畢業(yè)設(shè)計(jì)（論文）的工作態(tài)度，研究?jī)?nèi)容與方法，工作量，文獻(xiàn)應(yīng)用，創(chuàng)新性，實(shí)用性，科學(xué)性，文本（圖紙）規(guī)范程度，存在的不足等進(jìn)行綜合評(píng)價(jià)]
指導(dǎo)人： （簽名）
年 月 日
指導(dǎo)人評(píng)定成績(jī)：
附件4：評(píng)閱人評(píng)語(yǔ)示例
畢業(yè)設(shè)計(jì)（論文）評(píng)閱人評(píng)語(yǔ)
[主要對(duì)學(xué)生畢業(yè)設(shè)計(jì)（論文）的文本格式、圖紙規(guī)范程度，工作量，研究?jī)?nèi)容與方法，實(shí)用性與科學(xué)性，結(jié)論和存在的不足等進(jìn)行綜合評(píng)價(jià)]
評(píng)閱人： （簽名）
年 月 日
評(píng)閱人評(píng)定成績(jī)：
附件5：答辯記錄示例
畢業(yè)設(shè)計(jì)（論文）答辯記錄
日期：
學(xué)生： 學(xué)號(hào)： 班級(jí)：
題目：
提交畢業(yè)設(shè)計(jì)（論文）答辯委員會(huì)下列材料：
1 設(shè)計(jì)（論文）說(shuō)明書(shū) 共 頁(yè)
2 設(shè)計(jì)（論文）圖 紙 共 頁(yè)
3 指導(dǎo)人、評(píng)閱人評(píng)語(yǔ) 共 頁(yè)
畢業(yè)設(shè)計(jì)（論文）答辯委員會(huì)評(píng)語(yǔ)：
[主要對(duì)學(xué)生畢業(yè)設(shè)計(jì)（論文）的研究思路，設(shè)計(jì)（論文）質(zhì)量，文本圖紙規(guī)范程度和對(duì)設(shè)計(jì)（論文）的介紹，回答問(wèn)題情況等進(jìn)行綜合評(píng)價(jià)]
答辯委員會(huì)主任： （簽名）
委員： （簽名）
（簽名）
（簽名）
（簽名）
答辯成績(jī)：
總評(píng)成績(jī)：
NOTICE
The submitted manuscript has been offered by an employee of the Midwest Research Institute (MRI), a contractor of the US Government under Contract No. DE-AC36-99GO10337. Accordingly, the US Government and MRI retain a nonexclusive royalty-free license to publish or reproduce the published form of this contribution, or allow others to do so, for US Government purposes.
This report was prepared as an account of work sponsored by an agency of the United States government. Neither the United States government nor any agency thereof, nor any of their employees, makes any warranty, express or implied, or assumes any legal liability or responsibility for the accuracy, completeness, or usefulness of any information, apparatus, product, or process disclosed, or represents that its use would not infringe privately owned rights. Reference herein to any specific commercial product, process, or service by trade name, trademark, manufacturer, or otherwise does not necessarily constitute or imply its endorsement, recommendation, or favoring by the United States government or any agency thereof. The views and opinions of authors expressed herein do not necessarily state or reflect those of the United States government or any agency thereof.
Available electronically at http://www.osti.gov/bridge
Available for a processing fee to U.S. Department of Energy and its contractors, in This paper describes a new research and development initiative to improve gearbox reliability in wind turbines begun at the National Renewable Energy Laboratory (NREL) in Golden, Colorado, USA. The approach involves a collaboration of NREL staff, expert consultants, and partners from the wind energy industry who have an interest in improving gearbox reliability. The membership of this collaborative is still growing as the project becomes more defined, but the goal is to include representatives ranging from the operators, owners, wind turbine manufacturers, gearbox manufacturers, bearing manufacturers, consultants, and lubrication industries. The project is envisioned to be a multi-year comprehensive testing and analysis effort. This will include complementary laboratory and field testing on a 600 to 750-kW turbine and gearbox of a configuration that exhibits reliability problems common to a broad population of turbines. The project will target deficiencies in the design process that are contributing to substantial shortfalls in service life for most designs. New design-analysis tools will be developed to model the test configuration in detail. This will include using multi-body dynamic analysis to model wind turbine loading, coupled to internal loading and deformations of the gearbox. Intellectual property conflicts will be minimized by maintaining a test configuration that does not replicate any specific manufacturer’s wind turbine model precisely, but represents a common configuration.
Background
The wind energy industry has experienced high gearbox failure rates from its inception [1]. Early wind turbine designs were fraught with fundamental gearbox design errors compounded by consistent under-estimation of the operating loads. The industry has learned from these problems over the past two decades with wind turbine manufacturers, gear designers, bearing manufacturers, consultants, and lubrication engineers all working together to improve load prediction, design, fabrication, and operation. This collaboration has resulted in internationally recognized gearbox wind turbine design standards [2]. Despite reasonable adherence to these accepted design practices, wind turbine gearboxes have yet to achieve their design life goals of twenty years, with most systems requiring significant repair or overhaul well before the intended life is reached [3,4,5]. Since gearboxes are one of the most expensive components of the wind turbine system, the higherthan-expected failure rates are adding to the cost of wind energy. In addition, the future uncertainty of gearbox life expectancy is contributing to wind turbine price escalation. Turbine manufacturers add large contingencies to the sales price to cover the warranty risk due to the possibility of premature gearbox failures. In addition, owners and operators build contingency funds into the project financing and income expectations for problems that may show up after the warranty expires. To help bring the cost of wind energy back to a decreasing trajectory, a significant increase in long-term gearbox reliability needs to be demonstrated.
In response to design deficiencies, modification and redesign of existing turbines is a continual process in current production units, but it is difficult to validate the effectiveness of the modifications in a timely manner to assure that multiple units with unsatisfactory “solutions” are not deployed. Presently, gear manufacturers introduce modifications to new models, replacing a deficient component with a re-engineered one that is
1 thought to deliver higher performance. To test these new designs, the re-engineered gearboxes are installed and a field evaluation process begins. This approach may eventually lead to the reliability goals needed, but it may take many years to develop the needed confidence in a solution, and reduce the uncertainty to a level where it will reduce turbine costs. By that time, the wind turbine industry may have moved to larger turbines or different drivetrain arrangements that could invalidate these solutions. Moreover, the fundamental failure mechanisms of the original problem may never be understood, making it easier for design unknowns to be inadvertently propagated into the next generation of machines.
This paper summarizes a long-term NREL/DOE project to explore options to accelerate improvements in wind turbine gearbox reliability by addressing the problems directly within the design process. In the execution of this program, our intentions are to improve the accuracy of dynamic gearbox testing to assess gearbox and drivetrain options, problems, and solutions under simulated field conditions. The project will evaluate the wide range of possible load events that comprise the design load spectrum [6], and how critical design-load cases
[7] may translate into unintended bearing and gear responses such as misalignment, bearing slip, and axial motion.
NREL has made a commitment to address gearbox reliability as a major part of its research agenda, and plans to engage a wide range of stakeholders including researchers, consultants, bearing manufacturers, gearbox manufacturers, wind turbine manufacturers, and wind turbine owner/operators to form a gearbox reliability collaborative (GRC). The collaborative will address major gearbox issues with the common goal of increasing overall reliability of wind turbines. The approach will involve three major technical efforts which include field testing, dynamometer testing, and drivetrain analysis. These elements make up a comprehensive strategy that will address the true nature of the problem and hopefully spark a spirit of cooperation that can lead to better gearboxes.
Observations on the Basic Problems
While it is premature to draw firm conclusions about the nature of these failures, some reasonable observations have been made to help narrow the course and scope of this project.
1. Most of the problems with the current fleet of wind turbine gearboxes are generic in nature, meaning that the problems are not specific to a single gear manufacturer or turbine model. Over the years, most wind turbine gearbox designs have converged to a similar architecture with only a few exceptions. Therefore, there is an opportunity to collaborate among the many stakeholders in the wind turbine gearbox supply chain to find root causes of failures and investigate solutions that may advance the collective understanding of the industry.
2. The preponderance of gearbox failures suggests that poor adherence to accepted gear industry practices, or otherwise poor workmanship, is NOT the primary source of failures. Of course, some failures have been directly attributed to quality issues, and further improvements in this area are not precluded from consideration, but we assume that manufacturers are capable of identifying and correcting quality control problems on their own if they choose to do so. Therefore, the target of this project will be the greater problem of identifying and correcting deficiencies in the design process that may be diminishing the life of the fleet.
3. Most gearbox failures do not begin as gear failures or gear-tooth design deficiencies. The observed failures appear to initiate at several specific bearing locations under certain applications, which may later advance into the gear teeth as bearing debris and excess clearances cause surface wear and misalignments. Anecdotally, field-failure assessments indicate that up to 10% of gearbox failures may be manufacturing anomalies and quality issues that are gear related, but this is not the primary source of the problem.
4. The majority of wind turbine gearbox failures appear to initiate in the bearings. These failures are occurring in spite of the fact that most gearboxes have been designed and developed using the best bearing-design practices available. Therefore, the initial focus of this project will be on discovering weaknesses in wind turbine gearbox bearing applications and deficiencies in the design process.
2 Furthermore, we believe that the problems that manifested themselves in the earlier 500-kW to 1000kW sizes five to ten years ago still exist in many of the larger 1 to 2 MW gearboxes being built today with the same architecture. As such, it is likely that lessons learned in solving problems on the smaller scale can be applied directly to future wind turbines at a larger scale, but with less cost.
Using these observations to help bound the problem, we reason that the accepted design practices that are applied successfully throughout other industrial bearing applications must be deficient when applied to wind turbine gearboxes. This characterization is based primarily on anecdotal field-failure data, and the experience of gear and bearing experts who have studied the problems for many years. Unfortunately, the available analytical methods to assess design life in typical gearbox designs are not accurate enough to shed much light on this problem, so much of the investigation must be conducted empirically.
A major factor contributing to the complexity of the problem is that much of the bearing design-life assessment process is proprietary to the bearing manufacturers. Gearbox designers, working with the bearing manufacturers, initially select the bearing for a particular location and determine the specifications for rating. The bearing manufacturer then conducts a fatigue life rating analysis to determine if the correct bearing has been selected for the specific application and location. Generally, a high degree of faith is required to accept the outcome of this analysis because it is done with little transparency. Even though bearing manufacturers claim adherence to international bearing- rating standards (ISO 281:2007 [8]), each manufacturer uses its internally developed design codes that have the potential to introduce significant differences that can affect actual calculated bearing life without revealing the details to customers. A new code is needed in the public domain that will give the industry a common method for due diligence in bearing design [9].
Moreover, since the bearing manufacturers do not have broad or intimate knowledge of gearbox system loads and responses that may be contributing to unpredicted bearing behavior beyond the bearing mounting location such as housing deformations, they are not capable of making valid root-cause analyses on their own. A broader collaboration of the various stakeholders, each of whom holds a piece of the answer, is clearly needed.
Gearbox Reliability Collaborative
Many of the gearbox problems described above may be the direct result of institutional barriers that hinder communication and feedback during the design, operation, and maintenance of turbines. In isolation, it is very difficult for single entities in the supply chain to find proper solutions. Hence, a collaborative is needed to bring together the various portions of the design process, and to share information needed to address the problems. This promises to be one of the more challenging parts of this project, as information sharing introduces perceived risk to the protection of intellectual property, which is guarded dearly by most companies. A goal of this project is to establish this cooperative framework while protecting the intellectual property rights of all parties. These concerns will be addressed through legal agreements with NREL, and will be further mitigated since the project does not focus on any manufacturer’s specific design. The collaborative is operated by NREL staff and expert consultants hired by NREL to guarantee privacy of commercially sensitive information and data. In addition, a goal of the collaborative is to engage key representatives of the supply chain, including turbine owners, operators, gearbox manufacturers, bearing manufacturers, lubrication companies, and wind turbine manufacturers. Each party holds information and experience that is needed to guide the project, supply the components, and interpret results of the test. The collaborative partners will benefit by having input throughout the testing setup and execution, and will have access to data within the agreements established by the cooperative. Results will be released by the GRC as agreed upon by its members.
Generic Wind Turbine Drivetrain Architecture
The selected configuration is comprised of a single main bearing upwind of the gearbox with rear non-locating support bearings inside the gearbox. Trunnion mounts on either side of the gearbox are used to attach it to a mainframe or bedplate, typically through elastomeric bushings used to dampen noise and vibrations. Torque reactions are resolved through the trunnion support assembly that is normally an integral part of the gear housing. The external geometry of this configuration is shown in
The low speed stage of the gearbox is a planetary configuration with either spur or helical gears. The sun pinion drives a parallel intermediate shaft that in turn drives a high speed stage. Both the intermediate and high speed stages use helical gears. A generalized schematic of a typical wind turbine gearbox is shown in Figure 2. 4
Critical bearing locations are defined as places that have exhibited a high percentage of application failures in spite of the use of best current design practices. In the generic configuration, there are three critical bearing locations that we have identified:
1. Planet bearings
2. Intermediate shaft-locating bearings
3. High-speed locating bearings
Each location has exhibited a relatively high degree of bearing failures with a relatively low dependence on machine size, machine make, or model.
A Three Point Plan
As previously mentioned, some aspects of the wind turbine, gearbox, and bearing design process are preventing gearboxes from reaching expected life. These deficiencies could be the result of many factors, including:
? the possibility that one or more critical design-load cases were not accounted for in the design load spectrum,
? that transfer of loads (both primary torque loads and non-torque loads) from the shaft and mounting reactions is occurring in a non-linear or unpredicted manner, or
? that components within the gearbox (especially the bearings) are not uniformly specified to deliver the same level of reliability.
Due to the complexity of this problem, a comprehensive approach that expands our existing base of knowledge and capabilities will be required. Under this project, NREL plans an integrated three-pronged approach of analysis, dynamometer testing, and field testing as shown in Figure 3.
Figure 3 - Comprehensive Strategy to Investigate Wind Turbine Gearbox Reliability
5 Laboratory testing of a representative instrumented drivetrain in the NREL 2.5-MW dynamometer will be coordinated with parallel field tests on an identical instrumented drivetrain conducted at a nearby wind farm site. With the benefit of hindsight, the selected drivetrain will be upgraded prior to testing to current state-ofthe-art to eliminate known design weaknesses and quality issues as best as possible. These upgrades may include different bearing types, cooling and filtration system upgrades, lubrication changes, and gear tooth modifications. The test specimens will therefore not be precise representations of any manufacturer’s design. The laboratory and field measurements will be validated with dynamic analysis using an accurate structural-system model of the selected drivetrain.
The test will be based on a 600 to 750-kW wind turbine selected by a committee of expert gearbox consultants hired by NREL under the GRC. The exact details of the drivetrain to be tested and analyzed are confidential to the members of the GRC. Project success will be highly dependent on making the right measurements that correctly characterize the behavior of the critical bearings under various loading scenarios. Instruments will be developed and installed to capture data about significant loads, deflections, thermal effects, dynamic responses and events, and changes to the condition of the lubricant.
Critical loads measurements will include shaft bending and torque on the input shafts, but also measurements of how load sharing varies dynamically from one planet bearing to another. Similarly, measurements will be made to determine how the load is being shared between bearings axially along a single planet shaft. Displacement sensors to make continuous measurements will be installed internally, if possible, wherever gear tooth clearances or alignments of the gears might be affected. These locations may include bearing inner ring to outer ring alignments and clearances, shaft axial motions, bearing slip (inner or outer motions or bearing components), roller slipping or skidding, combined roller slip, relative motion of carrier to housing, sun pinion displacement relative to carrier, sun-pinion axial motion, housing stiffness, and displacement measurements of housing. We anticipate that certain locations will be difficult to access with standard instrumentation. Temperature measurements will be made at all critical bearing locations, including the inner rings, the outer rings, and planet bearings. Lubrication monitoring will include bulk sump temperature, cleanliness (e.g., particulate, ferrous, additive, and water), and filter debris. Laboratory analysis will be conducted frequently on all test specimens.
The test data will be analyzed and correlated to look for bearing behavior that is unexpected, non-linear, or is suspect under a wide range of input conditions. If this behavior can be correctly documented and understood, it may not be necessary to reproduce every type of bearing failure if subsequent analysis can demonstrate that certain abnormal behavior can result in loss of bearing life.
Dynamometer Testing
The National Renewable Energy Laboratory operates a 2.5-MW dynamometer test facility funded by the U.S. Department of Energy at its National Wind Technology Center in Golden, CO that is dedicated to the testing of wind turbine drive trains [12]. Since 1999, this facility has been in continuous operation providing testing services to prototype and production wind turbine drive trains up to 2 MW in size. NREL plans to use this facility and its support staff to conduct full-scale tests on the 750-kW drivetrain selected. A schematic of the facility is shown in Figure 4.
One of the benefits of using a full scale drive-train