China excellent quality 30HP OEM 61N-45501-00 DRIVE SHAFT for yamaha parsun Oversea boat custom drive shaft shop

Problem: New
保修：不可用
Applicable Industries: Producing Plant, Equipment Fix Stores, Farms, Property Use, Construction works
Showroom Location: None
Video clip outgoing-inspection: Offered
Equipment Examination Report: Offered
Advertising and marketing Sort: Very hot Solution 2019
Guarantee of core factors: 3 months
Core Factors: Gear
Structure: Spline
Substance: OCr17Ni4Cu4Nb, 20CrMnTi
Coatings: sprucing
Torque Ability:
Product Quantity: 61N-45501-00
Tooth Number: 14T
Module: one
Weight: 1192g
Packing: 4*4*80cm
Product identify: driver shaft
OEM: 61N-45501-00
Hardness: fifty seven-60
Soon after Warranty Service: On the web assist
Local Service Location: None
Port: HangZhou/ZheJiang

1、We have Yamaha/Tohatsu/Suzuki Marine spare elements.2、At the exact same time, we are also the first supplier of Parsun/Hidea.3、 In purchase to estimate far more efficiently, remember to ship us your quantity and OEM number or photographs when you seek the advice of us, thank you!4、Also, if you want freight, you should permit us know your nation and zip code.

Spline parameters
Enamel	Z	14T
Module	m	1
Entire diameter	Dee	ᴓ15.nine
Minimal diameter	Die	ᴓ13.6

664-45631-00CLUTCH Dog

61N-45560-00

61N-45551-0061N-45570-00

outboard gears

65W-45611-00  PROPELLER SHAFTOrganization Introduction       Proven in 2016,HangZhou gill transmission elements company is a company specialized in the analysis,development andproduction of equipment. We are located in ZHangZhoug,with convenient transporttation access.     Company previously known as Xihu (West Lake) Dis. HangZhou equipment manufacturing facility, was launched in 1997, has twenty years of equipment manufacturing experience HangZhou full set of imported processing products.      HangZhou gill transmission elements firm move to a new manufacturing facility, proven in 2016 .Normal workshop a lot more than20-5 thousand square, covers an spot of far more than fifteen thousand sq. meters. Why Decide on UsOur Solutions & Energy1、Our firm has been providing outboard equipment fittings for China’ Lower Intermediate Steering Shaft u-joint coupling s outboard equipment assembly plant for a prolonged time.2、We have YAMAHA, SUZUKI, TOHATSU and other outboard equipment accessories, as nicely as the HIDEA, PARSUN, PANIR and other outboard equipment components of the first manufacturing unit.3、 we can do custom processing for you.4、The quality of our merchandise is steady, and we have extended-phrase buyers in Russia, Spain, Africa and other areas. Related ProductsExhibition Packing&Transport Certifications FAQone. Merchandise ORIGIN?All of our products are created in China.2. MOQ?MOQ is not the very same for diverse products.3. Delivery TIME?Supply time is dependent on the real orders, usually we have stock, acquired the deposit 7-15 days soon after supply.4. WHAT IS THE Package FOR Merchandise?a. QTY significantly less than MOQ: neutral package deal or our box deal.b. QTY much more than MOQ: our bundle or in accordance to client’s need.c. Shipping and delivery Mark: normal mark or in accordance to client’s requirement.

样条联轴器的刚度和扭转振动

本文描述了花键联轴器的一些基本特性，并研究了其扭转振动特性。我们还探讨了花键不对中对转子-花键联轴器性能的影响。这些结果将有助于设计适用于各种应用的改进型花键联轴器系统。结果如表1所示。

样条联轴器的刚度

转子-花键联轴器的刚度取决于花键间的啮合力以及静态振动位移。啮合力取决于联轴器的参数，例如传递扭矩和花键厚度。它随花键厚度的增加呈非线性增长。
简化的花键耦合模型可用于评估花键在振动和瞬态载荷下的载荷分布。该模型中，轴花键套筒沿z方向发生位移，并在套筒外表面施加阻力矩T。这种简化的模型能够满足广泛的工程需求，但在复杂的载荷条件下可能存在缺陷。其不对称间隙可能会影响其啮合性能和应力分布模式。
仿真结果表明，图 10 和图 22 中的最大振动加速度均为 3.03 g/s。该结果表明，周向错位会增大瞬时冲击。啮合情况也存在耦合几何形状的不对称性。右侧样条齿轮的齿紧密啮合，而左侧样条齿轮的齿则错位啮合。
考虑到样条耦合器的几何形状，采用半解析模型计算刚度。该模型是经典样条耦合器模型的简化形式，其子矩阵定义了连接的形状和刚度。由于设计间隙已知，因此可以使用相同的公式分析样条耦合系统的刚度。
仿真结果还表明，可以使用MASTA（一款用于传动分析的高级商业CAE工具）对花键联轴器系统进行建模。在本例中，花键段被建模为一系列具有可变刚度的花键段，其刚度基于花键齿间的初始间隙计算得出。然后，为了考虑不同的制造偏差，将花键段建模为一系列刚度递增的花键。最后，将花键联轴器几何形状的分析结果与有限元方法的结果进行了比较。
尽管花键联轴器系统具有很高的刚度，但接触面的接触状态经常发生变化。此外，花键联轴器还会影响转子的横向振动和变形。然而，由于缺乏完全解析的模型，花键转子的刚度非线性特性尚未得到充分研究。

样条联轴器的特性

样条联轴器的研究涉及诸多设计因素，包括重量、材料和性能要求。重量在航空领域尤为重要。由于材料的尺寸稳定性、重量和耐久性各不相同，重量往往是设计工程师需要考虑的问题。此外，空间限制和其他结构限制也可能导致某些应用中必须使用样条联轴器。
The main parameters to consider for any spline-coupling design are the maximum principal stress, the maldistribution factor, and the maximum tooth-bearing stress. The magnitude of each of these parameters must be smaller than or equal to the external spline diameter, in order to provide stability. The outer diameter of the spline must be at least four inches larger than the inner diameter of the spline.
物理设计验证完成后，即可创建样条耦合器知识库。该模型预先编程，存储设计参数信号，包括性能和制造约束。然后，它将参数值与设计规则信号进行比较，并构建样条耦合器的几何表示。根据输入信号生成可视化模型，可通过更改不同的参数和规范对其进行操作。
花键接头的刚度是决定花键联轴器刚度的另一个重要参数。花键接头的刚度分布会影响转子的横向振动和变形。有限元法是获取花键接头横向刚度的有效方法。该方法需要进行大量的网格细化，计算成本较高。
花键联轴器的直径必须足够大才能传递扭矩。直径较大的花键由于周长较小，因此可能具有更大的扭矩传递能力。然而，直径较大的花键比轴细，如果扭矩分散到更多齿上，轴可能更合适。
花键联轴器根据其沿轴向和径向的齿形进行分类。径向和轴向齿形会影响部件的性能和磨损损伤。具有冠状齿形的花键容易出现角度偏差。通常，为了确保耐用性和安全性，这些花键联轴器的尺寸会偏大。

扭转振动分析中样条耦合的刚度

This article presents a general framework for the study of torsional vibration caused by the stiffness of spline-couplings in aero-engines. It is based on a previous study on spline-couplings. It is characterized by the following three factors: bending stiffness, total flexibility, and tangential stiffness. The first criterion is the equivalent diameter of external and internal splines. Both the spline-coupling stiffness and the displacement of splines are evaluated by using the derivative of the total flexibility.
花键连接的刚度会随沿花键的载荷分布而变化。影响花键连接刚度的变量包括扭矩水平、齿位定位误差和不对中。为了探究这些变量的影响，本文建立了一个解析公式。该方法适用于各种类型的花键连接，例如多部件花键。
尽管计算花键联轴器的刚度较为困难，但仍可采用解析方法模拟轴齿与轮毂之间的接触。该方法有助于确定联轴器运行的关键参数，例如接触峰值压力、反作用力矩和角动量。该方法能够获得花键联轴器的精确结果，适用于扭转振动和结构振动分析。
在动态模型中，通常假设样条联轴器的刚度为刚性。然而，高保真传动系统模型必须捕捉与样条连接相关的各种动态现象。为此，本文基于半解析样条载荷分布模型，提出了一种通用的解析刚度公式。所得刚度矩阵包含径向刚度、倾斜刚度和扭转刚度。此外，采用分块反演法进一步简化了分析过程。
在选择联轴器之前，必须考虑动力传输系统的扭转振动。对扭转振动进行精确分析对于联轴器的安全至关重要。本文还讨论了花键轴磨损和扭转引起的失效案例。最后，本文将提出一种稳健高效的方法，用于模拟实际场景中的这些问题。

花键错位对转子-花键联轴器的影响

本研究探讨了转子-花键联轴器中花键错位的影响，分析了其稳定性边界和转子失稳机理。研究发现，错位花键联轴器的啮合力随花键厚度呈非线性增长。结果表明，错位是导致转子-花键联轴器系统失稳的原因。
为了实现过盈配合和零齿隙，人为地引入了花键错位。这导致花键齿间载荷分布不均。进一步增加50μm的花键错位会导致转子-花键联轴器失效。在这种情况下，最大拉伸根应力向左偏移。
正花键错位会加剧齿轮啮合错位。相反，负花键错位则没有影响。右旋花键错位与螺旋方向相反。高接触面积从中心移至左侧。在这两种情况下，齿轮啮合错位都是由于齿轮在负载作用下的挠曲和倾斜造成的。
This variation of the tooth surface is measured as the change in clearance in the transverse plain. The radial and axial clearance values are the same, while the difference between the two is less. In addition to the frictional force, the axial clearance of the splines is the same, which increases the gear mesh misalignment. Hence, the same procedure can be used to determine the frictional force of a rotor-spline coupling.
齿轮啮合不对中会影响花键转子联轴器的性能。这种不对中会改变齿轮啮合的分布，并改变接触应力和弯曲应力。因此，了解花键联轴器中不对中的影响至关重要。Hong等人利用简化的螺旋齿轮副系统，研究了花键齿面界面的载荷分布。这种不对中导致齿面接触模式发生变化。不对中的齿在载荷作用下会发生挠曲，并在齿轮上产生倾覆力矩。
The effect of spline misalignment in rotor-spline couplings is minimized by using a mechanism that reduces backlash. The mechanism comprises cooperably splined male and female members. One member is formed by two coaxially aligned splined segments with end surfaces shaped to engage in sliding relationship. The connecting device applies axial loads to these segments, causing them to rotate relative to one another.

editor by czh 2023-02-17