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| Material | Alloy Steel, Copper alloy(brass,silicon bronze,phosphor bronze,aluminum bronze,beryllium copper),Stainless Steel,Aluminum,Titanium, Magnesium, Superalloys,Molybdenum, Invar,,Zinc,Tungsten steel,incoloy,Nickel 200,Hastelloy, Inconel,Monel,ABS, PEEK,PTFE,PVC,Acetal. |
| Surface Treatment | Zn-plating, Ni-plating, Cr-plating, Tin-plating, copper-plating, the wreath oxygen resin spraying, the heat disposing, hot-dip galvanizing, black oxide coating, painting, powdering, color zinc-plated, blue black zinc-plated, rust preventive oil, titanium alloy galvanized, silver plating, plastic, electroplating, anodizing etc. |
| Producing Equipment | CNC machine,automatic lathe machine,CNC milling machine,lasering,tag grinding machine etc. |
| Drawing Format | Pro/E, Auto CAD, CZPT Works, UG, CAD/CAM, PDF |
| Managing Returned Goods | With quality problem or deviation from drawings |
| Warranty | Replacement at all our cost for rejected products |
| Main Markets | North America, South America, Eastern Europe , West Europe , North Europe, South Europe, Asia |
| How to order | * You send us drawing or sample |
| * We carry through project assessment | |
| * We make the sample and send it to you after you confirmed our design | |
| * You confirm the sample then place an order and pay us 30% deposit | |
| * We start producing | |
| * When the goods is done, you pay us the balance after you confirmed pictures or tracking numbers. | |
| * Trade is done, thank you!! |
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FAQ
Q1:What kind of information do you need for quotation?
A: You can provide 2D/3D drawing or send your sample to our factory, then we can make according to your sample.
Q2: Can we CZPT NDA?
A: Sure. We can CZPT the NDA before got your drawings.
Q3: Do you provide sample?
A: Yes, we can provide you sample before mass order.
Q4: How can you ensure the quality?
A: We have profesional QC,IQC, OQC to guarantee the quality.
Q5: Delivery time?
A: For samples genearlly need 25 days. Mass production: around 30~45 days after receipt of deposit (Accurate delivery time
depends on specific items and quantities)
Q6: How about the transportation?
A: You can choose any mode of transportation you want, sea delivery, air delivery or door to door express.
| Layout: | Three-Ring |
|---|---|
| Hardness: | Hardened Tooth Surface |
| Tolerance: | +/- 0.005mm, According to Your Specification |
| MOQ: | 10PCS |
| Process: | CNC Machining/CNC Turning/CNC Milling/CNC Lathe |
| Material Capabilities: | Aluminum, Brass, Steel, Titanium etc. |
| Customization: |
Available
| Customized Request |
|---|
Stiffness and Torsional Vibration of Spline-Couplings
In this paper, we describe some basic characteristics of spline-coupling and examine its torsional vibration behavior. We also explore the effect of spline misalignment on rotor-spline coupling. These results will assist in the design of improved spline-coupling systems for various applications. The results are presented in Table 1.
Stiffness of spline-coupling
The stiffness of a spline-coupling is a function of the meshing force between the splines in a rotor-spline coupling system and the static vibration displacement. The meshing force depends on the coupling parameters such as the transmitting torque and the spline thickness. It increases nonlinearly with the spline thickness.
A simplified spline-coupling model can be used to evaluate the load distribution of splines under vibration and transient loads. The axle spline sleeve is displaced a z-direction and a resistance moment T is applied to the outer face of the sleeve. This simple model can satisfy a wide range of engineering requirements but may suffer from complex loading conditions. Its asymmetric clearance may affect its engagement behavior and stress distribution patterns.
The results of the simulations show that the maximum vibration acceleration in both Figures 10 and 22 was 3.03 g/s. This results indicate that a misalignment in the circumferential direction increases the instantaneous impact. Asymmetry in the coupling geometry is also found in the meshing. The right-side spline’s teeth mesh tightly while those on the left side are misaligned.
Considering the spline-coupling geometry, a semi-analytical model is used to compute stiffness. This model is a simplified form of a classical spline-coupling model, with submatrices defining the shape and stiffness of the joint. As the design clearance is a known value, the stiffness of a spline-coupling system can be analyzed using the same formula.
The results of the simulations also show that the spline-coupling system can be modeled using MASTA, a high-level commercial CAE tool for transmission analysis. In this case, the spline segments were modeled as a series of spline segments with variable stiffness, which was calculated based on the initial gap between spline teeth. Then, the spline segments were modelled as a series of splines of increasing stiffness, accounting for different manufacturing variations. The resulting analysis of the spline-coupling geometry is compared to those of the finite-element approach.
Despite the high stiffness of a spline-coupling system, the contact status of the contact surfaces often changes. In addition, spline coupling affects the lateral vibration and deformation of the rotor. However, stiffness nonlinearity is not well studied in splined rotors because of the lack of a fully analytical model.
Characteristics of spline-coupling
The study of spline-coupling involves a number of design factors. These include weight, materials, and performance requirements. Weight is particularly important in the aeronautics field. Weight is often an issue for design engineers because materials have varying dimensional stability, weight, and durability. Additionally, space constraints and other configuration restrictions may require the use of spline-couplings in certain applications.
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.
Once the physical design is validated, the spline coupling knowledge base is created. This model is pre-programmed and stores the design parameter signals, including performance and manufacturing constraints. It then compares the parameter values to the design rule signals, and constructs a geometric representation of the spline coupling. A visual model is created from the input signals, and can be manipulated by changing different parameters and specifications.
The stiffness of a spline joint is another important parameter for determining the spline-coupling stiffness. The stiffness distribution of the spline joint affects the rotor’s lateral vibration and deformation. A finite element method is a useful technique for obtaining lateral stiffness of spline joints. This method involves many mesh refinements and requires a high computational cost.
The diameter of the spline-coupling must be large enough to transmit the torque. A spline with a larger diameter may have greater torque-transmitting capacity because it has a smaller circumference. However, the larger diameter of a spline is thinner than the shaft, and the latter may be more suitable if the torque is spread over a greater number of teeth.
Spline-couplings are classified according to their tooth profile along the axial and radial directions. The radial and axial tooth profiles affect the component’s behavior and wear damage. Splines with a crowned tooth profile are prone to angular misalignment. Typically, these spline-couplings are oversized to ensure durability and safety.
Stiffness of spline-coupling in torsional vibration analysis
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.
The stiffness of a spline joint can vary based on the distribution of load along the spline. Variables affecting the stiffness of spline joints include the torque level, tooth indexing errors, and misalignment. To explore the effects of these variables, an analytical formula is developed. The method is applicable for various kinds of spline joints, such as splines with multiple components.
Despite the difficulty of calculating spline-coupling stiffness, it is possible to model the contact between the teeth of the shaft and the hub using an analytical approach. This approach helps in determining key magnitudes of coupling operation such as contact peak pressures, reaction moments, and angular momentum. This approach allows for accurate results for spline-couplings and is suitable for both torsional vibration and structural vibration analysis.
The stiffness of spline-coupling is commonly assumed to be rigid in dynamic models. However, various dynamic phenomena associated with spline joints must be captured in high-fidelity drivetrain models. To accomplish this, a general analytical stiffness formulation is proposed based on a semi-analytical spline load distribution model. The resulting stiffness matrix contains radial and tilting stiffness values as well as torsional stiffness. The analysis is further simplified with the blockwise inversion method.
It is essential to consider the torsional vibration of a power transmission system before selecting the coupling. An accurate analysis of torsional vibration is crucial for coupling safety. This article also discusses case studies of spline shaft wear and torsionally-induced failures. The discussion will conclude with the development of a robust and efficient method to simulate these problems in real-life scenarios.
Effect of spline misalignment on rotor-spline coupling
In this study, the effect of spline misalignment in rotor-spline coupling is investigated. The stability boundary and mechanism of rotor instability are analyzed. We find that the meshing force of a misaligned spline coupling increases nonlinearly with spline thickness. The results demonstrate that the misalignment is responsible for the instability of the rotor-spline coupling system.
An intentional spline misalignment is introduced to achieve an interference fit and zero backlash condition. This leads to uneven load distribution among the spline teeth. A further spline misalignment of 50um can result in rotor-spline coupling failure. The maximum tensile root stress shifted to the left under this condition.
Positive spline misalignment increases the gear mesh misalignment. Conversely, negative spline misalignment has no effect. The right-handed spline misalignment is opposite to the helix hand. The high contact area is moved from the center to the left side. In both cases, gear mesh is misaligned due to deflection and tilting of the gear under load.
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.
Gear mesh misalignment influences spline-rotor coupling performance. This misalignment changes the distribution of the gear mesh and alters contact and bending stresses. Therefore, it is essential to understand the effects of misalignment in spline couplings. Using a simplified system of helical gear pair, Hong et al. examined the load distribution along the tooth interface of the spline. This misalignment caused the flank contact pattern to change. The misaligned teeth exhibited deflection under load and developed a tilting moment on the gear.
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 CX 2023-10-17
China AISI4140 Steel Carbon Steel 42CrMo 45# Steel 42CrMo4 Nitriding Gear Splined Input Shaft drive shaft components
12 months: Universal
Model: Common
OE NO.: oem
Car Fitment: Common
Dimension: oem
Materials: #forty five Metal
Model Number: oem
Guarantee: Months
Automobile Make: vehicle
Item identify: 34CrNiMo6 automobile cardan shaft
Software: Speaker/ tools/instrument
Certification: ISO16949
Surface Therapy: anodize
MOQ: 1 Piece
ColorCustom: Black
Drawing Format: 2nd/(PDF/CAD)3D(IGES/Action)
Packing: Carton Box
Support: OEM ODM
Processing Type: Axis CNC Machining Provider
Packaging Specifics: Our business has a skilled packaging department, which supplies the safest packaging prepare for the customer’s merchandise, ensuring the order to get there at the spot safely and securely, with zero injury.
Port: HangZhou
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YUKAI, positioned in HangZhou of ZheJiang province, China, recognized in 1977, is specialised in the processing of precision areas.
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Merchandise precisionThe diameter tolerance is .5μm, the coaxial precision is .2μm, the roundness precision is .3μm, and the surface roughness is Ra0.04. The processing variety of outer diameter is from .06mm to 300mm, and the assortment of length is .5mm ~2000mm.
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FAQ Q. Are you a factory or a trading business?A: We are a factory which has been specialized in cnc and grinding machining & precision elements for a lot more than 19 years.Q. Exactly where is your manufacturing unit and how can I go to it?A: Our manufacturing unit is found in HangZhou town and we can decide you up from HangZhou.Q. How extended can I get some samples for examining and what about the price?A: Normaly samples will be accomplished within 3-5 days (Normal components) or 5-7 day (Non-regular parts). The sample price relies upon on all info (dimensions, substance, complete, and so on.). We will return the sample value if your purchase amount is very good.Q.How to get an precise quotation?A: If you are interested in our items, make sure you offer us with beneath info:♦ Drawings, photographs or samples of products.♦ Thorough sizes of merchandise.♦ Material of goods.♦ Floor remedy of products.♦ Ordinary purchasing amount.Q. How is the guarantee of the goods quality management?A: We have QC section with wonderful QC method, we will often supply QC report and certification to client for checking.
Analytical Approaches to Estimating Contact Pressures in Spline Couplings
A spline coupling is a type of mechanical connection between two rotating shafts. It consists of two parts – a coupler and a coupling. Both parts have teeth which engage and transfer loads. However, spline couplings are typically over-dimensioned, which makes them susceptible to fatigue and static behavior. Wear phenomena can also cause the coupling to fail. For this reason, proper spline coupling design is essential for achieving optimum performance.
Modeling a spline coupling
Spline couplings are becoming increasingly popular in the aerospace industry, but they operate in a slightly misaligned state, causing both vibrations and damage to the contact surfaces. To solve this problem, this article offers analytical approaches for estimating the contact pressures in a spline coupling. Specifically, this article compares analytical approaches with pure numerical approaches to demonstrate the benefits of an analytical approach.
To model a spline coupling, first you create the knowledge base for the spline coupling. The knowledge base includes a large number of possible specification values, which are related to each other. If you modify one specification, it may lead to a warning for violating another. To make the design valid, you must create a spline coupling model that meets the specified specification values.
After you have modeled the geometry, you must enter the contact pressures of the two spline couplings. Then, you need to determine the position of the pitch circle of the spline. In Figure 2, the centre of the male coupling is superposed to that of the female spline. Then, you need to make sure that the alignment meshing distance of the two splines is the same.
Once you have the data you need to create a spline coupling model, you can begin by entering the specifications for the interface design. Once you have this data, you need to choose whether to optimize the internal spline or the external spline. You’ll also need to specify the tooth friction coefficient, which is used to determine the stresses in the spline coupling model 20. You should also enter the pilot clearance, which is the clearance between the tip 186 of a tooth 32 on one spline and the feature on the mating spline.
After you have entered the desired specifications for the external spline, you can enter the parameters for the internal spline. For example, you can enter the outer diameter limit 154 of the major snap 54 and the minor snap 56 of the internal spline. The values of these parameters are displayed in color-coded boxes on the Spline Inputs and Configuration GUI screen 80. Once the parameters are entered, you’ll be presented with a geometric representation of the spline coupling model 20.
Creating a spline coupling model 20
The spline coupling model 20 is created by a product model software program 10. The software validates the spline coupling model against a knowledge base of configuration-dependent specification constraints and relationships. This report is then input to the ANSYS stress analyzer program. It lists the spline coupling model 20’s geometric configurations and specification values for each feature. The spline coupling model 20 is automatically recreated every time the configuration or performance specifications of the spline coupling model 20 are modified.
The spline coupling model 20 can be configured using the product model software program 10. A user specifies the axial length of the spline stack, which may be zero, or a fixed length. The user also enters a radial mating face 148, if any, and selects a pilot clearance specification value of 14.5 degrees or 30 degrees.
A user can then use the mouse 110 to modify the spline coupling model 20. The spline coupling knowledge base contains a large number of possible specification values and the spline coupling design rule. If the user tries to change a spline coupling model, the model will show a warning about a violation of another specification. In some cases, the modification may invalidate the design.
In the spline coupling model 20, the user enters additional performance requirement specifications. The user chooses the locations where maximum torque is transferred for the internal and external splines 38 and 40. The maximum torque transfer location is determined by the attachment configuration of the hardware to the shafts. Once this is selected, the user can click “Next” to save the model. A preview of the spline coupling model 20 is displayed.
The model 20 is a representation of a spline coupling. The spline specifications are entered in the order and arrangement as specified on the spline coupling model 20 GUI screen. Once the spline coupling specifications are entered, the product model software program 10 will incorporate them into the spline coupling model 20. This is the last step in spline coupling model creation.
Analysing a spline coupling model 20
An analysis of a spline coupling model consists of inputting its configuration and performance specifications. These specifications may be generated from another computer program. The product model software program 10 then uses its internal knowledge base of configuration dependent specification relationships and constraints to create a valid three-dimensional parametric model 20. This model contains information describing the number and types of spline teeth 32, snaps 34, and shoulder 36.
When you are analysing a spline coupling, the software program 10 will include default values for various specifications. The spline coupling model 20 comprises an internal spline 38 and an external spline 40. Each of the splines includes its own set of parameters, such as its depth, width, length, and radii. The external spline 40 will also contain its own set of parameters, such as its orientation.
Upon selecting these parameters, the software program will perform various analyses on the spline coupling model 20. The software program 10 calculates the nominal and maximal tooth bearing stresses and fatigue life of a spline coupling. It will also determine the difference in torsional windup between an internal and an external spline. The output file from the analysis will be a report file containing model configuration and specification data. The output file may also be used by other computer programs for further analysis.
Once these parameters are set, the user enters the design criteria for the spline coupling model 20. In this step, the user specifies the locations of maximum torque transfer for both the external and internal spline 38. The maximum torque transfer location depends on the configuration of the hardware attached to the shafts. The user may enter up to four different performance requirement specifications for each spline.
The results of the analysis show that there are two phases of spline coupling. The first phase shows a large increase in stress and vibration. The second phase shows a decline in both stress and vibration levels. The third stage shows a constant meshing force between 300N and 320N. This behavior continues for a longer period of time, until the final stage engages with the surface.
Misalignment of a spline coupling
A study aimed to investigate the position of the resultant contact force in a spline coupling engaging teeth under a steady torque and rotating misalignment. The study used numerical methods based on Finite Element Method (FEM) models. It produced numerical results for nominal conditions and parallel offset misalignment. The study considered two levels of misalignment – 0.02 mm and 0.08 mm – with different loading levels.
The results showed that the misalignment between the splines and rotors causes a change in the meshing force of the spline-rotor coupling system. Its dynamics is governed by the meshing force of splines. The meshing force of a misaligned spline coupling is related to the rotor-spline coupling system parameters, the transmitting torque, and the dynamic vibration displacement.
Despite the lack of precise measurements, the misalignment of splines is a common problem. This problem is compounded by the fact that splines usually feature backlash. This backlash is the result of the misaligned spline. The authors analyzed several splines, varying pitch diameters, and length/diameter ratios.
A spline coupling is a two-dimensional mechanical system, which has positive backlash. The spline coupling is comprised of a hub and shaft, and has tip-to-root clearances that are larger than the backlash. A form-clearance is sufficient to prevent tip-to-root fillet contact. The torque on the splines is transmitted via friction.
When a spline coupling is misaligned, a torque-biased thrust force is generated. In such a situation, the force can exceed the torque, causing the component to lose its alignment. The two-way transmission of torque and thrust is modeled analytically in the present study. The analytical approach provides solutions that can be integrated into the design process. So, the next time you are faced with a misaligned spline coupling problem, make sure to use an analytical approach!
In this study, the spline coupling is analyzed under nominal conditions without a parallel offset misalignment. The stiffness values obtained are the percentage difference between the nominal pitch diameter and load application diameter. Moreover, the maximum percentage difference in the measured pitch diameter is 1.60% under a torque of 5000 N*m. The other parameter, the pitch angle, is taken into consideration in the calculation.
editor by czh 2023-02-15
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1.framed structure
2.PTO assembly
three.Connection
4.transmission shaft
five.wheel hub
six.absorber
seven.Entrance axle and wheel hub
eight.differential mechanism
9.rear axle assembly, axle shaft
10.braking program
eleven.gap adjuster
twelve.wheel-side/planetary framework
13.front suspension cylinder
14.rear suspension cylinder
fifteen.steering cylinder
16.lifting cylinder
17.Chassis elements, fastening bolt, pin, shaft sleeve.
| drawing NO | Vehicle model |
| framed structure | |
| 9015218 | TR50 |
| 20019310 | TR50 |
| 9240460 | TR50 |
| 09015394 | TR50 |
| 09069246 | TR50 |
| PTO assembly | |
| 20000042 | TR50 |
| 9060268 | TR50 |
| 9274893 | TR50 |
| 9195847 | TR50 |
| 571528 | TR50 |
| 00907696 | TR50 |
| 0905711 | TR50 |
| 0905710 | TR50 |
| 15252439 | TR50 |
| 15245600 | TR50 |
| 15016501 | TR50 |
| 09264925 | TR50 |
| 1530571 | TR50 |
| 05714209 | TR50 |
| 06772182 | TR50 |
| 6772182 | TR50 |
| 09269703 | TR50 |
| connection | |
| 15300857 | TR50 |
| 15300858 | TR50 |
| 09227330 | TR50 |
| 06772182 | TR50 |
| transmission shaft | |
| old09060412/new15300854 | 3307/TR50 |
| old15233277/new15272774 | 3307/TR50 |
| old09072552/new1530571 | 3307/TR50 |
| old0957152/new15272772 | 3307/TR50 |
| 15352300 | TR100new |
| 15352330 | TR100 |
| 15352327 | TR100. |
| 09253468 | TR100 |
| 09255689 | TR100.11E |
| 09433576 | TR100 |
| 09062983 | TR100.11E. |
| 15571746 | TR100 |
| 09062983 | TR100 |
| 9011828 | TR100 |
| 15000838 | TR100 |
| 09015398 | TR100 |
| 15249677 | TR100 |
| 15228480 | TR100 |
| 15335654 | TR100 |
| PTO assembly | |
| 15252682 | TR60 |
| 9065715 | TR60 |
| 9274893 | TR60 |
| 9195847 | TR60 |
| 15252439 | TR60 |
| 15300845 | TR60 |
| transmission shaft | |
| 15300843 | TR60 |
| 15272772 | TR60 |
| 1530571 | TR60 |
| 15272865 | TR60 |
| wheel hub | |
| 15246296 | TR60 |
| 9253468 | TR60 |
| 15265338 | TR60 |
| differential mechanism | |
| 9272352 | TR60 |
| 1530571 | TR60 |
| 9272346 | TR60 |
| 9272386 | TR60 |
| front suspension cylinder | |
| 15336056 | TR60 |
| 15336055 | TR60 |
| 15247973 | TR60 |
| 09068668 | TR60 |
| 5714086 | TR60 |
| 0957149 | TR60 |
| 5716508A | TR60 |
| absorber | |
| 15228210 | TR100 |
| 9065712 | TR100 |
| 9423067 | TR100 |
| 15246912 | TR100 |
| 15229318 | 3311E |
| 15336167 | TR100 |
| 1535712 | TR100 |
| 15336167 | TR100 |
| PTO assembly | |
| old15257485/new15331595 | TR100 |
| old15257459/new15331594 | TR100 |
| 20038184 | TR100new |
| 20038083 | TR100new |
| 9274893 | TR100 |
| 9195847 | TR100 |
| 15331585 | TR100new |
| 15246910 | 3311E |
| 1530571 | TR100/11E |
| 15331582 | TR100 |
| connection | |
| old06777070/new1530571 | TR100 |
| old15258084/new15230619 | TR100 |
| 09227330 | TR100 |
| 06772182 | TR100 |
| transmission shaft | |
| old15300850/new15336537 | TR100 |
| 15272865 | TR100 |
| old15258114/new15352888 | TR100 |
| 15271476 | TR100 |
| differential mechanism | |
| 15315244 | TR100 |
| 9272346 | TR100 |
| 9272352 | TR100 |
| 9272386 | TR100 |
| 150571 | TR100 |
| 15007646 | TR100 |
| Front suspension cylinder | |
| 2003571/15250974/15352794 | TR100 |
| 15335709/15250973/15335709 | TR100 |
| 09069475 | TR100 |
| 5713858 | TR100 |
| 09069476 | TR100 |
| 9396484/9396486 | TR100 |
Different cargo techniques.
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