Product Description

Who we are?
HangZhou XIHU (WEST LAKE) DIS. CARDANSHAFT CO;LTD has 15 years history.;When the general manager Mr.;Rony Du graduated from the university,;he always concentrated his attention on the research and development,;production and sales of the cardan shaft.;Mr.;Rony Du and his team started from scratch,;from 1 lathe and a very small order,;step by step to grow up.;He often said to his team”We will only do 1 thing well——to make the perfect cardan shaft”.;

HangZhou XIHU (WEST LAKE) DIS. CARDANSHAFT CO.;,;LTD was founded in 2005.;The registered capital is 8 million ,;covers an area of 15 acres,; has 30 existing staff.; The company specializing in the production of SWC,; SWP cross universal coupling and drum tooth coupling.;The company with factory is located in the beautiful coast of Tai Lake –Hudai (HangZhou Economic Development Zone Hudai Industrial Park);.;
In order to become China’s leading cardan shaft one-stop solution expert supplier .;XIHU (WEST LAKE) DIS. CARDANSHAFT independent research and development of SWC light,; medium,; short,; heavy Designs cardan shaft have reached the leading domestic level.;Products not only supporting domestic large and medium-sized customers,; but also exported to the United States,; India,; Vietnam,; Laos,; Ukraine,; Russia,; Germany,; Britain and other countries and areas.;In the past 15 years,; the company has accumulated a wealth of experience,; learn from foreign advanced technology,; and to absorb and use the universal axis has been improved several times,; so that the structure is maturing,; significantly improved performance.;
 
XIHU (WEST LAKE) DIS. belief:; “Continuous innovation,; optimize the structure,; perseverance” to create a high quality of outstanding cardan shaft manufacturer.;We always adhere to the ISO9001 quality control system,; from the details to start,; standardize the production process,; and to achieve processing equipment “specialization,; numerical control” rapid increase in product quality.;This Not only won the majority of customers reputation,; but also access to peer recognition.; We continue to strive to pursue:; “for customers to create the greatest value,; for the staff to build the best platform”,; will be CZPT to achieve customer and business mutually beneficial win win situation.;

Why choose us?
First,;select raw material carefully
 
 The cross is the core component of cardan shaft,;so the selection of material is particularly critical.;Raw materials of the cross for light Duty Size and Medium Duty Size,;we choose the 20CrMnTi special gear steel bar from SHAGANG GROUP.;Being forged in 2500 ton friction press to ensure internal metallurgical structure,;inspecting the geometric dimensions of each part to meet the drawing requirements,;then transfer to machining,;the processes of milling,; turning,; quenching and grinding.;
 
The inspector will screen blank yoke head.;The porosity,; cracks,; slag,; etc.; do not meet the requirements of the casting foundry are all eliminated,;then doing physical and chemical analysis,; to see whether the ingredients meet the requirements,; unqualified re-elimination.;And then transferred to the quenching and tempering heat treatment,; once again check the hardness to see if meet the requirements,; qualified to be transferred to the machining process.; We control from the source of the material to ensure the supply of raw materials qualified rate of 99%.;
 
  
Second,;advanced production equipment
 
XIHU (WEST LAKE) DIS. Company introduced four-axis linkage machining center made in ZheJiang ,; milling the keyway and flange bolt hole of the flange yoke,; The once machine-shaping ensures that the symmetry of the keyway and the position of the bolt hole are less than 0.;02mm,;which greatly improves the installation accuracy of the flange,;the 4 axis milling and drilling center holes of the cross are integrated,;to ensure that the 4 shaft symmetry and verticality are less than 0.;02mm,;the process of the journal cross assembly service life can be increased by 30%,; and the speed at 1000 rpm above the cardan shaft running smoothly and super life is crucial to the operation.;
 
We use CNC machine to lathe flange yoke and welded yoke,;CNC machine can not only ensure the accuracy of the flange connection with the mouth,; but also improve the flange surface finish.;
 
5 meters automatic welding machine welding spline sleeve and tube,;welded yoke and tube.;With the welding CZPT swing mechanism,; automatic lifting mechanism,; adjustment mechanism and welding CZPT cooling system,; welding machine can realize multi ring continuous welding,; each coil current and voltage can be preset,; arc starting and stopping control PLC procedures,; reliable welding quality,; the weld bead is smooth and beautiful,; to control the welding process with fixed procedures,; greatly reducing the uncertainty of human during welding,; greatly improve the welding effect.;
 
 
High speed cardan shaft needs to do dynamic balance test before leaving the factory.;Unbalanced cardan shaft will produce excessive centrifugal force at high speed and reduce the service life of the bearing;the dynamic balance test can eliminate the uneven distribution of the casting weight and the mass distribution of the whole assembly;Through the experiment to achieve the design of the required balance quality,; improve the universal shaft service life.;In 2008 the company introduced 2 high-precision dynamic balance test bench,; the maximum speed can reach 4000 rev / min,; the balance of G0.;8 accuracy,; balance weight 2kg–1000kg.;
 
In order to make the paint standardization,; in 2009 the company bought 10 meters of clean paint room ,; the surface treatment of cardan shaft is more standardized,; paint fastness is more rugged,; staff’s working conditions improved,; exhaust of harmless treatment.;
 
Third,;Professional transport packaging
 
 
The packing of the export cardan shaft is all in the same way as the plywood wooden box,; and then it is firmly secured with the iron sheet,; so as to avoid the damage caused by the complicated situation in the long-distance transportation.; Meet the standard requirements of plywood boxes into Europe and other countries,; no matter where can successfully reach all the country’s ports.;

The following table for SWC Medium-sized Universal Shaft Parameters.; 
Designs

Data and Sizes of SWCZ Series Universal Joint Couplings
 

1.; Notations:; 
L=Standard length,; or compressed length for designs with length compensation; 
LV=Length compensation; 
M=Weight; 
Tn=Nominal torque(Yield torque 50% over Tn);; 
TF=Fatigue torque,; I.; E.; Permissible torque as determined according to the fatigue strength
Under reversing loads; 
Β=Maximum deflection angle; 
MI=weight per 100mm tube
2.; Millimeters are used as measurement units except where noted; 
3.; Please consult us for customizations regarding length,; length compensation and
Flange connections.; 
(DIN or SAT etc.; );
 

Analytical Approaches to Estimating Contact Pressures in Spline Couplings

A spline coupling is a type of mechanical connection between 2 rotating shafts. It consists of 2 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 1 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 2 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 2 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 1 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 4 different performance requirement specifications for each spline.
The results of the analysis show that there are 2 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 2 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.