China manufacturer Double Steering Universal Cross Joint with Free Design Custom

Product Description

Quick Details
Applicable Industries:Auto parts industry
Material:Stainless Steel
Operating Angle:Max Working Angle 45 Degree
Place of Origin:ZHangZhoug, China
Brand Name:Naqin
Product Name:Universal Joint Bearing
Application:American vehicle&truck
Color:Metal Color
Service:OEM Customized Services
Feature:Long Life
Quality:100% Tested

Lead Time :

Quantity(Pieces) 1 – 50 51 – 100 101 – 500 >500
Est. Time(days) 14 20 45 To be negotiated

Supply Ability:
5000 Set/Sets per Month universal bearing
Packaging & Delivery
Packaging Details
1. Industrial packaging: plastic bag/plastic tube + kraft paper + carton + plywood pallets
2. Commercial packing: 1pc/plastic bag + color box + carton + plywood pallets
3. As the clients’ requirement
HangZhou, ZheJiang ,ZheJiang ,HangZhou

Features of universal joint, cross joint, cardan jont:

Universal joint, U joint, Cross joint, Cardan joint, Hardy-Spicer joint or Hooke’s joint

is used in transmission systems of cars, buses, trucks, tractors and machines, 

including Asian, European and American cars.

Application of universal joint:

-universal joint are usually used in cars, trucks, heavy duty, etc


1. Type no.:

universal joint bearing

2. Size:

Different size

3. Material:

Cross (20Cr), bearing (20Cr), needle roller (GCr15)

4. Hardness:


5. Brand:

REM or OEM service

6. Packing:

Plastic bag, color/white boxes, cartons, wood Pallet

7. Sample Policy:

Paid sample, freight collect.


Other universal joint bearing Model NO.:


GUA-1   HS108 19.00.00 49.41       18   47 M
GUA-2           5-170X   19.02   52 M
                20   48 M
          200-6154     23.83 34.85   M
GUA-3 811 HS130   1.41 200-7155     22.02   54.15 M
GUA-4 812 HS132 10.01.00   200-8261     22   54.8 M
GUA-5 341AG HS185 20.00.00 2.41 200-0600 5-92X CPL6R-40 23.82   61.45 M
GGPL-6R         200-8370     24.6 33.6   M
GUA-7 813 HS168 11.03.00 3.41 200-8474     27   70 M
GUA-8 344AG HS186 21.00.00 4.41 200-1200 5-242X CPL12R 27   74.8 M
GGPL-12R         200-1400 5-129X CPL14R 27.036 42   M
                27   81.5 A
GGPL-14R               28.6   16.64 M
GUA-9       30.41 200-6580     29   80 M
GUA-11 815 HS198   5.41 200-8692     30.22   80.15 M
                30   82 M
GUA-12 331AG HS182 22.00.00 6.41       30.2   92 M
GUA-13 330 HS179 23.00.00 7.41 200-3500 5-243X CP35R 30.2   106.5 M
GGPL-35R         200-7676     31.75   81.4 M
GUA-14 814 HS204 35.00.00   200-4400 5-431X CP44R 31.98   76 M
                33.3 67.48   M
GUA-15         200-2600 5-188X   34 51.3   M
GUA-17   HS183     200-6794     34.93   106.31 M
  818     7.81 200-6806     34.95   94 M
GUA-19     24.01.00 8.41 200-7989     34.92   106.5 M
GUA-20 817 HS230 36.00.00 36.41 200-5500 5-432X CP55N 36.04   89 M
                38   106 M
                38.95   109.22 M
GUA-18 370   25.00.00 25.41       39.7   115.8  
        9.81       41   108  
GUA-21       10.41       41   118  
      26.00.00         42   104.5 M


PART NO. D(mm) L (mm)
ZY571 13 38
ZY571 14 39.5
ZY1438 14 38
ZY1538 15 38.1
ZY1638 16 38.5
ZY1641 16 41
ZY1643 16 43
ZY1847 18 47
ZY1944 19 44
ZY2044 20 44
ZY2055 20 55

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.

China manufacturer Double Steering Universal Cross Joint   with Free Design CustomChina manufacturer Double Steering Universal Cross Joint   with Free Design Custom