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
| pe | Design Data Item |
SWC160 | SWC180 | SWC200 | SWC225 | SWC250 | SWC265 | SWC285 | SWC315 | SWC350 | SWC390 | SWC440 | SWC490 | SWC550 | SWC620 |
| A | L | 740 | 800 | 900 | 1000 | 1060 | 1120 | 1270 | 1390 | 1520 | 1530 | 1690 | 1850 | 2060 | 2280 |
| LV | 100 | 100 | 120 | 140 | 140 | 140 | 140 | 140 | 150 | 170 | 190 | 190 | 240 | 250 | |
| M(kg); | 65 | 83 | 115 | 152 | 219 | 260 | 311 | 432 | 610 | 804 | 1122 | 1468 | 2154 | 2830 | |
| B | L | 480 | 530 | 590 | 640 | 730 | 790 | 840 | 930 | 100 | 1571 | 1130 | 1340 | 1400 | 1520 |
| M(kg); | 44 | 60 | 85 | 110 | 160 | 180 | 226 | 320 | 440 | 590 | 820 | 1090 | 1560 | 2100 | |
| C | L | 380 | 420 | 480 | 500 | 560 | 600 | 640 | 720 | 782 | 860 | 1040 | 1080 | 1220 | 1360 |
| M(kg); | 35 | 48 | 66 | 90 | 130 | 160 | 189 | 270 | 355 | 510 | 780 | 970 | 1330 | 1865 | |
| D | L | 520 | 580 | 620 | 690 | 760 | 810 | 860 | 970 | 1030 | 1120 | 1230 | 1360 | 1550 | 1720 |
| M(kg); | 48 | 65 | 90 | 120 | 173 | 220 | 250 | 355 | 485 | 665 | 920 | 1240 | 1765 | 2390 | |
| E | L | 800 | 850 | 940 | 1050 | 1120 | 1180 | 1320 | 1440 | 1550 | 1710 | 1880 | 2050 | 2310 | 2540 |
| LV | 100 | 100 | 120 | 140 | 140 | 140 | 140 | 140 | 150 | 170 | 190 | 190 | 240 | 250 | |
| M(kg); | 70 | 92 | 126 | 165 | 238 | 280 | 340 | 472 | 660 | 886 | 1230 | 1625 | 2368 | 3135 | |
| Tn(kN·m); | 16 | 22.;4 | 31.;5 | 40 | 63 | 80 | 90 | 125 | 180 | 250 | 355 | 500 | 710 | 1000 | |
| TF(kN·m); | 8 | 11.;2 | 16 | 20 | 31.;5 | 40 | 45 | 63 | 90 | 125 | 180 | 250 | 355 | 500 | |
| Β(°); | 15 | 15 | 15 | 15 | 15 | 15 | 15 | 15 | 15 | 15 | 15 | 15 | 15 | 15 | |
| D | 160 | 180 | 200 | 225 | 250 | 265 | 285 | 315 | 350 | 390 | 440 | 490 | 550 | 620 | |
| Df | 160 | 180 | 200 | 225 | 250 | 265 | 285 | 315 | 350 | 3690 | 440 | 490 | 550 | 620 | |
| D1 | 137 | 155 | 170 | 196 | 218 | 233 | 245 | 280 | 310 | 345 | 390 | 435 | 492 | 555 | |
| D2(H9); | 100 | 105 | 120 | 135 | 150 | 160 | 170 | 185 | 210 | 235 | 255 | 275 | 320 | 380 | |
| D3 | 108 | 114 | 140 | 159 | 168 | 180 | 194 | 219 | 245 | 273 | 299 | 325 | 402 | 426 | |
| Lm | 95 | 105 | 110 | 125 | 140 | 150 | 160 | 180 | 195 | 215 | 260 | 270 | 305 | 340 | |
| K | 16 | 17 | 18 | 20 | 25 | 25 | 27 | 32 | 35 | 40 | 42 | 47 | 50 | 55 | |
| T | 4 | 5 | 5 | 5 | 6 | 6 | 7 | 8 | 8 | 8 | 10 | 12 | 12 | 12 | |
| N | 8 | 8 | 8 | 8 | 8 | 8 | 8 | 10 | 10 | 10 | 16 | 16 | 16 | 16 | |
| D | 15 | 17 | 17 | 17 | 19 | 19 | 21 | 23 | 23 | 25 | 28 | 31 | 31 | 38 | |
| B | 20 | 24 | 32 | 32 | 40 | 40 | 40 | 40 | 50 | 70 | 80 | 90 | 100 | 100 | |
| G | 6.;0 | 7.;0 | 9.;0 | 9.;0 | 12.;5 | 12.;5 | 12.;5 | 15.;0 | 16.;0 | 18.;0 | 20.;0 | 22.;5 | 22.;5 | 25 | |
| MI(Kg); | 2.;57 | 3 | 3.;85 | 3.;85 | 5.;17 | 6 | 6.;75 | 8.;25 | 10.;6 | 13 | 18.;50 | 23.;75 | 29.;12 | 38.;08 | |
| Size | M14 | M16 | M16 | M16 | M18 | M18 | M20 | M22 | M22 | M24 | M27 | M30 | M30 | M36 | |
| Tightening torque(Nm); | 180 | 270 | 270 | 270 | 372 | 372 | 526 | 710 | 710 | 906 | 1340 | 1820 | 1820 | 3170 |
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.; );
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 4 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 3 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 2 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 2 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 1 another.
