Product Description

SWP-A Type Cardan Shaft(JB/T3241-1991)

SWP partition profile bearing the cross shaft universal coupling products: replacement of bearings for, SWP type Cardan shaft design bearing split shaft bolt, suitable for hoisting and conveying machinery and other heavy machinery, connecting 2 different axis transmission shaft, axis angle of A~F type not more than 10 degrees, the G type is not greater than 5 degrees.

Cardan shaft is widely used in rolling mill, punch, straightener, crusher, ship drive, paper making equipment, common machinery, water pump equipment, test bench, and other mechanical applications.

 

·SWP A Type Cardan Shaft Basic Parameter And Main Dimension(JB/T3241-1991)

 

Type	Tactical diameter D mm	Nominal torque Tn kN·m	Fatique torque Tf kN·m	Axis angle β (°)	Stretch length S mm	Size(mm)										Rotary inertia kg·m2		Mass kg
						Lmin	D1 js11	D2 H7	D3	E	E1	B×h	h1	L1	n-d	Lmin	Increase 100	Lmin	Increase 100
SWP160A	160	16	8	≤10	50	660	140	95	114	15	4	20×12	6	85	6-13	0.13	0.0059	47	2.1
SWP180A	180	20	10	≤10	60	752	155	105	121	15	4	24×14	7	95	6-15	0.22	0.0072	60	2.3
SWP200A	200	31.5	16	≤10	70	823	175	125	17	17	5	28×16	8	110	8-15	0.37	0.0114	81	3.4
SWP225A	225	40	20	≤10	76	933	196	135	152	20	5	32×18	9	130	8-17	0.63	0.5710	109	6.6
SWP250A	250	63	31.5	≤10	80	978	218	150	168	25	5	40×25	12.5	135	8-19	1.02	0.0407	147	7.3
SWP285A	285	90	45	≤10	100	1133	245	170	194	27	7	40×30	15	150	8-21	2.17	0.0702	241	9.4
SWP315A	315	140	63	≤10	110	1250	280	185	219	32	7	40×30	15	170	10-23	3.86	0.1144	322	12.0
SWP350A	350	180	90	≤10	120	1380	310	210	245	35	8	50×32	16	185	10-23	6.66	0.1663	428	13.6
SWP390A	390	250	112	≤10	120	1495	345	235	273	40	8	70×36	18	205	10-25	11.53	0.2695	566	18.0
SWP435A	435	355	160	≤10	150	1710	385	255	299	42	10	80×40	20	235	16-28	21.81	0.3645	932	20.0
SWP480A	480	450	224	≤10	170	1910	425	275	351	47	12	90×45	22.5	265	16-31	38.04	0.7571	1294	28.0
SWP550A	550	710	315	≤10	190	2135	492	320	402	50	12	100×45	22.5	290	16-31	61.28	1.1842	1744	35.7
SWP600A	600	1000	500	≤10	210	3580	544	380	450	55	15	90×55	27.5	360	22-34	98.63	1.7159	2330	40.5
SWP640A	640	1250	630	≤10	230	2685	575	385	480	60	15	100×60	30	385	18-38	167.67	2.3080	3153	48.3

 

·Note:L is the length of the installation, including the value of S/Z 

♦Product Show

♦Other Products List

Transmission Machinery  Parts Name	Model
Universal Coupling	WS, WSD, WSP
Cardan Shaft	SWC, SWP, SWZ
Tooth Coupling	CL, CLZ, GCLD, GIICL GICL, NGCL, GGCL, GCLK
Disc Coupling	JMI, JMIJ, JMII, JMIIJ
High Flexible Coupling	LM
Chain Coupling	GL
Jaw Coupling	LT
Grid Coupling	JS

♦Our Company
HangZhou CZPT Machinery Manufacturing Co., Ltd. is a technology-based company specializing in the design and manufacture of basic transmission parts and various auxiliary non-standard equipment accessories. The products are mainly used in metallurgy, electric power, mining, chemical industry, petroleum, papermaking, shipbuilding, heavy industry, etc.

In many industries, it has provided strong technical and equipment support for many companies around the world. At present, the products are also exported to Russia, Italy, Spain, Brazil, Ukraine, Turkey, Australia, Singapore, Vietnam, Indonesia, Malaysia, Sri Lanka, and other countries and regions.

Welcome to customize products from our factory and please provide your design drawings or contact us if you need other requirements.

♦Our Services
1. Design Services
Our design team has experience in Cardan shafts relating to product design and development. If you have any needs for your new product or wish to make further improvements, we are here to offer our support.

2. Product Services
raw materials → Cutting → Forging →Rough machining →Shot blasting →Heat treatment →Testing →Fashioning →Cleaning→ Assembly→Packing→Shipping

3. Samples Procedure
We could develop the sample according to your requirement and amend the sample constantly to meet your need.

4. Research & Development
We usually research the new needs of the market and develop the new model when there is new cars in the market.

5. Quality Control
Every step should be a special test by Professional Staff according to the standard of ISO9001 and TS16949.

♦FAQ
Q 1: Are you a trading company or a manufacturer?
A: We are a professional manufacturer specializing in manufacturing
various series of couplings.

Q 2:Can you do OEM?
Yes, we can. We can do OEM & ODM for all the customers with customized artworks in PDF or AI format.

Q 3:How long is your delivery time?
Generally, it is 20-30 days if the goods are not in stock. It is according to quantity.

Q 4: Do you provide samples? Is it free or extra?
Yes, we could offer the sample but not for free. Actually, we have a very good price principle, when you make the bulk order the cost of the sample will be deducted.

Q 5: How long is your warranty?
A: Our Warranty is 12 months under normal circumstances.

Q 6: What is the MOQ?
A: Usually our MOQ is 1pcs.

Q 7: Do you have inspection procedures for coupling?
A:100% self-inspection before packing.

Q 8: Can I have a visit to your factory before the order?
A: Sure, welcome to visit our factory.

Q 9: What’s your payment?
A:1) T/T. 2) L/C 

♦Contact Us
Add: No.1 HangZhou Road,Chengnan park,HangZhou City,ZheJiang Province,China

 

 

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.