Product Description

 

Product Parameters

TYPE	TOP WIDTH	PITCH WIDTH	HEIGHT	WEDGE ANGLE	CONVERSON TABLE		Length standard	Minimum Diameter of pulley (mm)	Weight/m
	MM	MM	MM						kgs
Z	10	8.5	6	40	Li=Lw-25	La=Li+38	La/Lw/Li	50	0.07
A	13	11	8	40	Li=Lw-33	La=Li+50	La/Lw/Li	75	0.112
B	17	14	11	40	Li=Lw-43	La=Li+69	La/Lw/Li	125	0.19
C	22	19	14	40	Li=Lw-56	La=Li+88	La/Lw/Li	200	0.31
D	32	27	19	40	Li=Lw-82	La=Li+119	La/Lw/Li	355	0.6
E	38	32	23	40	Li=Lw-95	La=Li+145	La/Lw/Li	500	0.9
F	50	42.5	30	40	Li=Lw-120	La=Li+188	La/Lw/Li
3L	10	8.5	6	40	Li=Lw-25	La=Li+38	La/Li	50	0.07
4L	13	11	8	40	Li=Lw-33	La=Li+50	La/Li	75	0.112
5L	17	14	11	40	Li=Lw-43	La=Li+69	La/Li	125	0.19

 

                                                                   Why Customer Trust/Choose Baopower Agricutural Belt ?

Product Application

–Wood-working Machinery                         –Packing Machinery                         –Wahsing Machinery                         –Automotive
–Construction Machinery                            –Energy Machinery                          –Agri Machinery                                 –Mining
 –Chemical Machinery                                –Food  Machinery                             –Lawn Mover                                     –Fan

Company Profile

Production Capacity

 

Packaging & Shipping

Available  Packing: Cartton, Poly Bags, Pallets, Wooden Case
 

Shipping: By Sea/ By Air/ By Train/ By Express

Customized is available

Power Exhibition

Certifications

FAQ

Q. What’s the raw material?
A. Main material NR, SBR, Polyester cord, Fabric. Aramid/kevlar available.
 
Q. What’s the minimum order qty?
A. Small sizes 100 pcs each size, big size (over 2500mm) could be smaller, 10 pcs – 50pcs, it depends on sizes and CZPT height. 
 
Q.Can we use our brand/LOGO ?
A. Yes, we can print customers’ brands/LOGO.
 
Q. How to guarantee your quality?
A. All the raw material are test in lab before production, the v-belts will be run on fatigue life machine.

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.

Product Description

 

Product Parameters

TYPE	TOP WIDTH	PITCH WIDTH	HEIGHT	WEDGE ANGLE	CONVERSON TABLE		Length standard	Minimum Diameter of pulley (mm)	Weight/m
	MM	MM	MM						kgs
Z	10	8.5	6	40	Li=Lw-25	La=Li+38	La/Lw/Li	50	0.07
A	13	11	8	40	Li=Lw-33	La=Li+50	La/Lw/Li	75	0.112
B	17	14	11	40	Li=Lw-43	La=Li+69	La/Lw/Li	125	0.19
C	22	19	14	40	Li=Lw-56	La=Li+88	La/Lw/Li	200	0.31
D	32	27	19	40	Li=Lw-82	La=Li+119	La/Lw/Li	355	0.6
E	38	32	23	40	Li=Lw-95	La=Li+145	La/Lw/Li	500	0.9
F	50	42.5	30	40	Li=Lw-120	La=Li+188	La/Lw/Li
3L	10	8.5	6	40	Li=Lw-25	La=Li+38	La/Li	50	0.07
4L	13	11	8	40	Li=Lw-33	La=Li+50	La/Li	75	0.112
5L	17	14	11	40	Li=Lw-43	La=Li+69	La/Li	125	0.19

 

                                                                   Why Customer Trust/Choose Baopower Agricutural Belt ?

Product Application

–Wood-working Machinery                         –Packing Machinery                         –Wahsing Machinery                         –Automotive
–Construction Machinery                            –Energy Machinery                          –Agri Machinery                                 –Mining
 –Chemical Machinery                                –Food  Machinery                             –Lawn Mover                                     –Fan

Company Profile

Production Capacity

 

Packaging & Shipping

Available  Packing: Cartton, Poly Bags, Pallets, Wooden Case
 

Shipping: By Sea/ By Air/ By Train/ By Express

Customized is available

Power Exhibition

Certifications

FAQ

Q. What’s the raw material?
A. Main material NR, SBR, Polyester cord, Fabric. Aramid/kevlar available.
 
Q. What’s the minimum order qty?
A. Small sizes 100 pcs each size, big size (over 2500mm) could be smaller, 10 pcs – 50pcs, it depends on sizes and CZPT height. 
 
Q.Can we use our brand/LOGO ?
A. Yes, we can print customers’ brands/LOGO.
 
Q. How to guarantee your quality?
A. All the raw material are test in lab before production, the v-belts will be run on fatigue life machine.

An Overview of Worm Shafts and Gears

This article provides an overview of worm shafts and gears, including the type of toothing and deflection they experience. Other topics covered include the use of aluminum versus bronze worm shafts, calculating worm shaft deflection and lubrication. A thorough understanding of these issues will help you to design better gearboxes and other worm gear mechanisms. For further information, please visit the related websites. We also hope that you will find this article informative.

Double throat worm gears

The pitch diameter of a worm and the pitch of its worm wheel must be equal. The 2 types of worm gears have the same pitch diameter, but the difference lies in their axial and circular pitches. The pitch diameter is the distance between the worm’s teeth along its axis and the pitch diameter of the larger gear. Worms are made with left-handed or right-handed threads. The lead of the worm is the distance a point on the thread travels during 1 revolution of the worm gear. The backlash measurement should be made in a few different places on the gear wheel, as a large amount of backlash implies tooth spacing.
A double-throat worm gear is designed for high-load applications. It provides the tightest connection between worm and gear. It is crucial to mount a worm gear assembly correctly. The keyway design requires several points of contact, which block shaft rotation and help transfer torque to the gear. After determining the location of the keyway, a hole is drilled into the hub, which is then screwed into the gear.
The dual-threaded design of worm gears allows them to withstand heavy loads without slipping or tearing out of the worm. A double-throat worm gear provides the tightest connection between worm and gear, and is therefore ideal for hoisting applications. The self-locking nature of the worm gear is another advantage. If the worm gears are designed well, they are excellent for reducing speeds, as they are self-locking.
When choosing a worm, the number of threads that a worm has is critical. Thread starts determine the reduction ratio of a pair, so the higher the threads, the greater the ratio. The same is true for the worm helix angles, which can be one, two, or 3 threads long. This varies between a single thread and a double-throat worm gear, and it is crucial to consider the helix angle when selecting a worm.
Double-throat worm gears differ in their profile from the actual gear. Double-throat worm gears are especially useful in applications where noise is an issue. In addition to their low noise, worm gears can absorb shock loads. A double-throat worm gear is also a popular choice for many different types of applications. These gears are also commonly used for hoisting equipment. Its tooth profile is different from that of the actual gear.

Bronze or aluminum worm shafts

When selecting a worm, a few things should be kept in mind. The material of the shaft should be either bronze or aluminum. The worm itself is the primary component, but there are also addendum gears that are available. The total number of teeth on both the worm and the addendum gear should be greater than 40. The axial pitch of the worm needs to match the circular pitch of the larger gear.
The most common material used for worm gears is bronze because of its desirable mechanical properties. Bronze is a broad term referring to various copper alloys, including copper-nickel and copper-aluminum. Bronze is most commonly created by alloying copper with tin and aluminum. In some cases, this combination creates brass, which is a similar metal to bronze. The latter is less expensive and suitable for light loads.
There are many benefits to bronze worm gears. They are strong and durable, and they offer excellent wear-resistance. In contrast to steel worms, bronze worm gears are quieter than their counterparts. They also require no lubrication and are corrosion-resistant. Bronze worms are popular with small, light-weight machines, as they are easy to maintain. You can read more about worm gears in CZPT’s CZPT.
Although bronze or aluminum worm shafts are the most common, both materials are equally suitable for a variety of applications. A bronze shaft is often called bronze but may actually be brass. Historically, worm gears were made of SAE 65 gear bronze. However, newer materials have been introduced. SAE 65 gear bronze (UNS C90700) remains the preferred material. For high-volume applications, the material savings can be considerable.
Both types of worms are essentially the same in size and shape, but the lead on the left and right tooth surfaces can vary. This allows for precise adjustment of the backlash on a worm without changing the center distance between the worm gear. The different sizes of worms also make them easier to manufacture and maintain. But if you want an especially small worm for an industrial application, you should consider bronze or aluminum.

Calculation of worm shaft deflection

The centre-line distance of a worm gear and the number of worm teeth play a crucial role in the deflection of the rotor. These parameters should be entered into the tool in the same units as the main calculation. The selected variant is then transferred to the main calculation. The deflection of the worm gear can be calculated from the angle at which the worm teeth shrink. The following calculation is helpful for designing a worm gear.
Worm gears are widely used in industrial applications due to their high transmittable torques and large gear ratios. Their hard/soft material combination makes them ideally suited for a wide range of applications. The worm shaft is typically made of case-hardened steel, and the worm wheel is fabricated from a copper-tin-bronze alloy. In most cases, the wheel is the area of contact with the gear. Worm gears also have a low deflection, as high shaft deflection can affect the transmission accuracy and increase wear.
Another method for determining worm shaft deflection is to use the tooth-dependent bending stiffness of a worm gear’s toothing. By calculating the stiffness of the individual sections of a worm shaft, the stiffness of the entire worm can be determined. The approximate tooth area is shown in figure 5.
Another way to calculate worm shaft deflection is by using the FEM method. The simulation tool uses an analytical model of the worm gear shaft to determine the deflection of the worm. It is based on a two-dimensional model, which is more suitable for simulation. Then, you need to input the worm gear’s pitch angle and the toothing to calculate the maximum deflection.

Lubrication of worm shafts

In order to protect the gears, worm drives require lubricants that offer excellent anti-wear protection, high oxidation resistance, and low friction. While mineral oil lubricants are widely used, synthetic base oils have better performance characteristics and lower operating temperatures. The Arrhenius Rate Rule states that chemical reactions double every 10 degrees C. Synthetic lubricants are the best choice for these applications.
Synthetics and compounded mineral oils are the most popular lubricants for worm gears. These oils are formulated with mineral basestock and 4 to 6 percent synthetic fatty acid. Surface-active additives give compounded gear oils outstanding lubricity and prevent sliding wear. These oils are suited for high-speed applications, including worm gears. However, synthetic oil has the disadvantage of being incompatible with polycarbonate and some paints.
Synthetic lubricants are expensive, but they can increase worm gear efficiency and operating life. Synthetic lubricants typically fall into 2 categories: PAO synthetic oils and EP synthetic oils. The latter has a higher viscosity index and can be used at a range of temperatures. Synthetic lubricants often contain anti-wear additives and EP (anti-wear).
Worm gears are frequently mounted over or under the gearbox. The proper lubrication is essential to ensure the correct mounting and operation. Oftentimes, inadequate lubrication can cause the unit to fail sooner than expected. Because of this, a technician may not make a connection between the lack of lube and the failure of the unit. It is important to follow the manufacturer’s recommendations and use high-quality lubricant for your gearbox.
Worm drives reduce backlash by minimizing the play between gear teeth. Backlash can cause damage if unbalanced forces are introduced. Worm drives are lightweight and durable because they have minimal moving parts. In addition, worm drives are low-noise and vibration. In addition, their sliding motion scrapes away excess lubricant. The constant sliding action generates a high amount of heat, which is why superior lubrication is critical.
Oils with a high film strength and excellent adhesion are ideal for lubrication of worm gears. Some of these oils contain sulfur, which can etch a bronze gear. In order to avoid this, it is imperative to use a lubricant that has high film strength and prevents asperities from welding. The ideal lubricant for worm gears is 1 that provides excellent film strength and does not contain sulfur.