Product Description
1.Company profile
ZheJiang Sohaipu Isostatic Press Technology Equipment Co., Ltd. was founded in 2005. It is a leading manufacturer dedicated to research, development and manufacture of cold isostatic presses. We are famous for its efficient R&D and technological breakthroughs.
Our company has large-scale mechanical production capacity, with 5-meter vertical lathe, 2*10-meter horizontal lathe, 2.5×6.5 CNC gantry milling machine and other large-scale mechanical equipment, using advanced strand technology, cold stability, long life. Guarantee isostatic pressure.
2.Product Description
At present, cold isostatic press has been widely used in industrial ceramics pressure forming, high temperature refractories, cemented carbides, permanent magnets, rare metal powder forming and other fields, occupying a considerable market share. Up to now, we have provided more than 500 sets of isostatic presses to the Chinese and international markets. All our products have passed the CE certification with PED clause issued by the European Union. Export countries or regions include Brazil, Russia, Europe, India, ZheJiang and etc..
3.Product Parameters
| 1 | Equipment Name: | Cold Isostatic Press |
| 2 | Equipment type: | CIP200/300-300 |
| 3 | Maximum pressure: | 300MPa |
| 4 | The effective inner diameter of suppress cylinder vessel: | Ø 200mm |
| 5 | The effective inner height of suppress cylinder vessel: | 300mm |
| 6 | Pressing system Working medium : |
emulsion |
| 7 | Pressing system driving medium : | L-HM32 anti-wear hydraulic oil |
| 8 | No working parts pressure rising time: | 0~300MPa,t≤ 3min |
| 9 | Assistant time: upper plug close+ frame move in: | t≤ 1.5min |
| Assistant time: upper plug open+frame remove : | t≤ 1.5min | |
| 10 | pressure hold time : | 0~9999s Setting freely |
| 11 | pressure falls during pressure holding : | hold 30min,falls≤2% (pressure setable self-compensation automatically ) |
| 12 | Control mode: | PLC(Siemens)+HMI(MCGS) / Automatic and Manual mode |
| 13 | Supercharging mode: | one – time supercharger , gradable pause |
| 14 | Pressure relief mode: | Automatic pressure relief, gradable pause |
| 15 | Loading mode: | the upper plug drives the feeding cage to move |
| 16 | Certificate: | By CE Certificated with PED directive |
| 17 | Install Way: | on floor |
| 18 | Power Supply system: | 50Hz, 380V, Three-phase 5 wire system |
| 19 | Working condition: |
|
| 20 | Install Power : | ≈ 15 kw |
| 21 | Install area: | ≈ 6-8 square meter |
| 22 | Running noise: | ≤ 75dB |
| S.NO. | Type | Diameter of Pressure Vessel |
Height of Pressure Vessel |
Maximum Isostatic Pressure |
| 1 | CIP 200/300-300 | 200mm | 300mm | 300Mpa |
| 2 | CIP 200/1000-300 | 200 mm | 1000mm | 300Mpa |
| 3 | CIP 420/4000-320 | 420mm | 4000mm | 320Mpa |
| 4 | CIP 500/1200-400 | 500mm | 1200mm | 400Mpa |
| 5 | CIP 500/1500-300 | 500mm | 1500mm | 300Mpa |
| 6 | CIP 710/2000-250 | 710mm | 2000mm | 250Mpa |
| 7 | CIP 1000/3500-200 | 1000mm | 3500mm | 200Mpa |
a. The vessel inner materials is 34CrNi3MoV alloy whole parts forged and then The forged vessel be wire wounded by alloy of wire(65Mn steel 1.5mm x 6mm size) as per the designed.
b.Whole procedure of the cold isostatic pressing (CIP) machine, increasing, holding and releasing pressure is controlled by PLC and also there is a decompression system to protect the system over pressure to keep the machine in safety running.
4.Equipment Composition
The equipment consists of 4 parts: Suppression system, hydraulic system, filling and pumping system and electrical control system.
5.About Acceptance
acceptance method
5.1. after finish the manufacturing of the press machine, the test production to be proceeded in the Seller’s workshop.
5.2. During test production, The Buyer have the right to send people to the Seller for on-site supervision, inspection, verifying all issues including inspection records, debugging records, final inspection reports or other necessary documents for examination and approval to carry out the pre-acceptance.
5.3 After the seller complete the installation and commissioning at the designated location, the final acceptance approved.
6.We and Our Customers
7.After Sales Service
1.Within the warranty period, we shall immediately reply and CZPT troubleshooting within 1 hour after receiving the buyer’s equipment failure notice. If it cannot be solved, we shall arrive at the buyer’s production site for maintenance and troubleshooting within 24 hours.
2.We shall provide major and medium-sized equipment repair services, spare parts and wearing parts services in a long-term preferential manner. Provide technical support and quality tracking for the use of equipment for life.
3.Be responsible for equipment installation and debugging until it passes the acceptance.
4.We shall train the buyer’s maintenance workers and operators free of charge.The training is divided into 2 parts: theoretical training and practical training.
The training shall be conducted in 2 times. The first time, theoretical and practical training shall be conducted during the general assembly, debugging and pre-acceptance at our production site for 1 week; For the second time, the maintenance and operation training shall be conducted from the whole process of hoisting, installation, debugging and acceptance at the buyer’s installation site.
2 ~ 3 equipment operators shall be trained free of charge. The training content includes: equipment operation, use, daily maintenance, etc., so that the trainees can operate the equipment independently.
5.We shall be responsible for the effect and quality of the training. If the training provided cannot meet the requirements, the buyer has the right to require retraining or extend the training time by itself.
8.Our Certification
| 9.Time Schedule |
9.1.Within 15 days after this agreement comes into force, party B shall submit to party A the outline drawing of the equipment and the basic drawing of installation;
9.2.it is total Four months for equipment design, outsourcing procurement, manufacturing, assembly and in-plant commissioning;
9.3.According to the requirements of the contract, the supplier shall complete the installation and debugging of the equipment within 5 days after the arrival of the goods.
How to Calculate Stiffness, Centering Force, Wear and Fatigue Failure of Spline Couplings
There are various types of spline couplings. These couplings have several important properties. These properties are: Stiffness, Involute splines, Misalignment, Wear and fatigue failure. To understand how these characteristics relate to spline couplings, read this article. It will give you the necessary knowledge to determine which type of coupling best suits your needs. Keeping in mind that spline couplings are usually spherical in shape, they are made of steel.
Involute splines
An effective side interference condition minimizes gear misalignment. When 2 splines are coupled with no spline misalignment, the maximum tensile root stress shifts to the left by 5 mm. A linear lead variation, which results from multiple connections along the length of the spline contact, increases the effective clearance or interference by a given percentage. This type of misalignment is undesirable for coupling high-speed equipment.
Involute splines are often used in gearboxes. These splines transmit high torque, and are better able to distribute load among multiple teeth throughout the coupling circumference. The involute profile and lead errors are related to the spacing between spline teeth and keyways. For coupling applications, industry practices use splines with 25 to 50-percent of spline teeth engaged. This load distribution is more uniform than that of conventional single-key couplings.
To determine the optimal tooth engagement for an involved spline coupling, Xiangzhen Xue and colleagues used a computer model to simulate the stress applied to the splines. The results from this study showed that a “permissible” Ruiz parameter should be used in coupling. By predicting the amount of wear and tear on a crowned spline, the researchers could accurately predict how much damage the components will sustain during the coupling process.
There are several ways to determine the optimal pressure angle for an involute spline. Involute splines are commonly measured using a pressure angle of 30 degrees. Similar to gears, involute splines are typically tested through a measurement over pins. This involves inserting specific-sized wires between gear teeth and measuring the distance between them. This method can tell whether the gear has a proper tooth profile.
The spline system shown in Figure 1 illustrates a vibration model. This simulation allows the user to understand how involute splines are used in coupling. The vibration model shows 4 concentrated mass blocks that represent the prime mover, the internal spline, and the load. It is important to note that the meshing deformation function represents the forces acting on these 3 components.
Stiffness of coupling
The calculation of stiffness of a spline coupling involves the measurement of its tooth engagement. In the following, we analyze the stiffness of a spline coupling with various types of teeth using 2 different methods. Direct inversion and blockwise inversion both reduce CPU time for stiffness calculation. However, they require evaluation submatrices. Here, we discuss the differences between these 2 methods.
The analytical model for spline couplings is derived in the second section. In the third section, the calculation process is explained in detail. We then validate this model against the FE method. Finally, we discuss the influence of stiffness nonlinearity on the rotor dynamics. Finally, we discuss the advantages and disadvantages of each method. We present a simple yet effective method for estimating the lateral stiffness of spline couplings.
The numerical calculation of the spline coupling is based on the semi-analytical spline load distribution model. This method involves refined contact grids and updating the compliance matrix at each iteration. Hence, it consumes significant computational time. Further, it is difficult to apply this method to the dynamic analysis of a rotor. This method has its own limitations and should be used only when the spline coupling is fully investigated.
The meshing force is the force generated by a misaligned spline coupling. It is related to the spline thickness and the transmitting torque of the rotor. The meshing force is also related to the dynamic vibration displacement. The result obtained from the meshing force analysis is given in Figures 7, 8, and 9.
The analysis presented in this paper aims to investigate the stiffness of spline couplings with a misaligned spline. Although the results of previous studies were accurate, some issues remained. For example, the misalignment of the spline may cause contact damages. The aim of this article is to investigate the problems associated with misaligned spline couplings and propose an analytical approach for estimating the contact pressure in a spline connection. We also compare our results to those obtained by pure numerical approaches.
Misalignment
To determine the centering force, the effective pressure angle must be known. Using the effective pressure angle, the centering force is calculated based on the maximum axial and radial loads and updated Dudley misalignment factors. The centering force is the maximum axial force that can be transmitted by friction. Several published misalignment factors are also included in the calculation. A new method is presented in this paper that considers the cam effect in the normal force.
In this new method, the stiffness along the spline joint can be integrated to obtain a global stiffness that is applicable to torsional vibration analysis. The stiffness of bearings can also be calculated at given levels of misalignment, allowing for accurate estimation of bearing dimensions. It is advisable to check the stiffness of bearings at all times to ensure that they are properly sized and aligned.
A misalignment in a spline coupling can result in wear or even failure. This is caused by an incorrectly aligned pitch profile. This problem is often overlooked, as the teeth are in contact throughout the involute profile. This causes the load to not be evenly distributed along the contact line. Consequently, it is important to consider the effect of misalignment on the contact force on the teeth of the spline coupling.
The centre of the male spline in Figure 2 is superposed on the female spline. The alignment meshing distances are also identical. Hence, the meshing force curves will change according to the dynamic vibration displacement. It is necessary to know the parameters of a spline coupling before implementing it. In this paper, the model for misalignment is presented for spline couplings and the related parameters.
Using a self-made spline coupling test rig, the effects of misalignment on a spline coupling are studied. In contrast to the typical spline coupling, misalignment in a spline coupling causes fretting wear at a specific position on the tooth surface. This is a leading cause of failure in these types of couplings.
Wear and fatigue failure
The failure of a spline coupling due to wear and fatigue is determined by the first occurrence of tooth wear and shaft misalignment. Standard design methods do not account for wear damage and assess the fatigue life with big approximations. Experimental investigations have been conducted to assess wear and fatigue damage in spline couplings. The tests were conducted on a dedicated test rig and special device connected to a standard fatigue machine. The working parameters such as torque, misalignment angle, and axial distance have been varied in order to measure fatigue damage. Over dimensioning has also been assessed.
During fatigue and wear, mechanical sliding takes place between the external and internal splines and results in catastrophic failure. The lack of literature on the wear and fatigue of spline couplings in aero-engines may be due to the lack of data on the coupling’s application. Wear and fatigue failure in splines depends on a number of factors, including the material pair, geometry, and lubrication conditions.
The analysis of spline couplings shows that over-dimensioning is common and leads to different damages in the system. Some of the major damages are wear, fretting, corrosion, and teeth fatigue. Noise problems have also been observed in industrial settings. However, it is difficult to evaluate the contact behavior of spline couplings, and numerical simulations are often hampered by the use of specific codes and the boundary element method.
The failure of a spline gear coupling was caused by fatigue, and the fracture initiated at the bottom corner radius of the keyway. The keyway and splines had been overloaded beyond their yield strength, and significant yielding was observed in the spline gear teeth. A fracture ring of non-standard alloy steel exhibited a sharp corner radius, which was a significant stress raiser.
Several components were studied to determine their life span. These components include the spline shaft, the sealing bolt, and the graphite ring. Each of these components has its own set of design parameters. However, there are similarities in the distributions of these components. Wear and fatigue failure of spline couplings can be attributed to a combination of the 3 factors. A failure mode is often defined as a non-linear distribution of stresses and strains.
