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China Blince hidromotor 4-Hole Square Flange Cylindrical Shaft OMR BMR200cc 315cc 400cc hydraulic orbital motors with Hot selling

Structure: Cycloid sort
Fat: ten
Power: 12KW
Dimension(L*W*H): twenty five*12*14
Warranty: 1 Calendar year, 1 calendar year
Showroom Spot: None
Motor Type: Orbit motor
Displacement: two hundred
Maximum Circulation Charge: 60L/min
Item identify: CZPT OMR hydraulic motor
Displacement Variety: 36,50,80,a hundred,125,one hundred sixty,two hundred,250,315,four hundred
Velocity range: 20-1050rpm
Max torque: 500N.m
Max Flow: 60L/min
Max. Force: 16Mpa
Flange varieties: 2-Gap rhombus Flange, 4-Gap rhombus Flange, 4-Hole Square Flange
Shaft kind: Cylindrical Shaft . Splined Shaft . Cone Shaft
steady max output energy: 10kw
Packaging Particulars: 1.sale packing contians carton or wooden circumstance 2.interior packing is substantial quality film

item description OMR sequence motor adapt the sophisticated Geroler gear set layout with shaft distribution movement, which can automatically compensate in running with higher strain, offer reputable and easy procedure, substantial effectiveness and extended existence.Characteristic attributes:1.Sophisticated manufacturing units for the Gerolor gear established, which use reduced force of start-up, provide smooth, trustworthy operation and large effectiveness.2.Shaft seal can bear substantial stress of back again and the motor can be employed in parallel or in collection.3.Particular design and style in the driver-linker and lengthen working lifestyle.4.Particular style for distribution program can fulfill the necessity of low sound of unit.5.Compact quantity and straightforward set up.Item application:Blince hydraulic motors are commonly applied in agriculture machinery, fishing machinery, plastic business, mining, and design machinery, particularly equipped to reduced load apps, Modest Silent Oil-free of charge Rocking Piston Substantial Stress Transportable Air Compressor 2.2KW 120L Decrease Noise Movable Blowing Dust Air Pump this kind of as plastic injection mold machine, cleaner, grass cutter,Winches, Conveyors, Slews, Sweeper Drives, Augers, Cutters, Mowers and Chippers.

OMRMax torque (N.m)Pace Assortment (rpm)Max pressure(MPA)Max flow(L/min)Max power(Kw)
OMR-36fiftya hundred-10301445eight.five
OMR-eightyone hundred twentysixty-600166012.five
OMR-a hundreda hundred and seventyfifty-480sixteen60thirteen
OMR-a hundred twenty five220fifty-390sixteensixty12.five
OMR-one hundred sixtythree hundred50-three hundredsixteen60twelve.5
OMR-two hundred360forty-240sixteensixtyeleven
OMR-250460thirty-a hundred and seventy16sixty10
OMR-31548020-one hundred twentyfourteen60nine
OMR-40041020-one hundred ten10607.5
Associated items Hydraulic motor– CZPT hydraulic motor Can ideal replaceDan-foss :OMM/ OMP/ OMR/ OMH/ OMS/ OMT/ OMV/ DH/ DS series , TE/ TG/ TF seriesEaton Char Lynn : J (129-), H(one zero one-) ,S(103-),T(158-),2000(104-),6000 collection orbit motor M+S : MM,MLHM/MP,MLHP/ MR,MLHR/ MH,MLHH/ MS,MLHS/ MT,MLHT/ MV,MLHV hydraulic motor.White : MP/RS/MR/RG/HB/CE/RE collection hydraulic motor Firm Profie Blince HangZhou CZPT Machinery & Electronics Co., Ltd was proven in the calendar year of 2004, HUAKE WPW80 sequence Worm Wheel Gearbox Transmission Gearbox Worm Speed Gearbox which specializing in design and style, manufacture and revenue of hydraulic factors. CZPT Hydraulics has become the leading producer of hydraulic factors, as properly as a effectively acknowledged company in the globe. Specializing in design, production and product sales of hydraulic solution consist of hydraulic orbital motor, radial piston motor, hydraulic pump, hydraulic steering manage device, oil cooler, hydraulic system and more, with in excess of fifteen several years encounter onproducts analysis and growth. Orbital motor from small OMM type to massive torque OMS, OMT and OMV sequence. Vane pump include CZPT PV2R collection, CZPT V/VQ series and Tokemic SQP sequence. Radial piston motor like NHM1 to NHM31. We are positioned in HangZhou city which is an production city nearby HangZhou port and HangZhou port. It is quite hassle-free for us to arrange shipment by sea. For hydraulic gear, remember to search for Blince Exhibition Customers Why Decide on Us *Blince business gain *Hydraulic motor spare portion and production line *Hydraulic motor assembly line *Hydraulic motor teat following production and ahead of cargo *Our Higher High quality Provider: Pre-Income Services Right after-Product sales Service * Inquiry and consulting help. * Teach how to MOUNTING and USE the hydraulic motor. * Sample tests support. * Arrange cargo 7-30days and update tracking No. * Look at our Factory. * Guarantee 1 calendar year. Payment Expression 1,T/T, Paypal, Wester union and Alibaba Trade Assurance. 2. Shipping and delivery time: 7-15days soon after acquiring deposite. 3. samples for high quality reference are available. 4. Shipping port: HangZhou/HangZhou as your require. *Packing & Deliver Package deal Dimensions: 1.2 (L) *.8(W) * .8 (D) Packaging Details: 1. 30/fifty/100pcs wood circumstance 2. 100pcs plastic/wood pallet. 3. 1 piece seperate weeden scenario. Shipping 1. MOQ is 1pc, price is far more favorable for large amount. 2. Top time is inside of 3days if have stock. If never, within 30days if the quantity is significantly less than 500pcs. 3. DHL, UPS, FEDEX, TNTetc, generally 5-7 times to get there. 4. By sea/air, Marine Gearbox Hydraulic Transfer Case Coupler Hydraulic Transfer Maritime Gearbox For Tiny Boat FOB/CIF trade and so on, is normally 20-30days.

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 four 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 three 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 two 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 two 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 one another.

China Blince hidromotor 4-Hole Square Flange Cylindrical Shaft OMR BMR200cc 315cc 400cc hydraulic orbital motors     with Hot selling		China Blince hidromotor 4-Hole Square Flange Cylindrical Shaft OMR BMR200cc 315cc 400cc hydraulic orbital motors     with Hot selling
editor by czh 2023-02-15