Product Description
CE Approved DQ1504 150HP 4WD big Agri wheel Farm Tractor hot sale in Romania
Tractor Main Features and Advantages:
1.Equipped famous brand engine showing advanced capacity,low fuel consumption,high economic efficiency.
2. Streamlined appearance design, beautiful and generous.
3.Transmission Case adopt meshed shift and add the gearbox interlock device makes the operation more smoothly,reliable and easier.
4. Double action clutch with disc spring, perform steadily and easy to operate.
5. Fully hydraulic steering system greatly reduced driver’s work strength.
6. Wet disc brake device, reliable brake performance.
7. Separate injection of hydraulic oil, reliable to operate.
8. The lifter with force and position adjustment, with reliable lift.
9. Tractor PTO:
PTO in Double speed : 540/760r/min Optional, For high working efficiency.
PTO shaft of 6 or 8 spline Optional, adaptable for agricultural equipment of all over the world.
10. Big Chassis and Heavy-duty Rear axle for Durable Strong machine.
11. Full series light, ROPS,Sunshade/Canopy, Fan/Heater/Air-conditioned cabin are all available, for more comfortable driving environment.
Tractor Main specificaiton and Technical parameters:
| Model | DQ1504 |
| Drive type | 4×4, 4WD wheel type |
| Engine | |
| Engine brand and model | YTO brand, diesel engine Model LR6M3Z-23 |
| Type | In-line, direct injection,Water cooling, 4 stroke,6-cylinder |
| Aspiration way | Turbo |
| Engine power at rated speed | 110.3kw/150HP |
| Rated Power of PTO | 94 KW |
| Max. traction Force (KN) | 32.5 |
| Displacement(L) | 7.13 |
| Compression ratio | 18:1 |
| Rated speed (r/min) | 2300 |
| Lowest fuel consumption (g/kw.h) | ≤210 |
| Cylinder·Bore·Stroke | 6-110×125 |
| Fuel tank capacity (L) | 350 |
| Muffler Dimension (Dia.×Length) (mm) | φ600×295×140 |
| Muffler weight (kg) | 7.2 |
| Steering type | Full Hydraulic steering |
| Transmission | |
| Clutch | USA JpV brand, 13 inch dual-stage Clutch |
| PTO Speed (rpm) | 540/1000 |
| Gearshift | 16F+8R |
| Speed range (km/h) | F: 1.37-32.93 / R:2.09-30.63 |
| Driving brake | Wet, disk, hydro-static operate |
| Gearbox | 4×2×(2+1) |
| Gearbox shifting way | Joggle cover |
| Walking system | |
| Frame type | Frameless |
| Tyre size( front/rear) | 14.9-26/18.4-38 |
| Pressure( front/rear) (kPa) | 157-196/150-200 |
| Rim material | 330CL |
| Working device | |
| Lifter type | Semi-detached model |
| Max. Lifting force (KN) | 27 |
| Suspension model | Rear, three-point linkages |
| Suspension category | Category II or III |
| Adjusting control | Position control, float control |
| Hydraulic pump type | Gear pump CBN-E325L |
| Hydraulic output valve | 3 Groups |
| P.T.O. type | 1 type, rear |
| Spline no. of P.T.O. | 6( standard), 8, 21 |
| Diameter of spline | 35 |
| RPM | 540/1000 or 760/1000 |
| Technical parameter | |
| Overall Dimension (LxWxH) (mm) | 5240×2345×2995 |
| Wheel base (mm) | 2530/2657 |
| Track base-Front /R(mm) | 1650-2285 (1950 ex-work) /1620-2420 (1850 ex-work) |
| Track base adjusting way | Limited/unlimited |
| Minimum ground clearance (mm) | 520 |
| Min. operational weight (kg) | 4755 |
| Front /Rear axle weight (kg) | 2050/2705 |
| Front Ballast | 440kg (11 pcs, 40kg/pcs) |
| Rear Ballast | 520kg (2 lays each side) |
| Covering | Air-conditioning Cabin or Sunshade (Canopy) |
| Structure weight (kg) | 5400(without cabin)/5780 (with cabin) |
DQ1504 150HP 4WD Heavy duty big tractor showing:
DQ1504 150HP 4WD Tractor have Canpy(Sunshade) type and AC cabin type for choose:
Top-rank technical team and Advance R&D Center :
Advance Production workshop :
Strictly inspect for every set machine before Goods Delivery :
Company Honors and Certificates:
Personalized Packing and Transporting Service to meet different customers’ demand :
Perfect after-sale service for both Distributors and Private customers:
Please contact us if you have any demand for our Product :
Best price will be quoted for you as soon as receive your Requirement !
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.
