valve plate hydraulic pump supplier

Proper setup requires knowledgeable individuals with capable test equipment. Whether it’s a constant volume vane pump, a gear pump or a variable volume, pressure compensated horsepower limiting pump, we can fulfill all your requirements.

We offer lapping capabilities to rectify and refurbish thrust and valve plates for pumps and motors. This allows us to improve turnaround time and reduce the overall cost of repairs.

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The K3VLS series are axial piston, swash-plate type pumps, designed for open loop systems. They are suitable for mobile and industrial applications with medium duty pressure requirements. The K3VLS pumps are a compact, light-weight design with performance and reliability to suit many medium duty applications. With many control options, mounting and thru drive configurations, the K3VLS pumps offer excellent flexibility for system design considerations.

Along with constantly improving performance, industrial machines continue to become increasingly sophisticated. Hydraulic equipment has to meet the challenge of diversifying needs.

You may already appreciate the Nachi-Fujikoshi reputation for compact equipment that delivers energy efficiency, safety, and high performance. Our equipment is also constantly refined by our quest for ultimate hydraulics that combine great power with flexible motion control.

We are focus on the research and development for hydraulic piston pump and gear pump industry parts according to customer drawings.Such as piston shoes, ball guide, valve plate, cylinder block, bearing, pressure plate, copper bushing, thrust plate for gear pump.

Due to the limitations of the parametric study, an optimization methodology is required to optimize the valve plate parameters to reduce the pump noise. A multi-objective optimization genetic algorithm that accounts for both the structure-borne noise sources and fluid-borne noise sources is employed.

At the beginning of the multi-objective optimization, objective functions must be defined properly to describe the noise characteristics. The amplitude of the swash plate moment and the flow rates in the inlet and outlet ports are chosen as the objective functions for their good representation of structure-borne noise sources and fluid-borne noise sources. There are three objective functions in total, as given by Eqs. (12)‒(15):

The ten structural parameters listed in Table 1 are variables used for the optimization. The parameters defining the starting and ending positions of the inlet and outlet ports result in four variables. The parameters defining each damping hole are the center of the location and the radius of the damping hole. There are six variables for the three damping holes in total. The ranges of the variables are also required to allow for the manufacturing of an actual valve plate, and their values are set according to the parametric analysis. In addition, different constraints are required to provide a reasonable and realistic optimization. The pressure overshoot and undershoot are limited, for which the smallest and largest piston chamber pressures are used as constraints to avoid unexpected phenomena. The upper limit of the piston chamber pressure is 3 MPa higher than the average outlet pressure, whereas the lower limit is 0.05 MPa to avoid air-release and cavitation.

Pareto-optimal solutions are obtained at the finish of the optimization as shown in Figure 20. Each triangle represents an individual design (49 out of 858). Among the designs, the amplitude of the inlet flow rate varies between 10 and 40 L/min, the amplitude of the outlet flow rate varies between 2 and 7 L/min, and the amplitude of the swash plate moment varies between 80 and 300 Nm. When the outlet flow ripple is the smallest, the inlet flow ripple is the largest, whereas when the inlet flow ripple is the smallest, the outlet flow ripple is the largest (Figure 20(a)). In addition, when the inlet flow ripple decreases, the swash plate moment increases (Figure 20(b)). Because the three objective functions are weighted equally, the optimal design is chosen as the one nearest to the origin (min (f1(x)2 + f2(x)2 + f3(x)2)1/2).

The final values of the valve plate parameters are determined by rounding the optimization result, as shown in Table 1. The simulated noise sources at a wide range of pressure levels for the original and optimized valve plates are shown in Figure 21. In the simulation, the pressure in the outlet line is regulated by a pressure relief valve, which coincides with the noise measurement in Section 5.5. In the optimization, the pressure in the outlet line is regulated by the throttle valve. This is because the pressure relief valve would affect the dynamics in the outlet line by varying the opening of the pressure relief valve to maintain a constant outlet pressure, whereas the dynamics are not affected by using the throttle valve. Therefore, the flow rates in the outlet and inlet are different when different methods are used to load the system.

As shown in Figure 21(a), the amplitudes of the outlet flow rates are reduced when the pressure levels are larger than 15 MPa, and the amplitudes are nearly the same when the pressure levels are smaller than 15 MPa. The amplitudes of the inlet flow rates are reduced at 25 and 28 MPa, and the values increase as the pressure level gets smaller. The amplitude of the swash plate moment is reduced when the pressure level is higher than 10 MPa, and the values increase at 5 and 10 MPa. The main cause of the larger noise sources is that the optimization is carried out at the rated operating condition (28 MPa), and the optimal results obtained at this operating condition cannot reduce the noise sources at lower pressure levels. However, because the investigated pump is designated to be used at a high pressure, the increase in noise sources at low pressures is acceptable.

The noise of the pump with the original and optimized valve plates was measured in a hemi-anechoic chamber built according to the requirements of ISO 4412-1 [30], as shown in Figure 22. The interior clear dimensions of the hemi-anechoic chamber are 5.1 × 4.4 × 2.6 m3 (length, width and height) with a minimum background noise of 11.4 dB and a lowest measurable frequency of 25 Hz. The test arrangement keeps the pump placed at the center of the reflecting plane. The pump mounting and drive shaft support bearing are mounted on massive concrete blocks to structurally isolate them from the floor to prevent vibrations from exciting the entire building.

The inlet, outlet and leakage lines are all flexible hoses. The shortage is that no acoustic cladding has been done to them, and no acoustic cladding has been done to the shaft support either. This allows the noise emitted from these components to reach the microphones as well. However, the noise emitted from these components is smaller than that emitted by the pump, and the measured sound pressure level can be regarded as the sound pressure level emitted from the pump.

The hydraulic system used to drive the pump is situated in another room to eliminate the effects of their noise on reducing the measurement accuracy. The hydraulic system is shown in Figure 23, with the specifications listed in Table 3. The pump is driven by an electrical motor, and the pressure in the outlet line is regulated by a pressure relief valve. A cardan shaft is used to transmit the torque to the pump with a hook joint at the motor end and a coupling at the pump end.

Figure 24 shows the sound pressure levels from the axial piston pump with the original and optimized valve plates at the speed of 1500 r/min and the maximum displacement. The noise level increases with an increase of pressure level. The noise level of the optimized design is higher at the pressure levels of 5 and 10 MPa. This result coincides with the increases of noise sources at low pressure levels (Figure 21). The optimized design is quieter than the original design when the measured pressure levels are larger than 15 MPa, and the noise level at the rated pressure is reduced from 80.7 dB(A) to 79.1 dB(A).

The objectives of this research are to investigate the principal advantages of using various valve-plate slot geometries within an axial piston pump. In particular, three types of geometries are considered: a constant area slot geometry, a linearly varying slot geometry, and a quadratically varying slot geometry. By analyzing the pressure transients that are associated with each design at low pump displacements, it is shown that the magnitude of the pressure transition itself and the maximum pressure time rate-of-change may be specified for each design. In conclusion, it is shown that the constant area slot design exhibits the principal advantage of minimizing the required discharge area of the slot, the linearly varying slot design exhibits the principal advantage of utilizing the shortest slot length, while the quadratically varying slot design exhibits no principal advantage over either of the other two designs. The results of this research suggest that the use of quadratically varying slot geometry is not justified since it offers no obvious performance improvement.

A hydraulic Cylinder is the most basic pump used to turn the valve plate to regulate the pressure of electronic, hydraulic systems. There are different methods for achieving this, such as ball and mechanical valves. The most straight way is to use a valve made of metal or plastic. They can be operated using a motor that is powered by electricity. It is referred to as an Electrohydraulic Pump (EHP). This mechanical pump has several advantages, including ease of maintenance, low cost, and long service life. They"re highly efficient, particularly in medium and large industries.

They utilize electric power to transport fluids and provide constant flow pressure within hydraulic systems. These pumps are used in numerous chemical plants, breweries, oils refineries, food processing factories, and other manufacturing facilities.

It is ideal for applications that require high-pressure output. It is a high-speed motor that can generate a high-pressure output, but it"s not recommended for use in low-pressure situations. The hydraulic fluid and the electricity are the two primary elements of this pump. Electro-Hydraulic Pumps are engineered to ensure reliability in various types of applications in the industrial sector. They are typically used in industrial and agricultural uses.

Electro-Hydraulic pumps are ideal for those needing an efficient, durable pump that can last. The Pumps have been designed to last and are highly efficient. The electro-hydraulic pumps have been made to supply fluids in various conditions. It can pump fluids with high viscosity, like water-based and molasses-based fluids. The pump is a highly durable, strong material that can stand up to heavy bars of pressure. Electro-Hydraulic Pumps are designed for use in the following scenarios.

Gs hydraulic is a well-known company that makes Electrohydraulic pumps and other parts that go with them. Since 1990, the group has been in business. We are the best Electrohydraulic pumps Suppliers and Dealers in Mumbai, Maharashtra, and India. It has grown to be one of the largest Suppliers in its field. The company makes Axial piston pumps, internal gear pumps, external gear pumps, radial piston pumps, and other parts used in cars, factories, and farms. It also offers services for oil pressure, rotating assembly, and compressors.

It is now one of the biggest companies that supplies different types of pumps, motors, and valves. Its main business is making pumps and pump systems used in cars, machines, fields, and other industrial settings. A team of experts at the company makes engines like oil pressure, internal gear pumps, centrifugal drum and piston pumps, and others. It also makes parts like bearings, seals, washers for directions, and other accessories. The company has a big factory in India, and the people who work there have a lot of experience with different systems. It sells high-end, high-quality products to people who know how to make hydraulic devices. Hence, we are the best Electro hydraulic pump Suppliers.