KR0162721B1 - Differential piston type hydraulic bracing device - Google Patents

Abstract

The present invention replaces and installs a plurality of hydraulic bracings installed between the engine and the hull to differential piston type hydraulic bracing to catch the vibration generated in the engine of the ship, while generating the engine while supporting the main engine in the lateral direction reliably. The present invention relates to a differential piston type hydraulic bracing device that reduces lateral and longitudinal vibrations to prevent the hull from overloading, and is provided in a plurality of bracing devices provided only at the front, rear, left and right ends of the engine, or on one side of the engine. The accumulator (3) is disposed inside the differential piston rod (7), which is a bracing flow part, and the relief valve (2) and the bypass valve (10) are provided in the valve box provided at the center of the bracing. , A pressure switch (4) and a low pressure chamber (9) between the piston rod (7) outside and the cylinder (11). It is a differential piston type hydraulic bracing in which spherical joints 6 are disposed at both ends of the y-shing.

Description

Differential Piston Type Hydraulic Bracing Device

1 is a schematic diagram of a differential piston type hydraulic bracing of the present invention.

2 is a schematic view of an operating state of the present invention differential piston type hydraulic bracing.

3 is a schematic diagram of a conventional hydraulic bracing.

4 is a schematic view of an operating state of a conventional hydraulic bracing.

* Explanation of symbols for the main parts of the drawings

1: check valve 2: relief valve

3: accumulator 4: pressure switch

5: sealing 6: spherical joint

7: piston rod 8: high pressure chamber

9: low pressure chamber 10: bypass valve

11: cylinder

The present invention relates to a differential piston type hydraulic bracing (DIFFERENTIAL PISTON TYPE HYDRAULIC TOP BRACING) device, and more specifically, to a differential piston type of a plurality of hydraulic bracings installed between the engine and the hull to reduce vibration generated in the engine of the ship. The present invention relates to a differential piston type hydraulic bracing device which replaces and installs with hydraulic bracing to reduce lateral and longitudinal vibrations generated in the engine so as not to overload the hull.

In general, hydraulic bracing, in which the maximum compression reaction force is set by the pressure relief valve, is installed to connect and support the hull and the engine. Since the size of the ship is large, the engine or the size of the large sized vessel to drive the large vessel is large. Appropriately reducing the force of vibration generated by the engine requires considerable technology. Too little compression reaction force of hydraulic bracing does not reduce the vibration of the engine. Conversely, if the bracing is too loosely assembled or vulnerable, it will cause cracks or cuts in the joints, making it impossible to function.

Conventionally, as shown in FIG. 3, when a certain amount of force is applied to the high pressure chamber, the oil opens the relief valve and flows to the accumulator side. The piston assembly is shaped like a ram, which is about 1.3 times the stroke volume of the piston. Since the pressure is large, the entire volume also occupies a large space, and a mechanical leak pressure gauge 20 is attached to the outside to confirm that the oil or gas leaks, and the mechanical pressure gauge 20 itself is a cause of leakage. In addition, the low pressure relief valves and solenoid valves are intricately composed of high pressure relief valves, low pressure relief valves and solenoid valves for pressure selection, although the frequency of use is very low.

FIG. 4 schematically illustrates a reaction force caused by eccentric vibration of a conventional hydraulic bracing. When a force is applied to the piston assembly while the connecting rod is inclined, the vertical load is generated in the hydraulic seal assembly.

Therefore, in the related art, excessive stress is generated at the bracing connection due to excessive vibration of the engine or installation eccentricity at both ends of the bracing, such that oil leakage due to fatigue occurs.

The present invention has been made in order to solve the above problems, the engine is installed on the front, rear and left and right ends of the engine or left and right one side and the differential piston type hydraulic bracing that is returned by the air pressure of the accumulator as a single-acting engine. Exposed between the hull and the hull, a chuck valve and a relief valve disposed inside the differential piston type bracing and controlling the piston left and right chambers are attached to the bracing, and a compression force greater than the force limited by the set pressure of the relief valve When acting on the hydraulic upper bracing, the relief valve opens and oil in the high pressure chamber escapes into the low pressure chamber and is stored in the accumulator and pushes the piston rod.

In this state, the compressive force of the load decreases again so that the oil stored in the high pressure chamber is lower than the pressure in the low pressure chamber. The oil stored in the low pressure chamber is compressed by the accumulator into the high pressure chamber through the chuck valve, and the piston rod is pushed back to its original position. The principle of return is to reduce the transverse and longitudinal vibrations generated in the engine while supporting the engine in the transverse direction.

Hereinafter, a detailed configuration and effect will be described with reference to the accompanying drawings.

1 is a schematic view of the differential piston type hydraulic bracing of the present invention. When a compression force greater than the force limited by the set pressure of the relief valve 2 acts on the hydraulic upper bracing, the relief valve 2 is opened to open the high pressure chamber. The oil of (8) exits the low pressure chamber (9), half of which is stored in the accumulator (3), and the piston rod (7) is pushed in. In this state, the load compressive force decreases again and is stored in the high pressure chamber (8). When the oil is lower than the pressure in the low pressure chamber 9, the oil stored in the low pressure chamber 9 is compressed by the pneumatic pressure of the accumulator 3 into the high pressure chamber 8 through the chuck valve 1 and the piston rod 7 Is pushed out again and returned to its original position. Only half of the amount of oil opening and exiting the relief valve 2 flows to the accumulator 3, thereby reducing the size of the gas chamber of the accumulator 3 to 1/2. Can reduce its size, This makes it possible to significantly reduce the size of the differential piston type hydraulic bracing than the conventional volume, and by installing the pressure switch 4 instead of the mechanical leak pressure gauge, the gas pressure may be lower than the constant pressure due to the leakage of oil or gas. When lowered, an alarm is issued from an alarm installed separately in the control room to prevent leakage of gas or oil. The valve box also includes a relief valve (2) and a bypass valve (BY-PASS V / V). Since the hydraulic components can be simplified and can be attached within the range of the hydraulic bracing, there is no fear of hydraulic bracing installation position or external mechanical damage.

2 is a schematic view of the operating state of the differential piston type hydraulic bracing device of the present invention, and the spherical joint 6 is located at both ends of the hydraulic bracing. To prevent.

Reference numeral 5 is a seal, and 11 is a cylinder.

Therefore, the present invention is a differential piston-type hydraulic bracing device, which relates to an apparatus capable of preventing the leakage of oil or gas as well as protecting the engine by reducing the transverse support role of the engine and the lateral and longitudinal vibrations generated in the engine. will be.

Claims (1)

In a plurality of bracing devices provided only at the front, rear, left and right ends of the engine, or at the left and right ends thereof, the accumulator 3 is disposed inside the differential piston rod 7 which is the bracing flow part, and the brace is arranged at the center of the bracing. A relief valve 2, a bypass valve 10, and a pressure switch 4 are installed in the valve box disposed outside the valve 1 and the bracing, and the low pressure chamber between the piston rod 7 outside and the cylinder 11 is provided. (9), and the differential piston type hydraulic bracing, characterized in that the spherical joints (6) are disposed at both ends of the differential piston type hydraulic bracing.