KR100250789B1 - Bracing for shockabsorbing of main engine - Google Patents

Abstract

PURPOSE: A bracing device is provided to improve ship quality by preventing vibration delivery to a hull with absorbing efficiently horizontal and vertical vibrations as well as impact force generated from an engine, to apply hydraulic and pneumatic pressure inside a cylinder and to enhance returning force of a piston by a spring and a plunger pressure-adjusted. CONSTITUTION: A bracing device for a ship engine is divided into a main chamber(59), a subsidiary chamber(60) and an air chamber(61) by a flange(56) and a subsidiary piston(58) fixed on a piston(52) end. A cylinder(51) is equipped with a check valve(65) for an oil movement filled in the subsidiary chamber and in the main chamber and with a filling valve(66) for compensating for hydraulic and pneumatic pressure in the main chamber, the subsidiary chamber and the air chamber. In a plunger groove(70) communicated with an air hole(73) and with the air chamber(61), the piston(52) includes a return spring(71) and a plunger(72). By combining an extension bar(82) and a distance bolt(83) containing a bolt groove(81) outside of the piston(52), a jointer(54) is equipped to be length-variable.

Description

Bracing device for vibration damping of ship engine

The present invention relates to a bracing device for vibration damping of ship engines, and more particularly, to a bracing device for preventing transmission to a hull while effectively absorbing vibrations generated from an engine of a ship.

In the case of large ships, the size of the engine is considerable, but with the corresponding force (horsepower), the ship generates thrust to move.

In such a large ship, when vibration generated from a large engine is transmitted to the hull, it is a factor that causes not only the abnormality of the hull but also the abnormality of the engine. Therefore, the vibration of the hull by the engine must be kept to a minimum. It becomes a baro-mater.

For this reason, the intrinsic vibration of the engine, which is the main cause of the hull vibration, is minimized from being transmitted to the hull, and the vibration of the engine itself is minimized by using an appropriate support device to protect the engine, its attached facilities, and the facilities of the hull. There is a need for a device capable of exerting.

In order to accommodate such demands, a bracing device has been developed and used to absorb and offset the engine vibration to isolate the hull and at the same time perform a supporting function of the engine.

There are many kinds of such bracing devices, and examples thereof include bar type 1 and hydraulic cylinder type 2 using hydraulic pressure.

In the case of the bar type 1, the rod-shaped long bar 6 is fixed by welding between the engine 3 and the hull 4 with the fixing bracket 5 interposed therebetween.

In such a case, since the structure is simply fixed between the engine 3 and the hull 4 by the bar 6 without fluidity, it is difficult to absorb the vibration generated by the engine, and the vibration of the engine is difficult. There is a high risk of cracking.

In addition, since the overall length is long and the weight is heavy, considerable difficulties arise in installation.

Overall, it does not play a role of blocking the transmission of the engine to the hull by absorbing the vibration of the engine, and serves to support the engine and the ship's hull. Investors will be wasted on unnecessary parts replacement.

In addition, when the engine is mounted on a large vibration engine such as a large ship, the welding part may be damaged by cracks due to the vibration, which may require post maintenance. This type is suitable for small engines with a weak degree.

In the case of the hydraulic cylinder type (2), a pump for supplying hydraulic pressure to the cylinder (11) fixed to the hull (10) and the piston rod (13) and the cylinder (11) inserted into it and fixed to the engine (12) 14 and a plurality of pipelines 15.

In the case of the hydraulic cylinder type as described above, the strength against the impact is relatively excellent compared to the bar type, but can not exhibit sufficient vibration absorbing power, and above all, there is a problem that a considerable investment in additional auxiliary equipment.

In other words, a considerable amount of manpower, time and money must be invested in the installation of pumps, pipelines and other electrical equipment as a means of supplying hydraulic pressure into the hydraulic cylinders, thus occupying a lot of installation space and paying attention to maintenance and maintenance.

In addition, the piston is inserted into the cylinder by vibration and shock generated from the engine, and the piston is absorbed. The resilience of the inserted piston is so weak that the vibration and shock absorption functions are substantially inadequate.

This means that if the speed at which the piston is inserted into the cylinder while absorbing vibration and shock is 5 mm / S, the speed required for restoring the piston is about 8 mm / S. There were problems such as.

Therefore, the present invention solves the above problems by providing a bracing device having a simple structure without additional equipment for performing an auxiliary role, and effectively absorbs vibration generated in the engine as well as transverse and longitudinal vibrations. The purpose is to prevent the vibration of the ship to be transmitted to the hull, improve the quality of the ship.

To this end, the present invention is characterized in that the oil and pneumatic pressure are simultaneously applied in the cylinder, and the restoring force of the piston is improved by the spring and the plunger which are pressure-controlled by the oil and pneumatic pressure inside the piston.

1 is a front view showing an embodiment of a conventional bracing device.

2 is a front view of a bracing device showing another embodiment of the prior art.

3 is a schematic front view of a bracing device to which the technique of the present invention is applied.

Figure 4 is a perspective view of the bracing device of the present invention.

FIG. 5 is a half sectional view taken along the line A-A of FIG.

6 to 8 are schematic cross-sectional views showing the operating relationship of the bracing device of the present invention,

6 is a sectional view showing an initial state.

7 is a cross-sectional view showing a vibration absorption state.

8 is a sectional view showing a state restored to an initial state.

* Explanation of symbols for main parts of the drawings

51: cylinder 52: piston

54: Jointer 65: Check Valve

71: restoring spring 72: plunger

84,85: Male Bushing

Looking at the working relationship with the preferred embodiment of the present invention for achieving the above object with reference to the accompanying drawings as follows.

3 is a schematic front view of a bracing device to which the technique of the present invention is applied, FIG. 4 is a perspective view showing the bracing device of the present invention, FIG. 5 is a half sectional view taken along line AA of FIG. 4, and FIGS. 6 is a cross-sectional view showing an initial state, FIG. 6 is a cross-sectional view showing a vibration absorption state, and FIG. 8 is a cross-sectional view showing a state restored to an initial state. Explain together.

The bracing device 100 of the present invention is largely composed of a cylinder 51 fixed to the hull 50, a piston 52 accommodated therein, and a jointer 54 fixed to the engine 53. The outer side of the and the jointer 54 is provided with a bracket 55 for fixing the hull 50 and the engine 53.

The cylinder 51 has a main chamber 59 filled with oil by a flange 56 fixed to an end of the piston 52 inserted therein and an auxiliary piston 58 positioned between the flange 56 and the cylinder cover 57. ) And the auxiliary chamber 60 and the air chamber 61.

The main chamber 59 and the sub chamber 60 which are partitioned inside the cylinder 51 are provided with a check valve 65 so as to effectively transmit the pressure of the piston 52 which transmits the engine vibration to the cylinder 51. It can be dispersed and canceled out.

The main chamber 59, the auxiliary chamber 60, and the air chamber 61 further include a filling valve 66 for supplementing oil and pneumatic pressure.

A plunger groove 70 is formed in the center of the piston 52 to insert a restoring spring 71 and a plunger 72, and the plunger groove 70 conducts air to the air chamber 61 and the air hole 73. Let's do it.

The auxiliary piston 58 moves the auxiliary piston 58 by the adjustment nut 76 to protrude outwardly through the adjustment nut 76 provided on the cylinder cover 57. By changing the volume of 61, it is possible to adjust the restoring force of the plunger 72.

The jointer 54 provided between the outer side of the piston 52 and the joining groove 80 provided on the bracket 55 fixed to the engine 53 has a gap between the engine 53 and the hull 50. The length can be changed to overcome and install.

An extension bar 82 having a bolt groove 81 formed in the axial direction is inserted into the joiner groove 80 of the piston 52, and a disengagement bolt 80 is inserted into the joiner groove 80 of the bracket 55. A distance bolt (83) is inserted so that the tip of the bolt (83) is screwed into the bolt groove (81) of the extension bar (82).

Both ends of the extension bar 82 and the distance bolt 83 and the inside of the joining groove 80 are provided with the semi-circular and hemispherical hermetic bushings 84 and 85 in the vibration direction of the engine 53. Regardless of the movement, it moves freely to the piston (52).

The male and female bushings 84 and 85 are formed of a material such as reinforced plastic of a synthetic resin system, and have a lubricating effect of smoothing the movement of the jointer 54 as well as a buffering function for primaryly absorbing vibration of the engine 53. It is desirable to be able to perform.

The present invention as described above impacts the main chamber 59, the auxiliary chamber 60 and the air chamber 61 through the filling valve 66 provided in the cylinder 51 in consideration of the size and force of the vessel engine to be applied Supply oil and air for vibration absorption.

When the supply of oil and air is completed on each of the chambers 59, 60, 61, the bracing device 100 is positioned between the engine 53 and the hull 50, and then the outer side of the cylinder 51 and the jointer 54. Fix and install using the bracket 55 provided on the outside.

In this process, the length of the jointer 54 is varied according to the distance between the engine 53 and the hull 50 so that a gap does not occur, and the cylinder 51, the piston 52, and the jaw are prevented. Adjust the inter 54 to the proper position.

The adjustment thereof allows the distance bolt 83 of the jointer 54 to rotate so that the distance bolt 83 enters and exits the bolt groove 81 of the extension bar 82.

As described above, the operation relationship in the state in which the installation of the bracing device 100 is completed is as follows.

The initial state in which the vibration of the engine 53 is not transmitted is in a state in which the jointer 54 does not move as shown in FIG. 6, so that the piston 52 adheres to the initial setting (setting) state.

When the vibration and shock of the engine 53 is transmitted in this state, the aftershock is transmitted to the jointer 54 and the piston 52 through the bracket 55.

Vibration and shock transmitted to the jointer 54 is the piston (84, 85) is further provided at both ends of the jointer 54, the piston ( 52).

In addition, the male and female bushings 84 and 85 positioned at both ends of the jointer 54 buffer the shocks and vibrations transmitted from the engine 53 and apply them to the piston 52 in a state where they are primarily absorbed. 54) lubrication that can move freely.

When the vibration and shock of the engine 53 are transmitted by the jointer 54, the piston 52 is inserted into the cylinder 51 inwardly, so that the reaction force of the oil filled in the main chamber 59 and the auxiliary chamber 61 is increased. This is to offset the shock and vibration.

Actually, the piston 52 receives the vibration and impact force of the engine 53 and is inserted into the cylinder 51 to a very small level (about 1 to 5 mm).

When the piston 52 is inserted, the flange 56 fixed to the end of the piston 52 pressurizes the entire surface of the main chamber 59, so that the oil filled in the main chamber 59 generates a reaction force and at the same time The piston 52 is finally absorbed by the impact force and vibration by moving to the auxiliary chamber 60 through the check valve 65 by the pressing force.

As the oil of the main chamber 59 moves to the auxiliary chamber 60, the volume of the main chamber 59 is reduced while the volume of the auxiliary chamber 60 is increased, and at the same time, the plunger groove (formed at the center of the piston 52) The plunger 72 inserted into 70 overcomes the elasticity of the restoring spring 71 by the oil reaction force in the main chamber 59 and retreats.

At the same time, the air in the air chamber 61 connected to the plunger groove 70 and the air ball 73 is in a state in which the pressure of the plunger 72 is retracted is increased.

After the shock and vibration are absorbed by the above-described action, the piston 52 is restored to the initial state and enters the standby operation standby state. In this case, the piston 52 serves to assist the restoration of the piston 52. Spring 71.

When the vibration and impact force transmitted to the piston 52 are canceled out, the auxiliary chamber 60 has a higher pressure than the pressure of the main chamber 59 because the pressure of the auxiliary chamber 60 whose volume is increased by the oil moved from the main chamber 59 is higher. The piston 52 is restored to the initial state by the pressure of the main chamber 59 gradually increased as the oil of 60 moves to the main chamber 59 by xd the check valve 65.

At the same time, the plunger 72, which has been retracted by the reaction force of the main chamber 59, returns to the initial state due to the recovery of the elastic force of the air chamber 61 and the restoring spring 71, thereby helping to quickly restore the piston 52.

This is because the restoring spring 71 is in a contracted state due to the retraction of the plunger 72 and the pressure of the air chamber 61 is raised, and the air chamber is at the point of returning to the initial state by canceling the vibration and impact force. Since the plunger 72 is positioned by the force to initialize the pressure of the 61 and the elastic recovery of the restoring spring 71, the oil in the main chamber 59 is moved again in the direction of the main chamber 59. This is possible by generating a reaction force against

By absorbing and canceling the impact force and vibration generated in the engine 53 by the continuous repetitive action as described above is to prevent the vibration and impact force of the engine 53 is transmitted to the hull 50 direction.

In the main chamber 59, the auxiliary chamber 60, and the air chamber 61 while the bracing device 100 repeats the process of absorbing and restoring the vibration and impact force by the oil, pneumatic, plunger and spring as described above. If there is room for replenishment of the oil and air filled due to natural extinction, etc., check through a gauge (not shown) provided in the bracing device 100 and then replenish it in an appropriate state through the filling valve 66.

And, in order to increase the restoring force according to the type and size of the engine, etc., the adjustment bolt 74 is connected to the auxiliary piston 58 and protrudes outward through the adjustment nut 76 provided in the cylinder cover 57. By moving in and out of the cylinder cover 57, the auxiliary piston 58 can be moved to adjust the volume of the air chamber 61 to the appropriate state.

The present invention as described above, by absorbing and offsetting the vibration and impact force of the engine by the joint, the piston and the cylinder without the installation of additional supporting equipment, by restoring to the same level as the conditions for absorbing the vibration and impact force Not only contributes to the improvement of the quality of the bracing device but also contributes to the quality and safety of the ship.

Claims (3)

In the configuration of the ship engine vibration damping device 100 for absorbing and canceling the vibration generated in the engine of the ship to prevent transmission to the hull (Hull); The bracing device (100) is divided into a main chamber (59), an auxiliary chamber (60) and an air chamber (61) by a flange (56) and an auxiliary piston (58) fixed to an end of a piston (52); Check valve 65 for oil flow filled in the main chamber 59 and the auxiliary chamber 60, and filling valve for oil and pneumatic supplementation to the main chamber 59, the auxiliary chamber 60 and the air chamber 61 A cylinder 51 further comprising 66; A piston (52) comprising a restoring spring (71) and a plunger (72) in the plunger groove (70) which is conducted to the air chamber (61) and the air hole (73); An extension bar 82 having a bolt groove 81 formed therein and a distance bolt 83 coupled to the outside of the piston 52 are arranged to have a joint 54 provided to be able to change length. Bracing device for vibration damping of ship engine. The bracing device for ship engine vibration dampening according to claim 1, wherein both ends of the jointer (54) are further interposed with a semi-circular and hemispherical male bush (84,85). The ship engine vibration according to claim 1, wherein the auxiliary piston (58) further comprises an adjusting bolt (74) for changing the volume of the air chamber (61) to adjust the restoring force of the plunger (72). Reduction bracing device.