A damper cylinder and a device for fender of ship with thereof

Abstract

The present invention relates to a damper cylinder and a ship anti-buoyant device including the same, and more specifically, to a damper cylinder and a ship anti-buoyant device including the same that can absorb shocks generated from the outside by utilizing fluid friction, and can enable stable operation of the damper cylinder through the shape and structure of a metering pin, and can easily achieve the absorption energy and reaction force conditions required when a ship docks. A damper cylinder according to one embodiment of the present invention is a damper cylinder for absorbing an external shock using fluid friction, comprising: a gas tube having a gas chamber to accommodate gas inside and forming a passage of a predetermined length; a first piston having an orifice formed in the center to form a passage for fluid transfer, which is coupled and fixed to one end of the gas tube; a hydraulic tube having a fluid chamber to accommodate fluid inside and forming a passage of a predetermined length to surround a part of the outer surface of the gas tube and the first piston; a metering pin having a predetermined length formed such that one end is coupled and fixed to the end located on the fluid chamber side among the two ends of the hydraulic tube, and is inserted longitudinally into the orifice to change the frictional force of the fluid passing through the orifice according to the movement of the first piston; and a second piston disposed inside the gas tube to separate the gas chamber and the fluid chamber.

Description

Technology Field

[0001] The present invention relates to a damper cylinder and a ship anti-buoyant device including the same, and more specifically, to a damper cylinder and a ship anti-buoyant device including the same that can absorb shocks generated from the outside by utilizing fluid friction, and can enable stable operation of the damper cylinder through the shape and structure of a metering pin, and can easily achieve the absorption energy and reaction force conditions required when a ship docks. Background Technology

[0002] In the conventional berthing operation of anchoring a vessel to a harbor quay, once the vessel enters the harbor, a pilot first boards the vessel to guide it to the vicinity of the quay; from a point close to the quay (approximately 100m), the operation proceeds using the vessel's own side thrust and receiving support from a tugboat.

[0003] In addition, in conventional technology, not only the crew, pilot, and tugboat of the docking vessel but also a so-called land support team participates to observe the course of the docking vessel from land and provide information to the docking vessel and tugboat, thereby enabling more precise docking operations.

[0004] However, according to this conventional technology, since safe docking operations can only be performed through close cooperation among the three parties—the docking vessel, the tugboat, and the land support team—there is a risk of serious accidents occurring if information transmission among the three parties is not carried out quickly and stably due to reasons such as a malfunction in the means of communication, or if any one team makes an error and loses the ability to respond.

[0005] An example of an accident that can occur during the berthing process is a berthing vessel colliding with a quay wall due to a failure to control its speed. Such collisions cause not only damage to the vessel but also significant losses to port operations, including cracks in the quay wall that require a long time for facility repairs.

[0006] As a solution to the problems of such conventional technology, a buffering means has been devised to prevent direct collision between the quay and the berthing vessel, and to absorb the impact applied to the quay from the berthing vessel, thereby increasing safety during berthing operations.

[0007] For example, the technology described in Korean Published Patent No. 10-2017-0053969 is proposed, and the technology described therein is configured by attaching multiple cushion blocks made of elastic material to the face of a quay wall. According to such conventional cushioning means, when the cushion blocks come into contact with the berthing vessel, the cushion blocks are elastically deformed, thereby absorbing the impact applied from the berthing vessel toward the quay wall.

[0008] However, as described above, due to the nature of the cushioning means according to such conventional technology being composed of a combination of simple cushion blocks, it cannot actively respond to various variables (such as the size, direction of approach, angle of approach, and speed of approach) that affect the collision process with a berthing vessel, and always performs only a passive cushioning action in a fixed pattern against external impacts (forces applied from the vessel).

[0009] Therefore, according to conventional technology, impacts from berthing vessels are not sufficiently and effectively absorbed. Consequently, even though cushioning means are provided, workers must exercise great caution to safely berth the vessel, and since berthing operations are not carried out quickly, the efficiency of port logistics operations does not improve significantly. Furthermore, as the material is made of elastic materials such as rubber, it is difficult to recycle, leading to numerous problems such as environmental pollution caused by unauthorized disposal and quality degradation due to damage. Prior art literature

[0010] Korean Patent Publication No. 10-2017-0053969 (May 17, 2017) The problem to be solved

[0011] The present invention was created to solve the aforementioned problems, and more specifically, aims to provide a damper cylinder and a ship anti-buoyancy device including the same, which can absorb shocks generated from the outside by utilizing fluid friction, enable stable operation of the damper cylinder through the shape and structure of the metering pin, and easily achieve the absorption energy and reaction force conditions required when a ship docks. means of solving the problem

[0012] A damper cylinder according to one embodiment of the present invention is a damper cylinder for absorbing an external shock using fluid friction, comprising: a gas tube having a gas chamber to accommodate gas inside and forming a passage of a predetermined length; a first piston having an orifice formed in the center to form a passage for fluid transfer, which is coupled and fixed to one end of the gas tube; a hydraulic tube having a fluid chamber to accommodate fluid inside and forming a passage of a predetermined length to surround a part of the outer surface of the gas tube and the first piston; a metering pin having a predetermined length formed such that one end is coupled and fixed to the end located on the fluid chamber side among the two ends of the hydraulic tube, and is inserted longitudinally into the orifice to change the frictional force of the fluid passing through the orifice according to the movement of the first piston; and a second piston disposed inside the gas tube to separate the gas chamber and the fluid chamber.

[0013] More specifically, the metering pin is characterized by including a cylindrical stroke portion having a cutting surface of a predetermined area to change the frictional force of the fluid passing through the space between the orifice and the metering pin according to the degree of movement of the first piston and the position on the metering pin.

[0014] More specifically, the cutting surface is formed in the longitudinal direction on one side of the outer circumference of the stroke portion, and is characterized by the area decreasing so that the cross-sectional area of ​​the stroke portion increases as it moves from the end located on the gas chamber side among the two ends of the stroke portion to the other end.

[0015] More specifically, the cutting surface is characterized by being formed such that its length is equal to the length of the stroke portion.

[0016] More specifically, the above-mentioned cutting surface is characterized by being formed to have a planar shape.

[0017] More specifically, the cutting surface is formed in the longitudinal direction on one side of the outer circumference of the stroke portion and is characterized by being formed in a diagonal shape inclined at a predetermined angle with respect to the longitudinal side of the damper cylinder.

[0018] More specifically, the stroke portion is characterized in that the cross-sectional area of ​​the end portion located on the gas chamber side among the two ends is formed to have a value smaller than the cross-sectional area of ​​the orifice, and the cross-sectional area of ​​the other end portion is formed to have a value corresponding to the cross-sectional area of ​​the orifice.

[0019] More specifically, the stroke portion is characterized in that the area of ​​the outer surface region excluding the cutting surface is formed to have a diameter corresponding to the diameter of the orifice.

[0020] More specifically, the metering pin is characterized by having a cylindrical shape formed to extend a predetermined length in the longitudinal direction of the stroke portion from the gas chamber side end of the stroke portion, and having an extension portion formed to have a diameter smaller than the diameter of the orifice and the stroke portion.

[0021] More specifically, the extension is characterized by including a plurality of recessed grooves formed on the outer surface of the extension at a mutually spaced distance apart, forming an area recessed to a predetermined depth in the direction of the center of the extension.

[0022] More specifically, the metering pin comprises a path limiting portion having a cylindrical shape formed to extend a predetermined length in the longitudinal direction of the stroke portion from the gas chamber side end of the extension portion, and having a screw thread formed on its outer surface to allow a fastening member to be fastened; and the extension portion comprises a plurality of catch projections formed on the outer surface of the extension portion at a predetermined distance from each other and formed to protrude a predetermined height from the center of the extension portion toward the outer circumference so as to catch a fastening member fastened to the path limiting portion.

[0023] More specifically, the metering pin is characterized by having a cylindrical shape that is formed to extend a predetermined length in the longitudinal direction of the stroke portion from the end located in the outer direction of the damper cylinder among the two ends of the stroke portion, and having a coupling portion having a screw thread formed on its outer surface so as to be coupled and fixed to a hydraulic tube.

[0024] More specifically, the damper cylinder is formed with a fluid storage space formed between the second piston and the first piston to store fluid discharged from the fluid chamber, and the fluid storage space is characterized by increasing in volume as fluid flows into it when the damper cylinder is compressed, and decreasing in volume as the fluid contained inside is discharged into the fluid chamber when the damper cylinder returns.

[0025] More specifically, the first piston is characterized by including a check valve configured to discharge the fluid contained in the fluid storage space into the fluid chamber when the pressure of the fluid storage space reaches a preset pressure upon the return of the damper cylinder.

[0026] More specifically, the first piston is characterized by including a relief valve configured to urgently discharge fluid contained in a fluid storage space into the fluid chamber when the pressure of the fluid chamber reaches a preset pressure.

[0027] In addition, a ship insect repellent device according to one embodiment of the present invention is characterized by being provided to include the damper cylinder described above.

[0028] More specifically, the ship anti-vibration device is installed on the quay wall of a ship docking facility, and is characterized by the damper cylinder being configured to absorb the shock generated when the ship docks. Effects of the invention

[0029] A damper cylinder according to one embodiment of the present invention can absorb shocks generated from the outside by utilizing fluid friction, and through the shape and structure of the metering pin, stable operation of the damper cylinder is possible, and the effect of easily achieving the absorption energy and reaction force conditions required when docking a ship is provided.

[0030] More specifically, a damper cylinder according to one embodiment of the present invention includes a metering pin, thereby adjusting the length of the stroke in which the piston reciprocates inside the cylinder, and thus providing the effect of more easily achieving various absorption energy and reaction force conditions required of the damper cylinder.

[0031] In particular, the damper cylinder according to one embodiment of the present invention includes a cutting surface formed on one side of the outer circumference of the stroke portion, thereby providing improved machinability compared to a conventional tapered metering pin. Additionally, the portion of the outer circumference of the stroke portion where the cutting surface is not formed, or the portion located opposite to the area where the cutting surface is formed, is fixed in contact with the inner circumference of the orifice, thereby stably maintaining the axial center of the metering pin. This prevents shaking of the metering pin during the operation of the damper cylinder, which would otherwise affect the energy absorbed and reaction force of the damper cylinder.

[0032] In addition, a damper cylinder according to one embodiment of the present invention includes a recessed groove formed on the outer surface of an extension, thereby expanding the area through which the fluid passes and preventing friction from occurring in the fluid even after the fluid flowing into the fluid storage space through the space between the orifice and the cutting surface passes through the cutting surface area, thus providing the effect of more stably realizing the required energy absorption and reaction force performance of the damper cylinder.

[0033] In addition, a damper cylinder according to one embodiment of the present invention includes a check valve, thereby providing the effect of rapidly discharging fluid contained in a fluid storage space into a fluid chamber, enabling the rapid return of the damper cylinder.

[0034] In addition, the damper cylinder according to one embodiment of the present invention includes a relief valve, thereby providing the effect of preventing damage to the rear end of the damper cylinder caused by an abnormal rise in the pressure of the fluid chamber.

[0035] In addition, the ship fender according to one embodiment of the present invention includes a damper cylinder, thereby stably absorbing the impact generated when the ship docks, which prevents damage caused by collision between the ship and the quay wall, and provides the effect of solving problems such as environmental pollution and quality degradation of existing fenders by replacing conventional rubber fenders. Brief explanation of the drawing

[0036] FIG. 1 is a drawing illustrating a damper cylinder according to one embodiment of the present invention. FIG. 2 is a diagram illustrating the compression process of a damper cylinder according to one embodiment of the present invention. FIG. 3 is a diagram illustrating the return process of a damper cylinder according to one embodiment of the present invention. FIG. 4 is a drawing illustrating an orifice and a check valve constituting the first piston of a damper cylinder according to one embodiment of the present invention. FIG. 5 is a drawing illustrating an orifice and a relief valve constituting the first piston of a damper cylinder according to one embodiment of the present invention. FIG. 6 is a cross-sectional view of the first piston of a damper cylinder according to one embodiment of the present invention. FIG. 7 is a perspective view and a front view illustrating a metering pin constituting a damper cylinder according to one embodiment of the present invention. FIG. 8 is an enlarged view showing the extension and path limiting portions of the metering pin illustrated in FIG. 7. FIG. 9 is a drawing illustrating an example in which a ship insecticidal device including a damper cylinder according to one embodiment of the present invention is installed on a quay. FIG. 10 is an enlarged view of the ship insect repellent device shown in FIG. 9. Specific details for implementing the invention

[0037] The following detailed description of the invention refers to the accompanying drawings, which illustrate specific embodiments in which the invention may be practiced. These embodiments are described in sufficient detail to enable those skilled in the art to practice the invention. It should be understood that various embodiments of the invention are different but need not be mutually exclusive. For example, specific shapes, structures, and characteristics described herein may be implemented in other embodiments without departing from the spirit and scope of the invention in relation to one embodiment.

[0038] Furthermore, it should be understood that the location or arrangement of individual components within each disclosed embodiment may be changed without departing from the spirit and scope of the invention. Accordingly, the following detailed description is not intended to be taken in a limiting sense, and the scope of the invention is limited only by the appended claims, including all equivalents thereof, provided appropriately described. Similar reference numerals in the drawings refer to the same or similar functions across various aspects.

[0039] Hereinafter, in order to enable a person skilled in the art to easily practice the present invention, preferred embodiments of the present invention will be described in detail with reference to the attached drawings.

[0040] First, a damper cylinder according to an embodiment of the present invention will be described with reference to FIGS. 1 to 3.

[0041] FIG. 1 is a drawing illustrating a damper cylinder according to an embodiment of the present invention, FIG. 2 is a drawing illustrating the compression process of a damper cylinder according to an embodiment of the present invention, and FIG. 3 is a drawing illustrating the return process of a damper cylinder according to an embodiment of the present invention.

[0042] The damper cylinder of the present invention is a device for absorbing shocks generated from the outside by utilizing fluid friction.

[0043] As illustrated in FIG. 1, the damper cylinder (1000) of the present invention includes a gas tube (100), a first piston (200), a hydraulic tube (300), a metering pin (400), a second piston (500), and a joint unit (600).

[0044] First, the gas tube (100) is characterized by having a gas chamber (110) to accommodate gas inside, as shown in FIG. 1, and forming a passage of a predetermined length.

[0045] In addition, the gas tube (100) is formed such that a first piston (200) is connected to one end and a first cover (120) is connected to the other end so that gas inside the gas chamber (110) does not leak out to the outside.

[0046] Next, the first piston (200) is characterized by being coupled and fixed to one end of the gas tube (100) as described above, and having an orifice (210) that forms a passage for fluid to be transported in the center.

[0047] At this time, the orifice (210) is provided in the form of a through hole in the center of the first piston (200).

[0048] Hereinafter, the detailed configuration of the first piston (200) will be explained in more detail with reference to FIGS. 4 to 6, which will be described later.

[0049] Next, the hydraulic tube (300) is provided with a fluid chamber (310) to accommodate fluid inside, as shown in FIG. 1, and is provided to form a passage of a predetermined length to surround a part of the outer surface of the gas tube (100) and the first piston (200).

[0050] At this time, the fluid may be provided in the form of oil.

[0051] In addition, the hydraulic tube (300) is formed such that a second cover (320) is attached to the end located on the side of the fluid chamber (310) among the two ends so that the fluid inside the fluid chamber (310) does not leak out to the outside.

[0052] Next, the metering pin (400) is formed with a predetermined length and is characterized in that one end is fixedly connected to the end located on the fluid chamber (310) side among the two ends of the hydraulic tube (300).

[0053] More specifically, the metering pin (400) can be fastened to the second cover (320) and secured to the end of the hydraulic tube (300).

[0054] Here, the metering pin (400) is inserted longitudinally into the orifice (210) described above and is configured to change the frictional force of the fluid passing through the orifice (210) according to the movement of the first piston (200).

[0055] Accordingly, the damper cylinder of the present invention includes a metering pin (400), thereby adjusting the length of the stroke in which the piston reciprocates inside the cylinder, and thus providing the effect of more easily achieving various absorption energy and reaction force conditions required of the damper cylinder.

[0056] Hereinafter, the detailed configuration of the metering pin (400) will be described in more detail with reference to FIGS. 7 and FIGS. 8, which will be described later.

[0057] Next, the second piston (500) is positioned inside the gas tube (100) as shown in FIG. 1 to separate the gas chamber (110) and the fluid chamber (310).

[0058] More specifically, the second piston (500) may be provided in the form of a separator or a floating piston.

[0059] Through the configuration of the gas tube (100) to the second piston (500) described above, the damper cylinder (1000) of the present invention is characterized by being driven to compress and return as shown in FIGS. 2 and FIGS. 3.

[0060] At this time, the damper cylinder (1000) of the present invention is formed with a fluid storage space (S) formed between the second piston (500) and the first piston (200) during the compression and return driving process to store fluid discharged from the fluid chamber (310).

[0061] More specifically, as shown in FIGS. 2a to 2c, the damper cylinder (1000) of the present invention is compressed as the gas tube (100) and the first piston (200) are pushed toward the fluid chamber (310) by an impact generated from the outside.

[0062] When the damper cylinder (1000) is compressed, as shown in FIG. 2b, the fluid contained inside the fluid chamber (310) flows into the fluid storage space (S) through the space between the metering pin (400) and the orifice (210) described above.

[0063] Here, the fluid storage space (S) is characterized by an increase in volume as fluid flows into it, as shown in FIGS. 2b and 2c.

[0064] Next, the damper cylinder (1000) of the present invention is driven back as the gas tube (100) and the first piston (200) are pushed in the opposite direction of the fluid chamber (310), as shown in FIGS. 3a to 3c.

[0065] When the damper cylinder (1000) is driven back, as shown in FIG. 3b, the fluid contained in the fluid storage space (S) is discharged into the fluid chamber (310) through the check valve of the first piston to be described later.

[0066] Here, the fluid storage space (S) is characterized by a decrease in volume as the fluid contained inside is discharged to the outside, i.e., the fluid chamber (310), as shown in FIGS. 3b and 3c.

[0067] As described above, the damper cylinder of the present invention provides the effect of more stably absorbing shocks generated from the outside by utilizing the friction of the fluid occurring between the metering pin (400) and the orifice (210).

[0068] Additionally, the damper cylinder (1000) of the present invention is equipped with joint units (600) at both ends so that it can be installed on objects for various purposes, and the joint units (600) can be configured in the form of universal joints so as to absorb shocks occurring in various directions.

[0070] Next, the first piston (200) constituting the damper cylinder of the present invention will be described in more detail with reference to FIGS. 4 to 6.

[0071] FIG. 4 is a drawing illustrating an orifice and a check valve constituting the first piston of a damper cylinder according to one embodiment of the present invention, FIG. 5 is a drawing illustrating an orifice and a relief valve constituting the first piston of a damper cylinder according to one embodiment of the present invention, and FIG. 6 is a drawing illustrating a cross-section of the first piston of a damper cylinder according to one embodiment of the present invention.

[0072] First, the first piston (200) includes an orifice (210), a check valve (220), and a relief valve (230), as shown in FIG. 6.

[0073] As previously explained, the orifice (210) is provided in the center of the first piston (200) in the form of a through hole to form a passage through which fluid is transported.

[0074] Next, the check valve (220) is configured to discharge the fluid contained in the fluid storage space into the fluid chamber when the pressure of the fluid storage space described above reaches a preset pressure upon the return of the damper cylinder.

[0075] More specifically, as shown in FIG. 4, the check valve (220) may be provided in multiple numbers and spaced apart from each other by a predetermined distance with respect to the orifice (210).

[0076] Accordingly, the damper cylinder of the present invention includes a plurality of check valves (220), thereby providing the effect of rapidly discharging the fluid contained in the fluid storage space into the fluid chamber, enabling the rapid return of the damper cylinder.

[0077] Next, the relief valve (230) is configured to urgently discharge fluid contained in the fluid storage space into the fluid chamber when the pressure of the fluid chamber described above reaches a preset pressure.

[0078] At this time, the preset pressure of the relief valve (230) is set to a higher pressure than the preset pressure of the check valve (220).

[0079] For example, the preset pressure of the check valve (220) can be set to about 50 bar, and the preset pressure of the relief valve (230) can be set to about 180 bar.

[0080] More specifically, the relief valve (230) is a valve that operates when the pressure in the fluid chamber reaches an abnormally high pressure, and does not operate when the damper cylinder is in a normal operating state.

[0081] Accordingly, the damper cylinder of the present invention includes a plurality of relief valves (230), thereby providing the effect of preventing damage to the rear end of the damper cylinder caused by an abnormal rise in the pressure of the fluid chamber.

[0082] Additionally, as shown in FIG. 5, the relief valve (230) may be provided in multiple numbers, similar to the check valve described above, and may be spaced apart from each other by a predetermined distance with respect to the orifice (210).

[0083] Accordingly, the check valve (220) and relief valve (230) can be arranged radially with respect to the orifice (210), as shown in FIG. 6.

[0085] Next, the metering pin (400) constituting the damper cylinder of the present invention will be described in more detail with reference to FIGS. 1, FIGS. 7 and FIGS. 8.

[0086] FIG. 7 is a perspective view and a front view illustrating a metering pin constituting a damper cylinder according to one embodiment of the present invention, and FIG. 8 is an enlarged view illustrating an extension and a path limiting portion of the metering pin illustrated in FIG. 7.

[0087] As previously explained, the metering pin (400) is inserted longitudinally into the orifice (210) described above and is configured to change the frictional force of the fluid passing through the orifice (210) according to the movement of the first piston (200).

[0088] More specifically, the metering pin (400) includes a stroke portion (410), an extension portion (420), a path limiting portion (430), and a coupling portion (440), as shown in FIG. 7.

[0089] First, the stroke portion (410) is provided in a cylindrical shape having a cutting surface (411) of a predetermined area to change the frictional force of the fluid passing through the space between the orifice (210) and the metering pin (400) according to the degree of movement of the first piston (200) and the position on the metering pin (400).

[0090] Here, the cutting surface (411) is formed in the longitudinal direction on one side of the outer surface of the stroke portion (410) as shown in FIG. 7, and is characterized by the area becoming smaller so that the cross-sectional area of ​​the stroke portion (410) becomes wider as it goes from one end, which is the end located on the gas chamber side among the two ends of the stroke portion (410), to the other end.

[0091] Accordingly, the damper cylinder of the present invention has a structure in which the fluid passage area gradually decreases as the first piston described above moves, and thus the friction of the fluid gradually increases, thereby allowing it to absorb shocks generated from the outside using the friction of the fluid, and through the shape and structure of the metering pin (400), stable operation of the damper cylinder is possible, and the absorption energy and reaction force conditions required when docking a ship can be easily achieved.

[0092] In particular, the damper cylinder of the present invention includes a cutting surface (411) formed on one side of the outer circumference of the stroke portion, thereby providing improved machinability compared to a conventional tapered metering pin. Additionally, the portion of the outer circumference of the stroke portion where the cutting surface is not formed, or the portion located opposite to the area where the cutting surface is formed, is fixed in contact with the inner circumference of the orifice, thereby stably maintaining the axis center of the metering pin. This prevents shaking of the metering pin during the operation of the damper cylinder, which would otherwise affect the energy absorption and reaction force of the damper cylinder.

[0093] More specifically, the cutting surface (411) is characterized by being formed such that its length is equal to the length of the stroke portion (410), as shown in FIG. 7.

[0094] Accordingly, the cutting surface (411) is configured to change the frictional force of the fluid over the entire length of the stroke section (410), thereby securing the energy absorbed by the damper cylinder for the length of the stroke section, reaching the maximum reaction force with a short stroke, and maintaining the maximum reaction force constant, thus providing the effect of enabling more efficient driving of the damper cylinder.

[0095] In addition, the cutting surface (411) is formed to have a flat shape, which can provide the effect of facilitating the manufacturing and processing of the metering pin (400).

[0096] In other words, the cutting surface (411) is formed in the longitudinal direction on one side of the outer circumference of the stroke portion (410) as shown in FIG. 7, and is formed in a diagonal shape inclined at a predetermined angle with respect to the longitudinal side of the damper cylinder.

[0097] More specifically, the cutting surface (411) is formed to form an arc and a chord of the cylindrical cross-section of the stroke portion (410) with respect to the longitudinal front of the damper cylinder, as shown in FIG. 8b.

[0098] Here, the stroke portion (410) is characterized in that the cross-sectional area of ​​the end portion located on the gas chamber (110) side among the two ends is formed to have a value smaller than the cross-sectional area of ​​the orifice (210) described above, and the cross-sectional area of ​​the other end portion is formed to have a value corresponding to the cross-sectional area of ​​the orifice (210).

[0099] In other words, the maximum diameter of the stroke portion (410) is formed to a value corresponding to the diameter of the orifice (210).

[0100] Additionally, as shown in FIG. 7 and FIG. 8b, the stroke portion (410) is formed such that the portion excluding the cutting surface (411) among the outer surface areas has a diameter corresponding to the diameter of the orifice.

[0101] More specifically, the stroke portion (410) is characterized in that the maximum diameter is formed uniformly throughout the entire length direction, but due to the formation of the cutting surface (411), the cross-sectional area increases from the end located on the gas chamber side among the two ends to the other end.

[0102] As described above, the damper cylinder of the present invention can provide improved machinability compared to a conventional tapered metering pin through the structural shape of the stroke portion (410), and the portion of the outer circumference of the stroke portion where a cutting surface is not formed or the portion located opposite to the area where a cutting surface is formed is fixed in contact with the inner circumference of the orifice, thereby stably maintaining the axis center of the metering pin, so that shaking of the metering pin occurs during the operation of the damper cylinder and affects the energy absorbed and reaction force of the damper cylinder.

[0103] Next, as shown in FIG. 7 and FIG. 8a, the extension portion (420) has a cylindrical shape that is extended a predetermined length in the longitudinal direction of the stroke portion (410) from the gas chamber side end of the stroke portion (410) and is formed to have a diameter smaller than the diameter of the orifice and the stroke portion (410).

[0104] More specifically, the extension (420) is configured to include a recessed groove (421) and a catch (422).

[0105] Here, as shown in FIG. 8a, the above-mentioned recesses (421) are formed on the outer surface of the extension (420) at a predetermined distance from each other and form an area that is recessed to a predetermined depth in the direction of the center of the extension (420).

[0106] Accordingly, the damper cylinder of the present invention includes a recessed groove (421) formed on the outer surface of the extension, thereby expanding the area through which the fluid passes. This prevents friction from occurring in the fluid even after the fluid flowing into the fluid storage space through the space between the orifice and the cutting surface passes through the cutting surface area, and allows the fluid pressure to be lowered, thus providing the effect of more stably realizing the required energy absorption and reaction force performance of the damper cylinder.

[0107] In addition, as shown in FIG. 8a, the above-mentioned catch (422) is formed on the outer surface of the extension part (420) at a mutually spaced distance apart and is formed to protrude a certain height from the center of the extension part (420) toward the outer circumference so that a fastening member that is fastened to the path limiting part (430) to be described later is caught.

[0108] At this time, the above-mentioned stopper (422) is characterized by being formed between a plurality of the above-mentioned recesses (421).

[0109] Next, the path limiting portion (430) has a cylindrical shape that extends a predetermined length in the longitudinal direction of the stroke portion (410) from the gas chamber side end of the extension portion (420), and a screw thread is formed on the outer surface so that a fastening member is fastened.

[0110] More specifically, the path limiting member (430) is configured to limit the movement path of the first piston (200) by being coupled with a separate fastening member and engaging with the gas tube side hole of the orifice (210) during the return process of the damper cylinder.

[0111] At this time, the fastening member may be composed of a nut and a spacer, etc.

[0112] Accordingly, through the configuration of the aforementioned stopper (422), the fastening member connected to the path limiting part (430) is prevented from moving toward the stroke part (410) by being caught.

[0113] Next, as shown in FIG. 7, the coupling portion (440) has a cylindrical shape that is formed to extend a predetermined length in the longitudinal direction of the stroke portion (410) from the end located in the outer direction of the damper cylinder among the two ends of the stroke portion (410), and has screw threads formed on its outer surface so as to be coupled and fixed to the hydraulic tube described above.

[0114] More specifically, the coupling portion (440) is configured to secure the metering pin (400) to the hydraulic tube (300) by being coupled and fixed to the second cover (320) of the hydraulic tube (300) through the screw thread, as shown in FIG. 1 and FIG. 7.

[0116] Next, a ship insect repellent device according to an embodiment of the present invention will be described with reference to FIGS. 9 and FIGS. 10.

[0117] FIG. 9 is a drawing illustrating an example in which a ship insecticidal device including a damper cylinder according to an embodiment of the present invention is installed on a quay, and FIG. 10 is an enlarged view illustrating the ship insecticidal device shown in FIG. 9.

[0118] First, the ship insecticidal device of the present invention is characterized by being equipped to include the damper cylinder (1000) described above.

[0119] More specifically, the ship anti-buoyancy device (D) is installed on the quay wall (W) of a ship docking facility as shown in FIGS. 9 and 10, and is characterized by the damper cylinder (1000) being configured to absorb the shock generated when the ship docks.

[0120] Accordingly, the ship fender of the present invention includes the above-described damper cylinder (1000), thereby stably absorbing the impact generated when the ship docks, preventing damage caused by collision between the ship and the quay wall, and provides the effect of solving problems such as environmental pollution and quality degradation of existing fenders by replacing conventional rubber fenders.

[0122] Although the present invention has been described above with specific details such as specific components, limited embodiments, and drawings, this is provided only to aid in a more comprehensive understanding of the invention, and the invention is not limited to the above embodiments, and a person skilled in the art to which the invention belongs can make various modifications and variations from this description.

[0123] Accordingly, the scope of the present invention should not be limited to the embodiments described above, and all modifications equivalent to or equivalent to the claims set forth below, as well as the claims described below, shall be considered to fall within the scope of the concept of the present invention. Explanation of the symbols

[0124] 1000: Damper cylinder 100: Gas tube 110: Gas chamber 120: The 1st Cover 200: 1st piston 210: Orifice 220: Check valve 230: Relief valve 300: Hydraulic tube 310: Fluid chamber 320: The 2nd Cover 400: Metering pin 410: Stroke section 411: Cutting surface 420: Extension part 421: Depression 422: Stopper 430: Path restriction section 440: Joint 500: 2nd piston 600: Joint unit S: Fluid storage space D: Ship insect repellent W: Quay wall

Claims

Claim 1 A damper cylinder for absorbing an external shock using fluid friction, comprising: a gas tube (100) having a gas chamber (110) to accommodate gas inside and forming a passage of a predetermined length; a first piston (200) having an orifice (210) that is coupled and fixed to one end of the gas tube and forms a passage for fluid to be transported in the center; a hydraulic tube (300) having a fluid chamber (310) to accommodate fluid inside and forming a passage of a predetermined length to surround a part of the outer surface of the gas tube and the first piston; a metering pin (400) having a predetermined length, one end of which is coupled and fixed to the end located on the fluid chamber side among the two ends of the hydraulic tube, and inserted longitudinally into the orifice to change the frictional force of the fluid passing through the orifice according to the movement of the first piston; and a second piston (500) disposed inside the gas tube and configured to separate the gas chamber and the fluid chamber. Claim 2 A damper cylinder according to claim 1, wherein the metering pin (400) comprises a cylindrical stroke portion (410) having a cutting surface (411) of a predetermined area to change the frictional force of the fluid passing through the space between the orifice and the metering pin according to the degree of movement of the first piston and the position on the metering pin. Claim 3 In claim 2, the cutting surface (411) is formed in the longitudinal direction on one side of the outer circumference of the stroke portion, and is characterized by the area decreasing so that the cross-sectional area of ​​the stroke portion increases as it goes from one end, which is the end located on the gas chamber side among the two ends of the stroke portion, to the other end. Claim 4 A damper cylinder according to claim 2, characterized in that the cutting surface (411) is formed such that its length is equal to the length of the stroke portion. Claim 5 A damper cylinder according to claim 2, characterized in that the cutting surface (411) is formed to have a planar shape. Claim 6 In claim 2, the cutting surface (411) is formed in the longitudinal direction on one side of the outer circumferential surface of the stroke portion and is formed in a diagonal shape inclined at a predetermined angle with respect to the longitudinal side of the damper cylinder. Claim 7 In claim 2, the stroke portion (410) is characterized in that the cross-sectional area of ​​one end portion, which is the end portion located on the gas chamber side among the two ends, is formed to have a value smaller than the cross-sectional area of ​​the orifice, and the cross-sectional area of ​​the other end portion is formed to have a value corresponding to the cross-sectional area of ​​the orifice. Claim 8 In claim 2, the damper cylinder is characterized in that the stroke portion (410) is formed such that the portion of the outer surface area excluding the cutting surface has a diameter corresponding to the diameter of the orifice. Claim 9 A damper cylinder according to claim 2, wherein the metering pin (400) comprises an extension portion (420) formed to have a cylindrical shape extending a predetermined length in the longitudinal direction of the stroke portion from the gas chamber side end of the stroke portion and having a diameter smaller than the diameter of the orifice and the stroke portion. Claim 10 A damper cylinder according to claim 9, wherein the extension part (420) comprises a plurality of recessed grooves (421) formed on the outer surface of the extension part at a mutually spaced distance apart and forming an area recessed to a predetermined depth in the direction of the center of the extension part. Claim 11 In claim 9, the metering pin (400) comprises a path limiting portion (430) having a cylindrical shape formed to extend a predetermined length in the longitudinal direction of the stroke portion from the gas chamber side end of the extension portion and having a screw thread formed on its outer surface to allow a fastening member to be fastened; and the extension portion (420) comprises a plurality of catch projections (422) formed on the outer surface of the extension portion at a predetermined distance from each other and formed to protrude a predetermined height from the center of the extension portion in the outer circumference direction so as to catch a fastening member fastened to the path limiting portion. Claim 12 In claim 2, the damper cylinder is characterized by comprising: a metering pin (400) having a cylindrical shape formed to extend a predetermined length in the longitudinal direction of the stroke portion from the end located in the outer direction of the damper cylinder among the two ends of the stroke portion, and a coupling portion (440) having a screw thread formed on its outer surface to be coupled and fixed to a hydraulic tube. Claim 13 In claim 1, the damper cylinder is characterized in that a fluid storage space (S) is formed between the second piston and the first piston to store fluid discharged from the fluid chamber, and the fluid storage space (S) increases in volume as fluid flows into it when the damper cylinder is compressed, and decreases in volume as the fluid contained inside is discharged into the fluid chamber when the damper cylinder returns. Claim 14 In claim 13, the damper cylinder is characterized by including a check valve (220) which, when the first piston (200) returns to the damper cylinder, discharges the fluid contained in the fluid storage space into the fluid chamber when the pressure of the fluid storage space reaches a preset pressure. Claim 15 A damper cylinder according to claim 13, wherein the first piston (200) comprises a relief valve (230) configured to urgently discharge fluid contained in a fluid storage space into the fluid chamber when the pressure of the fluid chamber reaches a preset pressure. Claim 16 A ship anti-vibration device comprising a damper cylinder described in any one of claims 1 to 15, wherein the damper cylinder is installed on a quay wall (W) of a ship berthing facility and is configured to absorb shock generated when the ship berths.

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