Gas supply pump for marine dual-fuel engines

Abstract

To provide a gas supply pump of a vessel dual fuel engine capable of driving cylinders independently.SOLUTION: A gas supply pump comprises: a camshaft that can be driven in a rotatable manner; a plurality of cam noses spaced apart along a longitudinal direction of the camshaft, and having an eccentric shape from the center of the camshaft; a cam roller provided in close contact with each cam nose; a drive shaft and a piston provided adjacent to one side of the cam roller; and a liquefied gas compression device that pressurizes and discharges liquefied gas in accordance with the linear reciprocating motion of the piston. When the camshaft rotates, the piston is compressed when the cam nose moves in a compression direction of the piston, and when the cam nose moves in a decompression direction of the piston, the piston is decompressed. The cam roller can be selectively separated from the cam nose, and when the cam roller and cam nose are separated, a rotational driving force of the cam nose is not transmitted to the piston.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a gas supply pump for a marine dual fuel engine, and more particularly, to a gas supply pump for a marine dual fuel engine capable of independently driving cylinders.

Background Art

[0002] A dual fuel engine adopted in a ship uses natural gas or heavy oil as fuel. An FGSS (Fuel Gas Supply System) is a device that supplies liquefied gas to a dual fuel engine. Therefore, in a dual fuel engine with a high-pressure injection system, a high-pressure pump for FGSS for high-pressure gas supply is required to be provided as an essential component. For example, a high-pressure pump for FGSS as described in Korean Patent Publication No. 2018-0093403 generally has a plurality of cylinders provided on one crankshaft, and the connecting rods and pistons attached to each cylinder reciprocate within the cylinder to drive and compress / discharge high-pressure fuel. However, in the case of such a high-pressure pump, the connecting rods and pistons are structurally connected to the crankshaft, and the operations of the connecting rods and pistons attached to the cylinders cannot be selectively controlled. Therefore, in order to prepare for failures or inspections of the high-pressure pump, an additional high-pressure pump must be installed.

[0003]

[0004] Instead, the installation of two high-pressure pumps will incur additional costs. [Overview of the project] [Problems that the invention aims to solve]

[0005] The present invention was made to solve the above-mentioned problems, and the cylinder The objective is to provide a gas supply pump for a ship's dual-fuel engine that can be driven independently. There is. [Means for solving the problem]

[0006] To achieve the above objective, the gas supply pump for a ship's dual-fuel engine according to the present invention is , a camshaft capable of rotational drive, with a constant interval along the longitudinal direction of the camshaft It is equipped with multiple cam noses that are eccentric in shape from the center of the camshaft, each of which A cam roller is fitted in close contact with the nose, and is fitted adjacent to one side of the cam roller. The drive shaft and piston, along with the linear reciprocating motion of the piston, pressurize and discharge liquefied gas. It comprises a liquefied gas compressor, and when the camshaft rotates, the cam nose moves against the piston. When moving in the compression direction, the piston is compressed, and the cam nose moves in the direction of piston decompression. Then the compression of the piston is released, and the cam roller can be selectively separated from the cam nose. Yes, when the cam roller and cam nose are separated, the rotational driving force of the cam nose is transmitted to the piston. It is characterized by not being able to do so.

[0007] Multiple drive shafts are arranged in a perpendicular direction on a single camshaft, and the camshaft A cam roller is provided between the cam nose and the drive shaft.

[0008] The rotation center of the cam nose is the same as the rotation center of the camshaft, and the radius of the cam nose is C The radius of rotation of the cam nose is smaller than the radius of the camshaft, and the radius of rotation of the cam nose corresponds to the radius of rotation of the camshaft. When the camshaft rotates, the cam roller, which is in close contact with the cam nose, moves in a straight line back and forth within a certain distance. To move.

[0009] The rotation of the camshaft caused the cam nose to be positioned at a 90-degree angle relative to the vertical. At that time, the cam roller moves in the compression direction of the piston, and the rotation of the camshaft moves the cam nose When the cam roller is positioned at a 270-degree angle, it moves in the direction of decompression of the piston.

[0010] An integrated connecting member is further provided to connect the cam roller and the drive shaft in an integrated manner, A cam roller is housed at one end of the integrated connecting member, and a drive shaft is attached to the other end. A compression spring, positioned to surround the camshaft, is fixed to the inside of the integrated connecting member, and the camshaft During rotation, the cam roller and drive shaft, which are in close contact with the cam nose, and the integrated connecting member are both in a straight line. It moves back and forth.

[0011] This is the part where the drive shaft and piston are connected, providing a certain amount of space on one end of the drive shaft. It is provided with a first housing section and a second housing section, the first housing section is located in the direction inward of the drive shaft, The second housing is provided facing outward from the drive shaft, and the first housing has a moment of inertia A buffer is provided, and one exposed surface of the inertia moment buffer is in close contact with the piston. .

[0012] One surface of the inertia moment buffer member that is in close contact with the piston has a convex radius of curvature. When the moment of inertia of the camshaft is applied to the drive shaft, the moment of inertia applied to the drive shaft The torque is dispersed by the convex surface of the moment of inertia buffer member.

[0013] The diameter of the second receiving portion is larger than the diameter of the first receiving portion, and the diameter of the first receiving portion corresponds to the diameter of the piston. A stopper is fitted into the space between the second receiving portion and the piston, and the stopper is provided in close contact with the inner diameters of the piston and the second receiving portion to prevent the piston from rotating.

[0014] A clamp for protecting the coupling portion may be provided at the coupling portion between the drive shaft and the piston.

[0015] The liquefied gas compression device includes a liquefied gas supply flow path for supplying liquefied gas to be compressed to an intake valve, an intake valve for inhaling liquefied gas from the liquefied gas supply flow path and supplying the inhaled liquefied gas to the discharge valve side when the pressure of the piston is applied, and a discharge valve for discharging the liquefied gas supplied from the intake valve in a pressurized state.

[0016] One end of the liquefied gas supply flow path is connected to a liquefied gas supply port provided on one side of a gas supply pump, and the other end is connected to a liquefied gas intake port provided on one side of the intake valve. The liquefied gas to be compressed passes through the liquefied gas supply port and the liquefied gas supply flow path and is supplied to the internal space of the intake valve through the liquefied gas intake port.

[0017] An opening and closing member for selectively opening and closing the liquefied gas intake port is provided around the intake valve. The opening and closing member is connected to a spring member provided around the lower end side of the intake valve and can perform a linear reciprocating motion as the spring member compresses and restores. When the opening and closing member moves in the compression direction due to the compression of the spring member, the liquefied gas intake port is opened, and when the opening and closing member moves in the restoration direction as the spring member restores. the liquefied gas intake port is closed.​​​​​​​​​​​ The liquefied gas inlet is shut off, and the opening / closing member is shutting off the liquefied gas inlet, while the liquefied gas supply is in place. When liquefied gas is supplied through the flow path, the supply pressure of the liquefied gas causes the opening and closing member to move against the spring member. As it moves in the compression direction, the liquefied gas intake port opens, allowing the liquefied gas to enter the intake valve. It is supplied to the space.

[0018] The discharge valve is located inside the discharge chamber, and a spring member is provided on the lower end side of the discharge valve. The compression and recovery of the spring member enables linear reciprocating motion of the discharge valve, and the discharge chamber An auxiliary chamber with a certain amount of space around the upper end is provided, and the auxiliary chamber and the discharge valve A discharge inlet pipe is provided in between, and the liquefied gas discharged from the intake valve enters the auxiliary chamber and discharge It is supplied to the discharge valve after passing through the inlet pipe in sequence.

[0019] The discharge valve is positioned to block the intake valve discharge pipe when the spring member returns to its original position. As the spring member moves in the compression direction, a space is formed on the upper end side of the discharge chamber. The intake valve discharge pipe is opened, and the movement of the discharge valve creates space on the upper side of the discharge chamber. Once formed, the upper end space of the discharge chamber is spatially connected to the intake valve discharge pipe. The liquefied gas, which is connected to the auxiliary chamber and discharged through the suction valve discharge pipe, is discharged through the discharge chamber. Through the upper end space of the valve, and via the auxiliary chamber and discharge inlet pipe, into the internal space of the discharge chamber. It will be supplied.

[0020] When liquefied gas is discharged through the intake valve, the operating pressure of the piston is such that the liquefied gas Because the supply pressure of the liquefied gas supplied to the supply channel is greater than that of the liquefied gas inlet, the opening and closing member... Therefore, it is blocked.

[0021] The integrated connecting member is protected on the outside of the integrated connecting member and also prevents the integrated connecting member from moving. The cam roller drive shaft case is further equipped, One side of the pipe is equipped with a cutoff bolt insertion port through which a cutoff bolt is inserted, and the integrated connection Cutoff bolt insertion: A cutoff bolt can be inserted to a certain depth on one side of the connecting member. A groove is provided, and the cutoff bolt is cut off when inserted through the cutoff bolt insertion port. The process of the bolt being inserted into the cutoff bolt insertion groove involves the cam nose and cam roller Separation is induced.

[0022] The center of the cutoff bolt insertion opening and the center of the cutoff bolt insertion groove are spaced apart. Based on the assumption that the piston is positioned perpendicular to the camshaft, the cutoff bolt The center of the insertion groove is located slightly lower than the center of the cutoff bolt insertion opening, The bolt insertion groove has a tapered shape, where the radius decreases as the depth increases, and the tapered shape The radius at the entrance and the radius at the bottom of the cutoff bolt insertion groove have a radius difference of only "d".

[0023] The cutoff bolt, having passed through the cutoff bolt insertion opening, is inserted into the cutoff bolt insertion groove. During the insertion process, the cutoff bolt is positioned on the side of the tapered cutoff bolt insertion groove. It makes contact and moves along the side of the cutoff bolt insertion groove towards the inside of the cutoff bolt insertion groove. As the cutoff bolt moves inward into the cutoff bolt insertion groove, the cutoff bolt insertion The integrated connecting member with grooves moves upward, and the cam roller separates from the cam nose. It can be done.

[0024] When one end of the cutoff bolt contacts the bottom surface of the cutoff bolt insertion groove, the integrated connecting part The material is positioned upward by a length of "d", which is the difference in radius between the entrance side and the bottom side of the cutoff bolt insertion groove. It moves, and the cam roller and cam nose are separated by a length of "d".

[0025] The integrated connecting member is protected on the outside of the integrated connecting member and also prevents the integrated connecting member from moving. The cam roller drive shaft case is further equipped, One side of the cutoff pin guide member is provided with a hollow cylindrical shape, and the cutoff pin A cutoff pin is inserted into the guide member so as to be able to move up and down, and the cutoff pin guide A cutoff pin guide groove is provided on one side of the component, and the cutoff pin guide groove is spatially It is divided into vertical guide grooves and horizontal guide grooves that are connected to each other, and the vertical guide grooves are along the vertical line It extends from the first point to the second point, and the horizontal guide groove is at the second point of the vertical guide groove. It extends to a third point in the horizontal direction, and on one side of the cutoff pin there is a cutoff pin Guide pins are provided, and the cutoff pin guide pin is located within the cutoff pin guide groove. The cutoff pin guide pin moves vertically from the first point to the second point in the cutoff pin guide groove. When moved, the cutoff pin descends by the corresponding distance, and the cutoff pin guide pin cuts off. When the pin guide groove moves horizontally from the second point to the third point, the cutoff pin moves from the second point to the third point. It rotates by the angle between the three points, and the bottom surface of the cutoff pin has a radius smaller than the cutoff pin. It is equipped with a cylindrical cam roller separation projection having a cut in the center of the cam roller separation projection. The off-pin has an eccentric shape from the center of the circle, and the cutoff pin guide pin is the cutoff pin gar When moving horizontally from the second point to the third point of the groove, the bottom surface of the cutoff pin is The Murola septum rotates by a certain angle.

[0026] A cutoff pin is inserted through one side of the cam roller drive shaft case. A passage is provided, and the integrated connecting member corresponding to the cutoff pin insertion port has a cam roller separation gas When a groove is provided and the cutoff pin guide pin is positioned at the second point, the cutoff pin The cam roller separation projection at the lower end is located within the cam roller separation guide groove of the integrated connecting member, Within the cam roller separation guide groove, the cam roller separation projection is in a state where it does not come into contact with the integrated connecting member. When the cutoff pin projection is moved from the second point to the third point of the cutoff pin guide groove, As the cutoff pin rotates horizontally, the cam roller separation projection rotates horizontally, and the integrated connecting member... By physically pushing and moving, the integrated connecting member is moved by the cam roller separation projection. The cam roller and the cam nose are separated.

[0027] Coupling case provided at the joint between the drive shaft and the piston, coupling case The drive shaft is connected to and fixed in the inner space of the case, or both the drive shaft and the piston are connected. Rack members connected and fixed to one side, and tooth-shaped racks provided on the outer surface of the rack members. A pinion that meshes with the pinion, and a drive force that is provided on the other side of the pinion. The system further includes a pinion guide member that transmits power, and the pinion guide member moves downward. When this is done, the pinion rotates counterclockwise, and the counterclockwise rotation of the pinion causes the dry The rack member connected to the shaft moves upward, and the upward movement of the rack member causes the cam to move. The s and the cam roller are separated.

[0028] The pinion guide member may be reciprocated by a hydraulic cylinder.

[0029] A device is provided between the drive shaft and the piston that selectively transfers the driving force of the drive shaft to the piston. The system further includes a pressure chamber for applying pressure, and the amount of lubricating oil in the pressure chamber is adjusted. This allows for the control of the amount of liquefied gas discharged from the liquefied gas compressor.

[0030] The first surface of the pressure chamber is in contact with the drive shaft, and the second surface of the pressure chamber is in contact with the piston. Furthermore, the first surface of the pressure chamber is movable by the driving force of the drive shaft, and the movement of the first surface The volume of the pressure chamber can be changed accordingly.

[0031] With the pressure chamber filled with lubricating oil, the driving force of the drive shaft is applied to the first pressure chamber. When applied to the surface, the driving force of the drive shaft is transmitted to the piston via the lubricating oil filling the pressure chamber. Pressure is applied to the piston, and the resulting pressure is transmitted to the liquefied gas compressor, causing the liquefied gas to be discharged. .

[0032] When no lubricating oil is present in the pressure chamber, the driving force of the drive shaft is applied to the first surface of the pressure chamber. When pressure is applied, the first surface of the pressure chamber moves towards the second surface because the pressure chamber is an empty space. As the camshaft moves, the scroll length of the drive shaft accompanying the drive of the camshaft is between the first and second surfaces of the pressure chamber. If the distance between the faces is smaller, the driving force of the drive shaft is not transmitted to the second surface of the pressure chamber. Therefore, liquefied gas is not discharged by the liquefied gas compressor.

[0033] As the pressure chamber is filled with lubricating oil, the lubricating oil in the pressure chamber flows through the lubricating oil supply path. When the drive force of the drive shaft is applied to the first surface of the pressure chamber in a state where discharge is possible, pressure As the lubricating oil is discharged from the force chamber, the first surface moves by the amount of lubricating oil that was discharged, and the drive Of the total stroke length Ds of the hub shaft, the portion corresponding to the discharge of lubricating oil from the pressure chamber is driven by the piston. When no power is applied, the piston will remain wet in the pressure chamber for the remainder of its total stroke length Ds. The movement will be limited to the scroll length minus the length of the lubricant discharged.

[0034] A lubricant that allows for the supply of lubricant to the pressure chamber or the discharge of lubricant from the pressure chamber. The lubricating oil supply channel, the amount of lubricating oil supplied to the pressure chamber, and the amount of lubricating oil discharged from the pressure chamber. The system may further include a lubricating oil supply device for setting the amount of lubricating oil. [Effects of the Invention]

[0035] The gas supply pump for a ship's dual-fuel engine according to the present invention has the following effects:

[0036] Each cylinder in the high-pressure pump can be independently controlled. This allows for the installation of an extra pump in case a specific cylinder malfunctions or requires inspection. There is no need to install it.

[0037] Furthermore, the moment of inertia associated with the rotational motion of the camshaft exerts on the drive shaft and piston. The impact can be minimized, and the liquefied gas is composed of an intake valve and a discharge valve. The compression device effectively compresses the liquefied gas and prevents backflow of the liquefied gas. can.

[0038] In addition, the optimal sealing structure in the area where the piston moves allows for liquefaction of gases. This prevents cavitation caused by the inflow of fluid and also prevents overheating of the internal space of the cylinder. It can be effectively suppressed. [Brief explanation of the drawing]

[0039] [Figure 1] This is a perspective view of a gas supply pump for a ship's dual-fuel engine according to one embodiment of the present invention. [Figure 2] This is a cross-sectional view along the line A-A' in Figure 1. [Figure 3a] This is a reference diagram to explain the linear reciprocating motion of the cam roller in relation to the position of the cam nose. [Figure 3b] This is a reference diagram to explain the linear reciprocating motion of the cam roller in relation to the position of the cam nose. [Figure 4] This is a reference diagram showing the connection point between the drive shaft and the piston. [Figure 5] This is a perspective view showing the connection point between the drive shaft and the piston. [Figure 6] This is a diagram showing the configuration of a liquefied gas compressor. [Figure 7] This is a perspective view of a liquefied gas compressor. [Figure 8] This is a reference diagram showing the state in which the opening / closing member of the intake valve is open. [Figure 9a] This is a reference diagram to explain the operation of the discharge valve. [Figure 9b] This is a reference diagram to explain the operation of the discharge valve. [Figure 10] This is a reference diagram showing the sealing structure on the cylinder side and the sealing structure on the rod side. [Figure 11a] This is a perspective view of the sealing structure on the cylinder side. [Figure 11b] This is a perspective view of the sealing structure on the cylinder side. [Figure 12] This is a perspective view of the sealing structure on the rod side. [Figure 13] This is a reference diagram illustrating the separation between the cam roller and the cam nose using the cutoff bolt in the first embodiment. [Figure 14] This is a reference diagram illustrating the separation between the cam roller and the cam nose using the cutoff bolt in the first embodiment. [Figure 15] This is a reference diagram illustrating the separation between the cam roller and the cam nose using the cutoff pin in the second embodiment. [Figure 16] This is a reference diagram illustrating the separation between the cam roller and the cam nose using the cutoff pin in the second embodiment. [Figure 17a] This is a reference diagram showing the separation operation between the cam roller and the cam nose according to the second embodiment. [Figure 17b] This is a reference diagram showing the separation operation between the cam roller and the cam nose according to the second embodiment. [Figure 17c] This is a reference diagram showing the separation operation between the cam roller and the cam nose according to the second embodiment. [Figure 18] This is a reference diagram illustrating the separation between the cam roller and the cam nose using the rack and pinion of the third embodiment. [Figure 19] This is a diagram illustrating the configuration of a gas supply pump with a pressure chamber. [Figure 20a] This is a reference diagram illustrating a method for separating the drive shaft and piston using a pressure chamber. [Figure 20b] This is a reference diagram illustrating a method for separating the drive shaft and piston using a pressure chamber. [Figure 20c] This is a reference diagram illustrating a method for separating the drive shaft and piston using a pressure chamber. [Figure 21] This is a diagram of the gas supply pump system. [Figure 22] This graph shows the pulsation of discharge pressure in proportion to the number of pistons. [Figure 23] This graph shows the pulsation of discharge pressure in accordance with the phase of the cam nose. [Modes for carrying out the invention]

[0040] This invention presents technology relating to a high-pressure pump capable of independently driving each cylinder. The high-pressure pump in this case is responsible for supplying high-pressure gas to the dual-fuel engine. FGSS (fuel gas supply system) supplies high-pressure gas to the fuel engine. It could be adopted by em.

[0041] A high-pressure pump has multiple cylinders, and high-pressure gas is injected through each cylinder. Each cylinder needs to be prepared for failure or inspection, and if a particular cylinder fails... If inspection of a particular cylinder is necessary, measures will be taken only for that cylinder. It would be efficient to ensure that the remaining cylinders operate normally. However, As mentioned in the "Background Technology" section, in the case of conventional high-pressure pumps, one crank The shaft is equipped with multiple cylinders, and each cylinder is fitted with a connecting rod and a piston. Due to its structure, independent drive control for each cylinder is impossible. .

[0042] This invention enables independent drive control for each cylinder of a high-pressure pump. This invention presents a useful technology. More specifically, this invention provides a camshaft equipped with multiple cylinders, We present a technology that allows for the selective control of the drive of each cylinder.

[0043] In addition, the present invention relates to the moment of inertia of the camshaft to the drive shaft and piston. This paper presents an optimal coupling structure for the drive shaft and piston that minimizes the impact of the connection. Furthermore, the present invention relates to a liquefied gas compressor comprising an intake valve and a discharge valve. We present a technology that can effectively compress liquefied gas while preventing its backflow. Furthermore, the present invention provides an optimal sealing structure in the region where the piston moves. This prevents cavitation caused by the inflow of liquefied gas and also prevents the internal cavity of the cylinder from We present a technology that can effectively suppress overheating during the process.

[0044] The following describes a gas supply port for a marine dual-fuel engine according to one embodiment of the present invention, with reference to the drawings. I will now explain the pump in detail.

[0045] Referring to Figures 1 and 2, the gas of a ship dual-fuel engine according to one embodiment of the present invention The supply pump consists of a camshaft, cam roller 30, drive shaft 40, piston 50 and liquefaction It includes a gas compressor.

[0046] The rotational motion of the camshaft 10 induces the linear reciprocating motion of the drive shaft 40 and the piston 50. Then, the pressure due to the linear reciprocating motion of the piston 50 is applied to the liquefied gas compressor, and the liquefied gas pressure This system uses a compression device to discharge liquefied gas at high pressure.

[0047] The camshaft 10 is rotated by the power of the drive means, and the camshaft 10 Multiple cam noses (cam n) are spaced at regular intervals along the longitudinal direction of the camshaft 10. A cam nose 20 is provided. A drive shaft 40 is provided for each cam nose 20. The drive shaft 40 is positioned perpendicular to the longitudinal direction of the camshaft 10. Cam nose 2 A cam roller 30 is provided between the 0 and the drive shaft 40. Therefore, one cam... Multiple drive shafts 40 are arranged in a perpendicular direction on the shaft 10, and the camshaft 10 The cam roller 30 is positioned between the cam nose 20 and the drive shaft 40.

[0048] The rotational motion of the camshaft 10 induces the linear reciprocating motion of the drive shaft 40, which in turn induces the camshaft This is made possible by the cam nose 20 of the shaft 10.

[0049] The rotation center of the cam nose 20 is the same as the rotation center of the camshaft 10, and the cam nose 2 The radius of 0 is smaller than the radius of camshaft 10, and the turning radius of cam nose 20 is smaller than the radius of camshaft It is designed to accommodate the turning radius of the T10.

[0050] On one side of each cam nose 20, there is a cam roller 30 that is in close contact with the cam nose 20. It is equipped with the following: The rotation center of the cam nose 20 is eccentric from the axis of the camshaft, Because the radius of the cam nose 20 is smaller than the radius of the camshaft 10, the camshaft 1 When the 0 rotates, the cam roller 30 located on one side of the cam nose 20 moves within a certain distance. It will begin to move back and forth in a straight line.

[0051] Furthermore, the drive shaft 40 and piston 50 are connected adjacent to one side of the cam roller 30. In this process, the drive shaft 40 and piston 50 also move together during the linear reciprocating motion of the cam roller 30. It moves in a straight line back and forth motion.

[0052] Specifically, as shown in Figure 3a, the rotation of the camshaft 10 causes the cam nose 20 When it is positioned at a 90-degree angle with respect to the vertical direction, the cam roller 30 presses against the piston 50. It moves in the contraction direction, and as shown in Figure 3b, the rotation of the camshaft 10 causes the cam nose When 20 is positioned at a 270-degree angle, the cam roller 30 is in the direction of decompression of the piston 50. It moves to this position. In this way, when the camshaft 10 rotates, the cam roller 30 moves within a certain distance. The cam roller 30 moves in a straight line, and the distance over which it moves in a straight line is such that the cam nose 20 is at a 90-degree angle. This corresponds to the position between when it is located at this angle and when the cam nose 20 is at a 270-degree angle. Then, when the cam nose 20 is positioned at an angle of 270 degrees, the cam roller 30 is relative to the piston 50. Movement in the compression release direction is made possible by the compression spring 120, which will be described later. In the specification, the compression direction of the piston 50 refers to the movement of the piston 50 inward of the cylinder 80. This means the direction in which the piston 50 is released from compression, and the direction in which the piston 50 is released from compression is the direction in which the piston 50 is released from the cylinder 80. It means the direction of movement.

[0053] A drive shaft 40 is provided at one end of the cam roller 30, and around the drive shaft 40 A compression spring 120 is provided. When the cam roller 30 moves in the compression direction of the piston 50, the compression When the compression spring 120 is compressed, the cam roller 30 moves in the direction of decompression of the piston 50, The compressed spring 120 is restored to its original state.

[0054] The cam roller 30 and the drive shaft 40 are connected as a single unit by an integrated connecting member 110. One end of the compression spring 120 is fixed to the integrated connecting member 110. Specifically, the integrated The connecting member 110 has a hollow shape, and a cam roller 30 is attached to one end of the integrated connecting member 110. It is housed within, and a drive shaft 40 is attached to the other end, and is provided in a manner that surrounds the drive shaft 40. The compression spring 120 is fixed to the inside of the integrated connecting member 110.

[0055] In this way, the cam roller 30, drive shaft 40, and integrated connecting member 110 are connected as a single unit. Because of the connected structure, the cam nose 20 is in close contact with the camshaft 10 when it rotates. Not only the roller 30, but also the drive shaft 40 and the integrated connecting member 110 all move in a linear reciprocating motion. As a result of these movements, the compression spring 120 is compressed or restored to its original state. They might do that.

[0056] On the other hand, the cam roller drive shaft case 130 is provided on the outside of the integrated connecting member 110. The cam roller drive shaft case 130 consists of an integrated connecting member 110 and a compression spring 12 This protects the 0 from the external environment and prevents the movement of the integrated connecting member 110 and the compression spring 120. It plays the role of iding.

[0057] The drive shaft 40 and the piston 50 are connected in the following configuration.

[0058] Since the piston 50 is a device designed to reciprocate linearly within the cylinder 80, The direction of the force applied to the piston 50 must precisely coincide with the linear reciprocating motion of the piston 50. There is a condition where the direction of the force applied to the piston 50 coincides with the direction of the linear reciprocating motion of the piston 50. If not, this means that a portion of the force applied to the piston 50 will be lost, and This means that the linear reciprocating motion of piston 50 is being obstructed.

[0059] On the other hand, the force applied to the piston 50 is the linear reciprocating motion of the drive shaft 40, and the drive The linear reciprocating motion of shaft 40 is induced by the rotational motion of camshaft 10. However, the cam In the process in which the rotational motion of shaft 10 is converted into the linear reciprocating motion of drive shaft 40, the camshaft The moment of inertia of part 10 acts on the drive shaft 40, hindering the linear reciprocating motion of the drive shaft 40. It can be harmful. Moment of inertia refers to the rotational inertia associated with the reciprocating motion of a cam or roller. Furthermore, in order to prevent such rotational inertia from affecting the reciprocating motion of the piston, as described below... An inertia moment buffering member 230 is provided to achieve this.

[0060] The coupling structure between the drive shaft 40 and the piston 50 according to the present invention is the camshaft 10 described above. It is designed taking into account the moment of inertia action of the camshaft 10. To minimize the effect of the moment of inertia on the drive shaft 40, the drive shaft 40 and the pin are... Stone 50 has the optimal bonding structure.

[0061] Specifically, referring to Figures 4 and 5, a certain space is provided on one end side of the drive shaft 40. A first storage section 210 and a second storage section 220 are provided. The first storage section 210 is for the drive shaft 4 Located in the inward direction of 0, the second housing portion 220 is provided facing outward from the drive shaft 40. The diameter of the second storage section 220 is larger than the diameter of the first storage section 210. The diameter corresponds to the diameter of the 50mm piston.

[0062] The first storage portion 210 is provided with an inertia moment buffering member 230. One exposed surface of the cushioning member 230 is in close contact with the piston 50. One surface of the inertia moment buffering member 230 is a gently convex shape with a large radius of curvature. Eggplant.

[0063] One side of the inertia moment buffer member 230 that is in close contact with the piston 50 has a large radius of curvature. The reason for designing it with a gently convex shape is the moment of inertia of the camshaft 10 on the drive shaft 40. When force is applied, the moment of inertia applied to the drive shaft 40 acts on the piston 50. This is to minimize the amount of inertia applied to the drive shaft 40. The pressure is dispersed by the convex surface of the pressure buffer member 230 and applied to the piston 50, thereby reducing the pressure on the piston. The moment of inertia applied to 50 tons is minimized.

[0064] A stopper 240 is fitted into the space between the second housing 220 and the piston 50. The stopper 240 is fitted in close contact with the inner diameter of the piston 50 and the second housing 220. It serves to prevent the 50-ton load from rotating.

[0065] Furthermore, the joint between the drive shaft 40 and the piston 50 is protected by a mechanism to protect the joint. A clamp 250 may be provided. That is, two clamp 250 members are bolted together with bolts or the like. The fastening mechanism protects the connection between the drive shaft 40 and the piston 50 from the external environment. ru.

[0066] The piston 50 moves in a linear reciprocating motion within the cylinder 80, and the linear reciprocating motion of the piston 50 Consequently, pressure is applied to the liquefied gas compressor. The liquefied gas compressor is operated by a piston 50. This device uses the applied pressure to discharge liquefied gas under high pressure.

[0067] As shown in Figures 6 and 7, the liquefied gas compressor has a liquefied gas supply channel 320 and an intake channel. It comprises a valve 60 and a discharge valve 70.

[0068] The liquefied gas supply channel 320 is a channel that supplies liquefied gas to the intake valve 60. One end of the supply channel 320 is connected to a liquefied gas supply port 310 located on one side of the gas supply pump. The two ends are connected, and the other end is connected to a liquefied gas inlet 62 provided on one side of the intake valve 60. The liquefied gas to be compressed passes through the liquefied gas supply port 310 and the liquefied gas supply channel 320. It is supplied to the internal space of the intake valve 60 via the gas intake port 62. The connected liquefied gas supply passage 320 surrounds the intake valve 60, and the housing of the intake valve 60 It is formed in a ring.

[0069] The intake valve 60 is surrounded by an opening / closing member 61 that selectively opens and closes the liquefied gas intake port 62. The opening / closing member 61 is connected to a spring member 63 provided around the lower end of the intake valve 60. The spring member 63 is connected and can perform linear reciprocating motion as it is compressed and restored. When the opening / closing member 61 moves in the compression direction, the liquefied gas intake port 62 is opened, and the spring member When the opening / closing member 61 moves in the restoring direction due to the restoration of 63, the liquefied gas intake port 62 is shut off. This is the method. The compression and restoration of the spring member 63 is performed by the force acting on the opening / closing member 61. .

[0070] With the opening / closing member 61 blocking the liquefied gas intake port 62, the liquefied gas supply path 320 is used. When liquefied gas is supplied, the piston 50 retracts as the pressure inside the intake valve 60 increases. When the force becomes less than the supply pressure of the liquefied gas, the opening / closing member 61 moves in the compression direction of the spring member 63. As it moves, the liquefied gas intake port 62 opens, and the liquefied gas enters the intake valve 60 It is supplied into space. In this manner, the liquid is supplied from the liquefied gas supply channel 320 to the suction valve 60. A supply of fermentation gas is provided.

[0071] The liquefied gas from the intake valve 60 is discharged under high pressure through the discharge valve 70, and the intake valve The liquefied gas from valve 60 is supplied to the discharge valve 70 via the suction valve discharge pipe 60a.

[0072] The discharge valve 70 is located inside the discharge chamber 71. Within 1, it moves in a linear reciprocating motion over a certain distance by applying pressure. Also, on the lower end side of the discharge valve 70 The intake valve 60 is equipped with a spring member 75, and the compression and recovery of the spring member 75 This enables linear reciprocating motion of the discharge valve 70. The compression and recovery of the spring member 75 is controlled by the discharge valve 7 Determined by the force acting on 0, the force acting on the discharge valve 70 is the pressure on the piston 50. Therefore, this is the pressure of the liquefied gas discharged from the intake valve 60.

[0073] The discharge valve 70 is positioned to block the intake valve discharge pipe 60a when the spring member 75 returns to its original position. Place it. When the discharge valve 70 moves in the compression direction of the spring member 75, the discharge chamber 71 A space is formed at the end and the suction valve discharge pipe 60a is opened. An auxiliary chamber 72 of a certain size is provided around the upper end of the chamber 71, and the auxiliary chamber 72 is connected to the space formed on the upper end side of the discharge chamber 71 and the discharge valve 7 It is also connected to the discharge inlet pipe 73 located on one side of 0.

[0074] In other words, the movement of the discharge valve 70 creates a space on the upper end side of the discharge chamber 71. Then, the space is spatially connected to the intake valve discharge pipe 60a and the auxiliary chamber 7 It is connected to 2. Also, the auxiliary chamber 72 is connected to the discharge inlet pipe 73. The liquefied gas discharged via the suction valve discharge pipe 60a is directed to the space 7 at the upper end of the discharge chamber. It is supplied through 4 to the internal space of the discharge chamber 71 via the auxiliary chamber 72.

[0075] With the intake valve 60 filled with liquefied gas (see Figure 9a), a piston is inserted into the intake valve 60. When a pressure of 50 tons is applied, the liquefied gas from the intake valve 60 is released through the intake valve discharge pipe 60a. It is then discharged, and at this time, the pressure of the liquefied gas discharged through the suction valve discharge pipe 60a is Pressure is applied to the discharge valve 70. When pressure is applied to the discharge valve 70, the discharge valve Bu 70 moves in the compression direction of the spring member 75, thereby causing the discharge chamber 7 A space 74 is formed on the upper end side of 1, and liquefied gas is discharged via the intake valve discharge pipe 60a. It is moved to the auxiliary chamber 72 via the space 74 at the upper end of the discharge chamber 71 (Figure 9b). (See reference). Because the auxiliary chamber 72 is connected to the discharge suction pipe, the auxiliary chamber 72 The liquefied gas inside is supplied to the internal space of the discharge suction pipe, and finally the pressurized liquefied gas It is discharged to the outside via the discharge valve 70.

[0076] As the piston 50 moves in the compression release direction, the liquefied gas in the intake valve 60 enters the intake valve When discharge stops through the discharge pipe 60a, the discharge chamber 71 is restored by the return of the spring member 75. Then it returns to its original state, and the space 74 on the upper end side of the discharge chamber 71 disappears, and discharge Chamber 71 will block the intake valve discharge pipe 60a.

[0077] The liquefied gas discharged from the suction valve discharge pipe 60a enters the space 7 at the upper end of the discharge chamber 71. Since it is supplied to the discharge valve 70 via 4 and the auxiliary chamber 72, the discharge valve Even if the liquefied gas at the rear end of b70 flows back, the upper end of the auxiliary chamber 72 and discharge chamber 71 The space 74 prevents backflow towards the intake valve 60.

[0078] Furthermore, when liquefied gas is discharged through the intake valve discharge pipe 60a, the piston The operating pressure of 50 is far greater than the supply pressure of the liquefied gas supplied to the liquefied gas supply channel 320. Due to its size, the liquefied gas intake port 62 is blocked by the opening / closing member 61.

[0079] As explained above, the pressure of the piston 50, which moves in a linear reciprocating motion inside the cylinder 80, is liquefied gas The gas is applied to the pressure device and transmitted through the suction valve 60 and discharge valve 70 of the liquefied gas pressure device. The liquefied gas is discharged under high pressure.

[0080] On the other hand, in the process of pressurizing and discharging liquefied gas by a liquefied gas pressure device, the liquefied gas pressure The liquefied gas of the device enters the cylinder 80 through the tiny gap between the piston 50 and the cylinder 80. It may flow into the space. If the inflow of such liquefied gas is blocked by sealing, Discharge is performed without leakage of liquefied gas, increasing pump efficiency. However, due to sealing... When the inflow of liquefied gas is blocked, the liquefied gas that has entered the internal space of cylinder 80 will be blocked. During the linear reciprocating motion of the 50, cavitation occurs due to frictional heat. This induces formation and prevents mechanical damage to the piston 50, cylinder 80, and drive shaft 40, etc. It can bring about results.

[0081] Therefore, to completely block the inflow of liquefied gas into the internal space of cylinder 80, or to partially Each approach has its pros and cons.

[0082] This invention relates to a sealing of a piston 50 that blocks or allows the inflow of liquefied gas. The ng) structure allows for increased pump efficiency and liquefied gas inflow We propose a method to prevent cavitation from occurring.

[0083] The sealing structure of piston 50 can be broadly divided into the cylinder side and the rod side. The sealing structure on the cylinder side is a sealing structure provided on the piston 50 that is installed in the cylinder. The construction is such that the sealing structure on the rod side is the piston portion that is not fitted into the cylinder 80, that is, This is a sealing structure provided on the rod.

[0084] The present invention provides a sealing structure on the cylinder side that allows a certain portion of liquefied gas to flow in. The sealing structure on the rod side is designed to prevent the inflow of liquefied gas and other substances. Furthermore, the present invention relates to the sealing structure on the cylinder side and the sealing structure on the rod side. We propose a configuration that prevents the inflow of liquefied gas and other substances to both sides.

[0085] In the case of a sealing structure on the cylinder side, as shown in Figures 10 and 11a, cylinder 8 A spring member housing groove 51a and guide rail are spatially connected around the piston portion that is inserted into 0. A spring member storage groove 51b is provided. The spring member storage groove 51a and the guide ring storage groove 51b are multiple It has a stepped configuration, and the width of the guide ring housing groove 51b is designed to be wider than the width of the spring member housing groove 51a. A hollow, elastic spring member 410 is fitted into the spring member housing groove 51a. In the guide ring housing groove 51b adjacent to the spring member housing groove 51a, there is a strip-shaped plate-shaped guide ring The spring member 420 is installed. The width of the spring member 410 that fits into the spring member housing groove 51a is the guide It is narrower than the width of the guide ring 420 that fits into the drum housing groove.

[0086] The guide ring 420 controls the movement of the piston 50 during the reciprocating motion of the piston within the cylinder. It serves as a guide and is in contact with the guide ring 420 and is housed in the spring member housing groove 51a. The component 410 plays a role in buffering the force applied to the guide ring when the piston 50 moves. The spring member 410 ensures that the position of the guide ring 420 remains constant. This allows for stable guidance of the movement of piston 50.

[0087] The combination of the guide ring 420 and the spring member 410 is along the longitudinal direction of the piston portion. These are arranged repeatedly at regular intervals. In one embodiment, the guide ring 420 and The combination of spring members 410 may be repeated five times.

[0088] The cylinder side is composed of the guide ring 420 and spring member 410 as described above. The ring structure is designed to allow a certain portion of liquefied gas to flow in, and such a design is used in the cylinder This configuration effectively suppresses overheating of the internal space of the DA80.

[0089] The sealing structure on the cylinder side is designed to allow the inflow of liquefied gas, as described above. Alternatively, it is possible to design a structure that does not allow the inflow of liquefied gas. The sealing structure on the cylinder side, which does not allow for sealing, is a structure that fully fulfills the original purpose of sealing. Yes, I can.

[0090] The sealing structure on the cylinder side that does not allow the inflow of liquefied gas is shown in detail in Figure 11b. As shown, it consists of a combination of a guide ring 420 and a piston seal 430. In general, a guide ring housing groove is provided around the piston section, and the guide ring housing A strip-shaped plate-shaped guide ring 420 is fitted into the groove. Also, from the guide ring housing groove, A piston seal housing groove is provided around the piston portion, which is located at a position separated in the longitudinal direction of the stone portion. The piston seal 430 is then installed in the piston seal housing groove.

[0091] The guide ring 420 is positioned on both sides of the piston seal 430, and the guide ring The 420 guides the movement of the piston 50, and the piston seal 430 liquefies the gas It plays a role in suppressing the influx of sewage.

[0092] The piston seal 430 is configured in detail as follows: Piston seal 430 It consists of a contact member 431, a spring member 432, and a stopper 433. Contact member 43 1. The spring member 432 and the stopper 433 surround the piston 50.

[0093] The contact member 431 has one side in close contact with the outer surface of the piston 50 and the other side in close contact with the inner surface of the cylinder 80. It is fitted tightly against the wall and has a recessed groove in which a spring member 432 can be housed. The spring member 432 is The spring member 432 is interposed in the groove of the contact member 431, and the restoring force of the spring member 432 causes the contact member 431 to move. Its role is to apply force to ensure tight contact between the outer surface of stone 50 and the inner wall of cylinder 80. The combination of attachment member 431 and spring member 432 allows liquefied gas to be released from one side of the cylinder to the other side. It is possible to suppress the flow to one side. The stopper 433 has a tight spring member 432. It serves to prevent the attachment member 431 from coming out of its storage groove.

[0094] Next, looking at the sealing structure on the rod side, it is as shown in Figures 10 and 12. The sealing structure on the rod side prevents the inflow of liquefied gas from the cylinder side, and also... Air, foreign matter, and other substances that may enter from the joint between the live shaft 40 and the piston 50. It is designed to prevent the influx of quality.

[0095] A piston cover 52 is positioned around the rod portion where the rod portion of the piston 50 is located. Piston cover 52, rod seal 520, guide ring 510 and wiper seal 530 The rod seal 520 is provided on the piston cover 52 on the cylinder 80 side. The wiper seal 530 is provided on the piston cover 52 in the direction of the drive shaft 40. Adjacent to the rod seal 520 and the wiper seal 530 are the piston cover 52 A guide ring is positioned on top, and the guide ring is located towards the inside of the rod section. Therefore Then, a wiper seal 53 is attached to the piston cover 52 from the drive shaft 40 direction towards the cylinder 80 direction. The structure consists of 0, guide ring, guide ring, and rod seal 520 arranged in sequence.

[0096] The wiper seal 530 is designed to prevent air, foreign matter, and other air that may enter from the drive shaft 40 direction. The rod seal 520 plays a role in preventing the inflow of substances, and it also prevents the inflow of liquefied gas from the cylinder 80 side. It serves to prevent this. Also, the guide ring moves on the piston cover 52 of the rod section. They play a guiding role.

[0097] The rod seal 520 and wiper seal 530 were applied to the sealing structure on the cylinder side. It has the same structure as a piston seal. That is, a rod seal 520 and a wiper seal 53 Each of the 0s is a sealing member 531, a spring member 532 and a stop, similar to the piston seal 430. It consists of 533.

[0098] Furthermore, the guide ring 510 applied to the sealing structure on the rod side is the sealing on the cylinder side Similar to the guide ring 510 applied to the ring structure, a spring member 511 is further provided on the inside. The guide ring 510 guides the movement of the rod during its reciprocating motion. The spring member 511 is split and contacts the guide ring 510, and when the rod section moves, the spring member 511 contacts the guide ring It plays a role in buffering the force applied to it. The spring member 511 is provided to guide The position of ring 510 can now be kept constant, providing stable guidance for the movement of the rod section. It is possible.

[0099] On the other hand, one of the most important features of the present invention is the multiple cylinders provided on the camshaft 10. This means that each of the 80s can be driven independently.

[0100] As mentioned above, the camshaft 10 is equipped with multiple cam noses 20 spaced apart, Each cam nose 20 is fitted in close contact with a cam roller 30, and each cam roller 3 The drive shaft 40, piston 50, cylinder 80, and liquefied gas compressor are connected to unit 0. This forms the structure. As a result, the operation of one camshaft 10 compresses multiple liquefied gases. The device is designed to be operational.

[0101] Under this structure, the drive of each of the multiple cylinders 80, that is, multiple Each drive of the liquefied gas compressor can be controlled independently. As a method for doing so, the present invention forcibly separates the cam roller 30 from the cam nose 20, and Drive shaft 40, piston 50, cylinder 80 and connected to the separated cam roller 30 This paper presents a technique for stopping the operation of a liquefied gas compressor. Specifically, it presents three different embodiments. This can be realized. In the first embodiment, the cam roller 30 is made available using the cut-off bolt 140. This method separates the nose 20, and the second embodiment utilizes the cutoff pin 620. This method separates the cam roller 30 from the cam nose 20, and the third embodiment is a rack-pinion This method uses ON 730 to separate the cam roller 30 from the cam nose 20.

[0102] First, the first embodiment is as follows.

[0103] Referring to Figures 13 and 14, one side of the cam roller drive shaft case 130 is cut A cutoff bolt insertion port 131 through which a cutoff bolt 140 is inserted is provided, and an integrated connecting part A cutoff bolt 140 can be inserted to a certain depth on one side of the material 110. A bolt insertion groove 111 is provided.

[0104] The cutoff bolt 140 is cut off when it is inserted through the cutoff bolt insertion opening 131. As bolt 140 is inserted into the cutoff bolt insertion groove 111, the cam nose 2 This can induce a separation between 0 and the cam roller 30.

[0105] The cam nose 20 and the cam roller 30 are separated from each other, thereby the camshaft 1 Even when the 0 is rotated, the cam nose 20 and the cam roller 30 do not make contact, and the cam roller The operation of the drive shaft 40 and piston 50 connected to 30 can be stopped. By such a method, the drive of each piston 50 attached to the camshaft 10 is It can be controlled selectively.

[0106] The cutoff bolt 140 is inserted into the cutoff bolt insertion groove 111 by The principle by which the cam roller 30 is separated from the cam nose 20 is as follows (Figures 4a and 4a) (See 4b).

[0107] Adjacent cutoff bolt insertion openings 131 and cutoff bolt insertion grooves 111 This means that their centers do not coincide and are separated from each other, forming a shape.

[0108] When the cam roller drive shaft case 130 is provided with a cutoff bolt insertion port 131 Both integrated connecting members 110 are provided with cutoff bolt insertion grooves 111, and cutoff bolt The bolt 140 is inserted through the cutoff bolt insertion opening 131 into the cutoff bolt insertion groove 111. It is inserted. The cutoff bolt insertion opening 131 and the cutoff bolt insertion groove 111 are the same. You may design it using diameter.

[0109] At this time, the center of the cutoff bolt insertion opening 131 and the inside of the cutoff bolt insertion groove 111 It takes on a form that is separated from the heart. The piston 50 is positioned vertically on the camshaft 10. Based on this, the center of the cutoff bolt insertion groove 111 is the cutoff bolt insertion opening 13 It is located slightly lower than the center of 1. Also, the cutoff bolt insertion groove 111 is deep It has a tapered shape where the radius decreases as the depth increases. The radius of the entrance side and the radius of the bottom side of the bolt insertion groove 111 have a radius difference of only "d". (See Figure 14).

[0110] Under these conditions, the cutoff bolt is inserted through the cutoff bolt insertion port 131. The 140 is inserted into the cutoff bolt insertion groove 111, cutoff bolt insertion groove 111 The center is located slightly lower than the center of the cutoff bolt insertion opening 131. Therefore, the cutoff bolt 140 is on the side of the tapered cutoff bolt insertion groove 111. It will come into contact with the surface.

[0111] If you continue screwing the cutoff bolt 140 in the insertion direction, the cutoff bolt T140 is along the side of the cutoff bolt insertion groove 111 cutoff bolt insertion groove 111 It will move further inward. Cut-off bolt 140 cut-off bolt insertion Moving to the inside of the insertion groove 111 means that the cutoff bolt insertion groove 111 is provided This means that the body-type connecting member 110 moves upward.

[0112] In this manner, one end of the cutoff bolt 140 is at the bottom of the cutoff bolt insertion groove 111. When it comes into contact with the surface, the integrated connecting member 110 has a radius on the entrance side of the cutoff bolt insertion groove 111. It moves upward by a length of "d", which is the difference in radius from the bottom radius. Here, cutoff bolt 1 40 may also have a tapered shape in a certain part for easier insertion, in which case an integrated connecting member The travel distance of 110 corresponds to the value obtained by subtracting the taper thickness of the cutoff bolt 140 from "d". It is correct.

[0113] Through the process described above, the integrated connecting member 110 can be moved upward by a length of "d". This means that the distance between the cam nose 20 and the cam roller 30 is a distance of "d". This principle allows the cam nose 20 and the cam roller 30 to maintain their separated state. This allows the camshaft 10 to rotate due to the separation between the cam nose 20 and the cam roller 30. Even if it is rotated, the drive shaft 40 and piston 50 connected to the cam roller 30 will not operate. stomach.

[0114] As mentioned above, a cutoff bolt 14 is located on one side of the cam roller drive shaft case 130. A cutoff bolt insertion opening 131 through which 0 is inserted is provided, on one side of the integrated connecting member 110 A cutoff bolt insertion groove 11 into which a cutoff bolt 140 can be inserted to a certain depth. Although it was stated that 1 is provided, the cutoff bolt insertion port 131 and cutoff bolt The position of the insertion groove 111 is not specified. In one embodiment, the camshaft case 10 The cutoff bolt insertion opening 131 and cutoff bolt insertion groove are located in the inner space. 111 may be provided (see Figures 4a and 4b), and on the outside of the camshaft 10 case A cutoff bolt insertion opening 131 and a cutoff bolt insertion groove 111 are provided in that location. It's okay.

[0115] The configuration of the second embodiment utilizing the cutoff pin 620 is as follows:

[0116] Referring to Figures 15 and 16, one side of the cam roller drive shaft case 130 is internal The cutoff pin guide member 610 is provided, which is a cylindrical cutoff pin guide part A cutoff pin 620 is inserted into material 610. The cutoff pin 620 is cut The toe-off pin guide member 610 is capable of moving up and down within it.

[0117] A cutoff pin guide groove 611 is provided on one side of the cutoff pin guide member 610. The cutoff pin guide groove 611 is divided into a vertical guide groove and a horizontal guide groove, and the vertical The id groove and the horizontal guide groove are spatially connected to each other. The vertical guide groove is the first ground on the vertical line. It extends from point 1 to point 2, and the horizontal guide groove extends horizontally from point 2 of the vertical guide groove. It extends to the third point in the opposite direction. The second and third points of the horizontal guide groove are at 0 degrees and It is preferable that it be installed at a point at 180 degrees.

[0118] A cutoff pin guide pin 621 is provided on one side of the cutoff pin 620. The cutoff pin guide pin 621 is located within the cutoff pin guide groove 611. The cutoff pin guide pin 621 is movable along the cutoff pin guide groove 611. Therefore, the cutoff pin guide pin 621 is at the first point of the cutoff pin guide groove 611. When you move vertically to the second point, the cutoff pin 620 descends by the corresponding distance, and the cutoff The pin guide pin 621 moves horizontally from the second point to the third point of the cutoff pin guide groove 611. When moved, the cutoff pin 620 moves by the angle between the second point and the third point, for example, 1 It rotates only 80 degrees.

[0119] The bottom surface of the cutoff pin 620 is a cylinder with a radius smaller than that of the cutoff pin 620. A cam roller separation projection 622 of a certain shape is provided. The center of the cam roller separation projection 622 is cut The cutoff pin 620 is eccentric in shape from the center of the circle. The cutoff pin guide pin 621 is When the cutoff pin guide groove 611 moves horizontally from the second point to the third point, the cutoff pin The cam roller separation projection 622 on the bottom surface of 620 also rotates at a certain angle, for example, 180 degrees. To change.

[0120] On the other hand, a cutoff pin 620 is inserted through one side of the cam roller drive shaft case 130. A cutoff pin insertion port 132 is provided, and a corresponding one The body-type connecting member 110 is provided with a cam roller separation guide groove 112.

[0121] When the cutoff pin guide pin 621 is at the second position, below the cutoff pin 620 The cam roller separation projection 622 at the end is located in the cam roller separation guide groove 112 of the integrated connecting member 110. Located inside, the cam roller separation projection 622 is integrally connected within the cam roller separation guide groove 112. It is in a state of not contacting the member 110 (see Fig. 17a).

[0122] In such a state, when the cut-off pin 620 protrusion is moved from the second point to the third point of the cut-off pin guide groove 611, the cut-off pin 620 rotates horizontally, and accordingly the cam roller separation protrusion 622 also rotates horizontally, whereby the cam roller separation protrusion 62 2 horizontally rotates at a certain angle within the cam roller separation guide groove 112 while the integral connecting member 11 0 comes into contact with it (see Fig. 17b). Next, the cam roller separation protrusion 622 physically pushes out the integral connecting member 110 with which it is in contact, and due to the movement of such an integral connecting member 110, the cam roller 30 also moves together with the integral connecting member 110, and finally the separation between the cam roller 30 and the cam nose 20 is achieved (see Fig. 17c). .

[0123] Conversely, when the cut-off pin guide pin 621 is moved from the third point to the second point of the cut-off pin guide groove 611, the moved integral connecting member 110 returns to the initial state, and the cam roller 30 and the cam nose 20 come into contact again.

[0124] As described above, the configuration using the cut-off pin 620 induces the separation between the cam nose 20 and the cam roller 30, and by the separation between the cam nose 20 and the cam roller 30, the driving of a specific piston 50, that is, the driving of a specific cylinder 80 can be selectively controlled.

[0125] The configuration of the third embodiment using the rack and pinion 730 is as follows.

[0126] In the first and second embodiments, the integrated connecting member 110 is fitted with a cut-off bolt 140 or a cut-off bolt. By inserting the toe-off pin 620, the cam roller 30 is separated from the cam nose 20. In contrast to the previous method, the third embodiment moves the cam roller 30 by the movement of the drive shaft 40. This method guides the separation from the cam nose 20.

[0127] According to the third embodiment, the drive shaft 40 and the piston 50 are connected as shown in Figure 18. A coupling case 710 is further provided in the area to protect it from the external environment. It can be further operated by the hydraulic cylinder 80, and the rack and pinion 730 device is also Prepare.

[0128] Specifically, a rack member 720 is provided in the inner space of the coupling case 710. The rack member 720 is connected to and fixed to one side of the drive shaft 40, or the drive shaft It is connected and fixed to both the eve shaft 40 and the piston 50. When the live axis 40 moves, the rack member 720 also moves with it. In other words, the rack member 7 When the 20 moves, the drive shaft 40 and piston 50 also move together.

[0129] The outer surface of the rack member 720 is provided with a tooth-shaped rack. The rack member 720 is equipped with a pinion 730 that meshes with it. This allows the rack member 720 to move up and down in conjunction with the rotational movement of the pinion 730. This becomes possible. On the other side of pinion 730 is a pinion gear that transmits driving force to pinion 730. A side member 740 is provided, and the pinion guide member 740 is selected by the hydraulic cylinder 80. It moves up and down. A rack is also provided on the surface of the pinion guide member 740, and the pinion 7 30 engages with the rack of pinion guide member 740.

[0130] Under this structure, the pinion guide member 740 is lowered via the hydraulic cylinder 80. When the orientation is changed, pinion 730 rotates counterclockwise, and the counterclockwise rotation of pinion 730 The rotation causes the rack member 720 connected to the drive shaft 40 to move upward. The upward movement of member 720 means the upward movement of drive shaft 40, and the drive shaft 40 is upward By moving, the separation between the cam nose 20 and the cam roller 30 is induced. You will be able to do it.

[0131] The above describes the separation method between the cam roller 30 and the cam nose 20 according to the first to third embodiments. The formula was explained. On the other hand, the cam using the first to third embodiments described above... Regarding the separation between the roller 30 and the cam nose 20, the cam nose 20 is in a positive position relative to the cam roller 30. In this state, the cam roller 30 and the cam nose 20 must separate, A predetermined slewing gear may be provided for this purpose. The slewing gear fine-tunes the rotation of the camshaft 10. This allows the cam nose 20 to be adjusted to face the cam roller 30 directly.

[0132] The separation between the cam roller and the cam nose is induced by the first to third embodiments described above. This means that it is possible to control the drive of each cylinder independently. As described above, according to the first to third embodiments, the cam roller and the cam nose are separated. Because this is the method used, when the cam roller and cam nose are separated, the piston The system stops and no liquefied gas is discharged.

[0133] The present invention presents a technology capable of adjusting the discharge amount of liquefied gas. According to one embodiment of the present invention For example, by adjusting the stroke length of the piston 50, the discharge amount of liquefied gas can be controlled.

[0134] Specifically, as shown in FIG. 19, a pressure chamber 810 is provided between the drive shaft 40 and the piston 50. The first surface 811 of the pressure chamber 810 abuts against the drive shaft 40, and the other second surface 812 of the pressure chamber 810 abuts against the piston 50 and is fixed. Therefore, when the drive shaft 40 moves in the direction of the piston 50, the driving force of the drive shaft 40 is applied to the first surface 811 of the pressure chamber 810 and transmitted to the pressure chamber 810. At this time, if the pressure chamber 810 is filled with lubricating oil, the driving force of the drive shaft 40 should be directly transmitted to the piston 50 through the pressure chamber 810 (the first case). If the pressure chamber 810 is an empty space, the driving force of the drive shaft 40 will disappear in the pressure chamber 810 and will not be transmitted to the piston 50 (the second case). When the driving force of the drive shaft 40 is applied with the pressure chamber 810 filled with lubricating oil and a part of the lubricating oil in the pressure chamber 810 is discharged, only a part of the driving force of the drive shaft 40 should be transmitted to the piston 50 (the third case).

[0135] One embodiment of the present invention can stop the discharge of liquefied gas or control the discharge amount of liquefied gas using the principle described above.

[0136] Here, a lubricating oil supply passage 830 is provided on one side of the pressure chamber 810, and lubricating ​​​​​​​​​​​​Supply of lubricating oil 820 to the pressure chamber 810 via the oil supply passage 830 or pressure chamber Lubricating oil 820 can be discharged from valve 810. Also, the lubricating oil supply channel 830 is lubricating oil It is connected to the supply device 840. The lubricating oil supply device 840 is used to supply the pressure chamber 810. The amount of lubricating oil 820 supplied and the amount of lubricating oil 820 discharged from the pressure chamber 810 are set. It is possible.

[0137] I will now explain the three cases mentioned above in detail.

[0138] As shown in Figure 20a, with the pressure chamber 810 filled with lubricating oil 820, When the driving force of the drive shaft 40 is applied to the first surface 811 of the pressure chamber 810, the drive shaft 4 The driving force is applied to the piston 50 via the lubricating oil 820 filling the pressure chamber 810. Finally, the pressure from piston 50 is transmitted to the liquefied gas compressor, resulting in the normal discharge of liquefied gas. Discharge occurs. At this time, the lubricating oil supply passage 830 is shut off and the lubrication of the pressure chamber 810 is interrupted. The oil is not discharged to the outside.

[0139] On the other hand, as shown in Figure 20b, if lubricating oil 820 is not present in the pressure chamber 810, When the driving force of the live shaft 40 is applied to the first surface 811 of the pressure chamber 810, the pressure chamber Because the 810 is an empty space, the first surface 811 of the pressure chamber 810 moves towards the second surface 812. It moves. At this time, the stroke length of the drive shaft 40 accompanying the drive of the camshaft is pressure cha If it falls between the first surface 811 and the second surface 812 of the rmb 810, the driving force of the drive shaft 40 is The pressure is not transmitted to the second surface 812 of the pressure chamber 810. Therefore, the camshaft is not driven. Consequently, even if the drive shaft 40 moves, the driving force of the drive shaft 40 is not transmitted to the piston 50. As a result, the liquefied gas compressor does not operate, and no liquefied gas is discharged.

[0140] Finally, looking at the third case, as shown in Figure 20c, lubricating oil is applied to the pressure chamber 810. With the lubricating oil supply passage 830 open along with the condition 7, the driving force of the drive shaft 40 When the pressure is applied to the first surface 811 of the pressure chamber 810, the lubricating oil inside the pressure chamber 810 The lubricating oil is discharged through the lubrication oil supply channel 830, and the first surface 811 moves towards the piston 50. This will occur. At this time, the amount of lubricating oil discharged through the lubricating oil supply passage 830 will be adjusted. By doing so, the movement distance of the first surface 811 can be controlled. That is, the first surface 8 The travel distance of 11 is the lubrication discharged from the pressure chamber 810 through the lubrication oil supply passage 830. The amount of lubricant discharged from the pressure chamber 810 through the lubricating oil supply passage 830 is proportional to the amount of oil. By adjusting the amount of oil, the piston stroke length can be controlled.

[0141] The length of the total stroke length Ds of the drive shaft 40 that is the length of the lubricating oil discharge from the pressure chamber 810. Because the drive force is not applied to the piston 50, the piston 50 also does not move through the entire stroke. This is the stroke length obtained by subtracting the length of the pressure chamber 810 used for lubricating oil discharge from the total stroke length Ds. It will start to move. In this way, the stroke length of piston 50 is shortened. As a result, the amount of liquefied gas discharged through the liquefied gas compressor decreases compared to normal operation. .

[0142] As mentioned above, the discharge of liquefied gas is stopped by setting the pressure chamber 810 to an empty space state. This can be done, and by filling the pressure chamber 810 with lubricating oil 820, the drive shaft 4 The driving force of 0 is fully transmitted to the piston 50 to maintain the discharge of liquefied gas in a normal state. This allows for adjustment of the amount of lubricating oil discharged from the pressure chamber 810. This allows for selective control of the discharge amount of liquefied gas from the liquefied gas compressor. Cut.

[0143] On the other hand, the gas supply pump according to the present invention is equipped with multiple pistons on a single camshaft. Each piston is then operated by any of the cutoff methods described in the first to third embodiments above or It can be driven independently by the pressure chamber system described above.

[0144] The liquefied gas compressor, which is linked to each piston, generates high pressure as the camshaft rotates. The liquefied gas is discharged under pressure, and the liquefied gas discharged through each liquefied gas compressor is integrated. The exhaust gases merge in the exhaust pipe and are ultimately supplied to the engine combustion chamber.

[0145] When supplying liquefied gas to the engine combustion chamber via an integrated exhaust pipe, the liquefied gas is discharged Pressure-induced pulsation (hereinafter referred to as "discharge pressure pulsation") will be observed (see Figure 21). The discharge pressure pulsation of the liquefied gas supplied to the engine combustion chamber via the combined discharge pipe is due to the combustion of the liquefied gas. It has a physical impact on the engine, not just on efficiency. If the discharge pressure pulsation is large, the combustion of the liquefied gas will be affected. As combustion efficiency decreases, the engine also begins to experience physical shocks.

[0146] The discharge pressure pulsation of liquefied gas is related to the number of pistons that operate in conjunction with the camshaft and the number of pistons The ton is related to the phase of the cam nose to which it is connected. The more pistons that are in motion, the greater the discharge. When the output pressure pulsation is reduced and the phases of the cam noses to which the pistons are connected are arranged at equal intervals. Experiments confirmed that this reduces discharge pressure pulsation.

[0147] Figures 22 and 23 show the discharge pressure pulsation corresponding to the number of pistons and the phase of the cam nose. These are the experimental results. Referring to Figure 22, there are four pistons connected to the camshaft. In some cases, when there are two operating pistons, the discharge pressure pulsation is 7.5 ba. r is the largest. On the other hand, the discharge pressure pulsation when there are 3 operating pistons is 5.5 When there are four operating pistons, the discharge pressure pulsation is 3.5 bar. It can be seen that the discharge pressure pulsation decreases as the number of pistons increases. The more pistons there are, the more liquefied gas is compressed and discharged through each piston. This is because the discharge pressure pulsations are canceled out.

[0148] Also, referring to Figure 23, the phases of the cam noses are equally spaced and the phases of the cam noses If there is no change and one piston is cut off, the number of operating pistons is two. When there are three, and when the phases of the cam noses are equally spaced, discharge It can be seen that the output pressure pulsation is reduced. Specifically, there are three operating pistons and the cam nose When the phases are equally spaced, the discharge pressure pulsation is 5.5 bar, whereas the position of the cam nose... If there is no phase change and one piston is cut off, and three pistons are operated, discharge The pressure pulsation increased to 10 bar. Also, there are two operating pistons and the phase of the cam nose is When the intervals are equal, the discharge pressure pulsation is 7.5 bar, whereas the phase change of the cam nose If there is no such mechanism and one piston is cut off, operating both pistons will result in a discharge pressure pulse. The dynamics increased to 10 bar.

[0149] As can be seen from the above, the number of pistons that are linked to the drive of the camshaft increases Furthermore, when the phases of the cam nose are equally spaced, discharge pressure pulsation can be reduced. .

[0150] Furthermore, the experimental results mentioned above show that the discharge pressure depends on the number of pistons and the phase arrangement of the cam nose. It can be seen that the force pulsation can be adjusted. In one embodiment, the allowable range of discharge pressure pulsation The number of pistons operating and the phase of the cam nose may be arranged taking the surrounding area into consideration. For example, discharge If the upper limit of the acceptable range for pressure pulsation is 8 bar or less, the cam nose phases are arranged at equal intervals. The minimum number of pistons that are positioned and operate simultaneously is two. [Explanation of Symbols]

[0151] 10 camshafts, 20 cam noses, 30 cam rollers, 40 drive shafts, 50 piston, 50a intake valve exhaust pipe, 51a Spring member housing groove, 51b Guide ring housing groove, 52 Piston cover, 60 Intake valve, 61 Opening / closing member, 62 Liquefied gas inlet, 63 Spring member, 70 Discharge valve, 71 Discharge chamber, 72 Auxiliary chamber, 73 Discharge inlet pipe, 74 Space at the upper end of the discharge chamber, 75 Spring member, 80 cylinders, 110 Integrated connecting member, 111 Cut-off bolt insertion groove, 112 Cam roller separation guide groove, 120 Compression spring, 130 Cam roller drive shaft case, 131 Cut-off bolt insertion port, 132 Cut-off pin insertion opening, 140 Cut-off bolt, 210 First storage section, 220 Second storage section, 230 Inertia moment buffer member, 240 Stopper, 250 clamps, 310 liquefied gas supply ports, 320 Liquefied gas supply channel, 410 Spring member, 420 guide ring, 510 guide ring, 520 rod seals, 530 wiper seals, 610 Cut-off pin guide member, 611 Cut-off pin guide groove, 620 Cutoff pin, 621 Cutoff pin guide pin, 622 Cam roller separation projection, 710 Coupling case, 720 rack components, 730 pinion, 740 Pinion guide component.

Claims

1. A camshaft capable of rotational drive; A plurality of cam noses are provided at regular intervals along the longitudinal direction of the camshaft and are eccentric in shape from the center of the camshaft; and It comprises a plurality of cylinder units for liquefied gas discharge, each provided corresponding to each of the plurality of cam noses, which discharge liquefied gas when the gas supply pump is driven; Each of the aforementioned plurality of cylinder units is A cam roller that is fitted in close contact with the corresponding cam nose; A drive shaft and piston provided adjacent to one side of the cam roller; A cylinder in which the piston moves linearly back and forth within the internal space; and A liquefied gas compressor is included, which pressurizes and discharges liquefied gas in accordance with the linear reciprocating motion of the piston; wherein the corresponding cam nose rotates in accordance with the rotation of the camshaft, causing the linear reciprocating motion of the piston; further The camshaft includes a separation mechanism that separates the cam roller from the corresponding cam nose when the camshaft rotates, and maintains a separated state between the cam roller and the cam nose such that the rotational driving force of the corresponding cam nose is not transmitted to the piston. The gas supply pump for a ship's dual-fuel engine is characterized in that the plurality of cylinder units comprises a first cylinder unit and a second cylinder unit, and when the gas supply pump is driven, parallel control of the driving of the first cylinder unit and the non-driving of the second cylinder unit by the separation mechanism is possible.

2. Each of the aforementioned plurality of cylinder units is The gas supply pump for a marine dual-fuel engine according to claim 1, characterized in that a drive shaft is arranged perpendicular to one camshaft, and a cam roller is provided between the cam nose of the camshaft and the drive shaft.

3. The gas supply pump for a marine dual-fuel engine according to claim 1, characterized in that the rotation center of the cam nose is the same as the rotation center of the cam shaft, the radius of the cam nose is smaller than the radius of the cam shaft, and the cam roller, which is in close contact with the cam nose when the cam shaft rotates, performs linear reciprocating motion within a certain distance.

4. The gas supply pump for a marine dual-fuel engine according to claim 1, characterized in that when the cam nose is positioned at a 90-degree angle with respect to the vertical direction due to the rotation of the camshaft, the cam roller moves in a direction in which the liquefied gas is compressed by the piston, and when the cam nose is positioned at a 270-degree angle due to the rotation of the camshaft, the cam roller moves in a direction in which the liquefied gas is decompressed by the piston.

5. Each of the aforementioned plurality of cylinder units is An integrated connecting member is further provided to connect the cam roller and the drive shaft in a single unit. A cam roller is housed at one end of the integrated connecting member, a drive shaft is mounted on the other end, and a compression spring surrounding the drive shaft is fixed inside the integrated connecting member. The gas supply pump for a marine dual-fuel engine according to claim 1, characterized in that the cam roller, which is in close contact with the cam nose, and the drive shaft and an integrated connecting member both perform linear reciprocating motion when the camshaft rotates.

6. Each of the aforementioned plurality of cylinder units is At the point where the drive shaft and piston are connected, A first housing portion and a second housing portion are provided on one end of the drive shaft, with the first housing portion located inward of the drive shaft and the second housing portion located outward of the drive shaft. The gas supply pump for a marine dual-fuel engine according to claim 1, characterized in that the first housing is provided with an inertia moment buffering member, and one exposed surface of the inertia moment buffering member is in close contact with the piston.

7. The diameter of the second housing is larger than the diameter of the first housing, and the diameter of the first housing corresponds to the diameter of the piston. A gas supply pump for a marine dual-fuel engine according to claim 6, characterized in that a stopper is fitted in the space between the second housing and the piston, and the stopper is provided in close contact with the inner diameter of the piston and the second housing to prevent the piston from rotating.

8. The gas supply pump for a marine dual-fuel engine according to claim 6, characterized in that a clamp is provided at the joint between the drive shaft and the piston to protect the joint.

9. The liquefied gas compressor is A liquefied gas supply channel that supplies the liquefied gas to be compressed to the intake valve, An intake valve that draws in liquefied gas from a liquefied gas supply channel and, when piston pressure is applied, supplies the drawn-in liquefied gas to the discharge valve side, The gas supply pump for a ship's dual-fuel engine according to claim 1, characterized in that it includes a discharge valve that discharges liquefied gas supplied from an intake valve under pressurized conditions.

10. One end of the liquefied gas supply channel is connected to a liquefied gas supply port located on one side of the gas supply pump, and the other end is connected to a liquefied gas intake port located on one side of the intake valve. The gas supply pump for a ship's dual-fuel engine according to claim 9, characterized in that the liquefied gas to be compressed is supplied to the internal space of the intake valve via a liquefied gas inlet through a liquefied gas supply port and a liquefied gas supply channel.

11. The intake valve is equipped with an opening / closing member that selectively opens and closes the liquefied gas intake port, and the opening / closing member is connected to a spring member provided around the lower end of the intake valve, and is capable of linear reciprocating motion as the spring member is compressed and restored. When the opening / closing member moves in the compression direction due to the compression of the spring member, the liquefied gas inlet is opened, and when the opening / closing member moves in the return direction due to the return of the spring member, the liquefied gas inlet is closed. The gas supply pump for a ship's dual-fuel engine according to claim 9, characterized in that when liquefied gas is supplied through the liquefied gas supply channel while the opening / closing member is blocking the liquefied gas inlet, the opening / closing member moves in the compression direction of the spring member due to the supply pressure of the liquefied gas, thereby opening the liquefied gas inlet and supplying liquefied gas to the internal space of the intake valve.

12. The discharge valve is located inside the discharge chamber. A spring member is provided on the lower end of the discharge valve, and the linear reciprocating motion of the discharge valve is made possible by the compression and recovery of the spring member. An auxiliary chamber with a certain amount of space is provided around the upper end of the discharge chamber, and a discharge inlet pipe is provided between the auxiliary chamber and the discharge valve. The gas supply pump for a ship's dual-fuel engine according to claim 9, characterized in that the liquefied gas discharged from the intake valve is supplied to the discharge valve by sequentially passing through an auxiliary chamber and a discharge inlet pipe.

13. Each of the aforementioned plurality of cylinder units is A cam roller drive shaft case is further provided on the outside of the integrated connecting member to protect the integrated connecting member and to guide its movement. One side of the cam roller drive shaft case is provided with a cutoff bolt insertion port through which a cutoff bolt is inserted, and one side of the integrated connecting member is provided with a cutoff bolt insertion groove into which a cutoff bolt can be inserted to a certain depth. The gas supply pump for a marine dual-fuel engine according to claim 5, characterized in that the separation between the cam nose and the cam roller is induced by the process in which the cutoff bolt is inserted into the cutoff bolt insertion groove while the cutoff bolt is inserted through the cutoff bolt insertion port, thereby forming the separation mechanism.

14. The center of the cutoff bolt insertion opening and the center of the cutoff bolt insertion groove are spaced apart, and assuming that the piston is positioned perpendicular to the camshaft, the center of the cutoff bolt insertion groove is located slightly lower than the center of the cutoff bolt insertion opening. The gas supply pump for a marine dual-fuel engine according to claim 13, characterized in that the cutoff bolt insertion groove has a tapered shape in which the radius decreases as the depth increases, and the radius difference between the inlet side radius and the bottom side radius of the cutoff bolt insertion groove is "d" due to the tapered shape.

15. During the process in which the cutoff bolt, after being inserted through the cutoff bolt insertion port, is inserted into the cutoff bolt insertion groove, The cutoff bolt contacts the side surface of the tapered cutoff bolt insertion groove and moves along the side surface of the cutoff bolt insertion groove towards the inside of the cutoff bolt insertion groove. The gas supply pump for a marine dual-fuel engine according to claim 13, characterized in that, as the cutoff bolt moves inward into the cutoff bolt insertion groove, the integrated connecting member provided with the cutoff bolt insertion groove moves upward, and the cam roller is separated from the cam nose.

16. Each of the aforementioned plurality of cylinder units is A cam roller drive shaft case is further provided on the outside of the integrated connecting member to protect the integrated connecting member and to guide its movement. A cylindrical cutoff pin guide member with an internal cavity is provided on one side of the cam roller drive shaft case, and a cutoff pin is inserted into the cutoff pin guide member so as to be able to move up and down. A cutoff pin guide groove is provided on one side of the cutoff pin guide member. The cutoff pin guide groove is divided into a vertical guide groove and a horizontal guide groove that are spatially connected to each other. The vertical guide groove extends from a first point to a second point on a vertical line, and the horizontal guide groove extends from the second point of the vertical guide groove to a third point in the horizontal direction. A cutoff pin guide pin is provided on one side of the cutoff pin, and the cutoff pin guide pin is located within the cutoff pin guide groove. When the cutoff pin guide pin moves vertically from a first point to a second point in the cutoff pin guide groove, the cutoff pin descends by the distance between the first and second points; when the cutoff pin guide pin moves horizontally from a second point to a third point in the cutoff pin guide groove, the cutoff pin rotates by the angle between the second and third points. The bottom surface of the cutoff pin is provided with a cylindrical cam roller separation projection having a smaller radius than the cutoff pin, and the center of the cam roller separation projection is eccentrically positioned from the circular center of the cutoff pin. The gas supply pump for a ship's dual-fuel engine according to claim 5, characterized in that when the cutoff pin guide pin moves horizontally from a second point to a third point in the cutoff pin guide groove, the cam roller separation projection provided on the bottom surface of the cutoff pin rotates by a certain angle, thereby forming the separation mechanism.

17. One side of the cam roller drive shaft case is provided with a cutoff pin insertion port through which a cutoff pin is inserted, and the integrated connecting member corresponding to the cutoff pin insertion port is provided with a cam roller separation guide groove. When the cutoff pin guide pin is positioned at the second point, the cam roller separation projection at the lower end of the cutoff pin is located within the cam roller separation guide groove of the integrated connecting member, and within the cam roller separation guide groove, the cam roller separation projection does not come into contact with the integrated connecting member. When the cutoff pin projection is moved from the second point to the third point of the cutoff pin guide groove, the cam roller separation projection rotates horizontally in conjunction with the horizontal rotation of the cutoff pin, physically pushing out and moving the integrated connecting member. The gas supply pump for a ship's dual-fuel engine according to claim 16, characterized in that the cam roller and the cam nose are separated by the movement of an integrated connecting member by a cam roller separation projection, thereby forming the separation mechanism.

18. Each of the aforementioned plurality of cylinder units is A coupling case provided at the connection point between the drive shaft and the piston; A rack member that is connected to and fixed to the drive shaft, or to both the drive shaft and the piston, within the inner space of the coupling case; A pinion that meshes with a toothed rack provided on the outer surface of a rack member; and A pinion guide member provided on the other side of the pinion for transmitting driving force to the pinion; further includes, The gas supply pump for a marine dual-fuel engine according to claim 1, characterized in that when the pinion guide member is moved downward, the pinion rotates counterclockwise, the counterclockwise rotation of the pinion causes the rack member connected to the drive shaft to move upward, and the upward movement of the rack member separates the cam nose and the cam roller, thereby forming the separation mechanism.

19. The gas supply pump for a marine dual-fuel engine according to claim 18, characterized in that the pinion guide member reciprocates by a cylinder.

20. When the gas supply pump is driven, each of the multiple cam noses rotates as the camshaft rotates, The first cylinder unit includes a first cam roller, which is driven by transmitting the rotational driving force of the corresponding cam nose to the corresponding piston, causing linear reciprocating motion. The gas supply pump for a marine dual-fuel engine according to claim 1, wherein the second cylinder unit includes a second cam roller, and the separation mechanism maintains a separated state in which the second cam roller is separated from the corresponding cam nose, and the rotational driving force of the cam nose is not transmitted to the corresponding piston, thereby not causing linear reciprocating motion of the piston and thus not being driven.

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