Gas supply pump of vessel dual fuel engine

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 cylinder-type dual fuel engine. This invention relates to a gas supply pump for a marine dual fuel engine capable of independent drive of the two engines. [Background technology]

[0002] Dual fuel engines used on ships are natural gas-fired. Uses gas or heavy oil as fuel. FGSS (fuel gas supply system) The tem is a device that supplies liquefied gas to a dual fuel engine. In dual fuel engines with gas injection, the high pressure pump for FGSS is used to supply high pressure gas. must be provided as a mandatory requirement.

[0003] For example, FG as described in Korean Patent Publication No. 2018-0093403 A high-pressure pump for a gas station generally has multiple cylinders on one crankshaft, each The connecting rod and piston attached to the cylinder reciprocate within the cylinder to push high-pressure fuel. However, in the case of high-pressure pumps of this type, The rod and piston are structurally connected to the crankshaft and are mounted in a cylinder. It is not possible to selectively control the operation of the head and piston. To prepare for failures and inspections, it is necessary to install an extra high pressure pump.

[0004] Thus, in addition to the high pressure pump for driving, an extra high pressure pump is installed in the FGSS. Therefore, it is necessary to secure space for two high pressure pumps. However, additional costs will be incurred due to the installation of two high pressure pumps. Summary of the Invention [Problem to be solved by the invention]

[0005] The present invention has been made to solve the above-mentioned problems, and the present invention relates to a cylinder. The object of the present invention is to provide a gas supply pump for a marine dual fuel engine capable of being driven independently. There is. [Means for solving the problem]

[0006] In order to achieve the above object, the present invention provides a gas supply pump for a marine dual fuel engine. , a camshaft that can be rotated, and at regular intervals along the longitudinal direction of the camshaft A plurality of cam noses each having an eccentric shape from the center of the camshaft. Cam rollers are installed close to the cams, and are installed adjacent to one side of the cam rollers. The drive shaft and piston, and the linear reciprocating motion of the piston pressurize and discharge the liquefied gas. and a liquefied gas compressor, the cam nose of the piston being rotated by the cam shaft. When it moves in the compression direction, the piston is compressed, and the cam nose moves in the piston decompression direction. Then, the piston is decompressed, and the cam roller can be selectively separated from the cam nose. When the cam roller and the cam nose separate, the rotational driving force of the cam nose is transmitted to the piston. It is characterized in that it is not possible to

[0007] A single camshaft has multiple drive shafts arranged in a line perpendicular to each other. A cam roller is provided between the cam nose of the drive shaft and the drive shaft.

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

[0009] When the cam nose is positioned at a 90 degree angle to the vertical due to the rotation of the camshaft, When the piston is compressed, the cam roller moves in the direction of the piston's compression, and the cam nose moves in the direction of the piston's compression. When the piston is at an angle of 270 degrees, the cam roller moves in the direction of decompressing the piston.

[0010] The cam roller and the drive shaft are further connected to each other by an integral connecting member. The cam roller is housed on one end of the integral connecting member, and the drive shaft is attached to the other end. A compression spring is provided around the drive shaft and fixed to the inside of the integral connecting member. When the cam roller is in contact with the cam nose, the drive shaft and the integral connecting member are all in a straight line. Move back and forth.

[0011] The part where the drive shaft and piston are connected provides a certain amount of space on one end of the drive shaft. The first receiving portion is located on the inner side of the drive shaft, The second receiving portion is provided toward the outside of the drive shaft, and the moment of inertia of the first receiving portion is A buffer member is provided, and one exposed surface of the buffer member is in close contact with the piston. .

[0012] One surface of the inertia moment buffer member that comes into 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 moment of inertia is dispersed by the convex surface of the moment of inertia damping member.

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

[0014] A clamp is provided at the joint between the drive shaft and the piston to protect the joint. It is okay to do so.

[0015] The liquefied gas compression device includes a liquefied gas supply passage that supplies the liquefied gas to be compressed to a suction valve. When the piston pressure is applied, the liquefied gas is sucked in from the liquefied gas supply passage. The suction valve supplies liquefied gas to the discharge valve, and the liquefied gas supplied from the suction valve is It includes a discharge valve that discharges under pressure.

[0016] One end of the liquefied gas supply passage is connected to a liquefied gas supply port provided on one side of the gas supply pump. The other end is connected to a liquefied gas intake port provided on one side of the intake valve, and the The liquefied gas is sucked in through the liquefied gas inlet and the liquefied gas supply passage. It is supplied to the inner space of the valve.

[0017] An opening and closing member is provided around the suction valve for selectively opening and closing the liquefied gas suction port, and the opening and closing member is connected to the spring member provided around the lower end of the intake valve to compress and restore the spring member. The spring member is compressed to move the opening and closing member in the compression direction. When the spring member is restored to its original position, the opening and closing member moves in the restoration direction. The liquefied gas supply is shut off when the liquefied gas inlet is shut off and the opening and closing member shuts off the liquefied gas inlet. When liquefied gas is supplied through the flow path, the opening and closing member is opened by the supply pressure of the liquefied gas. The compressor moves in the compression direction to open the liquefied gas intake port, allowing the liquefied gas to enter the intake valve. The pressure is supplied to the internal space.

[0018] The discharge valve is located in the discharge chamber, and a spring member is provided on the lower end side of the discharge valve. The compression and restoration of the spring member allows the discharge valve to move linearly back and forth, An auxiliary chamber having a certain space is provided around the upper end side of the discharge valve. The liquefied gas discharged from the suction valve is passed through the auxiliary chamber and the discharge inlet pipe. It is supplied sequentially through the inlet pipe to the outlet valve.

[0019] The discharge valve is positioned so as to block the suction valve exhaust pipe when the spring member is restored. When the spring member moves in the compression direction, a space is formed on the upper end side of the discharge chamber. The suction valve discharge pipe is opened, and the discharge valve moves to create space at the top of the discharge chamber. When the discharge chamber is formed, the upper end space of the discharge chamber is spatially connected to the suction valve exhaust pipe. The liquefied gas discharged through the suction valve discharge pipe is connected to the auxiliary chamber. through the upper end space of the discharge chamber, through the auxiliary chamber and the discharge inlet pipe, Supplied.

[0020] When liquefied gas is discharged through the suction valve, the acting pressure of the piston The supply pressure of the liquefied gas supplied to the gas supply passage is greater than the pressure of the liquefied gas intake port. So it is blocked.

[0021] The outer side of the integral connecting member is provided with a protective cover to protect the integral connecting member and to prevent the integral connecting member from moving. A cam roller drive shaft case is further provided, and the cam roller drive shaft case A cut-off bolt insertion hole through which the cut-off bolt passes is provided on one side of the A cut-off bolt insertion device that allows the cut-off bolt to be inserted to a certain depth on one side of the connecting member. A groove is provided, and the cut-off bolt is cut off when it is inserted through the cut-off bolt insertion hole. The bolt is inserted into the cutoff bolt groove, and the cam nose and cam roller are aligned. Separation of the nuclei is induced.

[0022] The center of the cutoff bolt insertion hole and the center of the cutoff bolt insertion groove are spaced apart. The cutoff bolt is based on the piston being positioned vertically on the camshaft. The center of the insertion groove is located slightly lower than the center of the cutoff bolt insertion hole, The bolt insertion groove has a tapered shape in which the radius decreases as the depth increases. The difference between the inlet radius and the bottom radius of the cutoff bolt insertion groove is "d".

[0023] The cut-off bolt that has passed through the cut-off bolt insertion hole is inserted into the cut-off bolt insertion groove. During the process of insertion, the cutoff bolt hits the tapered side of the cutoff bolt insertion groove. The cut-off bolt moves inward along the side of the cut-off bolt insertion groove. As the cutoff bolt moves inward, the cutoff bolt is inserted into the cutoff bolt insertion groove. The integral connecting member having the groove moves upward, and the cam roller moves away from the cam nose. can be.

[0024] When one end of the cutoff bolt abuts against the bottom surface of the cutoff bolt insertion groove, the integrated connection part The material is moved upward by the length "d", which is the difference in radius between the inlet side and the bottom side of the cutoff bolt insertion groove. The cam roller and the cam nose move apart by a distance "d".

[0025] The outer side of the integral connecting member is provided with a protective cover to protect the integral connecting member and to prevent the integral connecting member from moving. A cam roller drive shaft case is further provided, and the cam roller drive shaft case A cutoff pin guide member having a hollow cylindrical shape is provided on one side of the cutoff pin. The cutoff pin is inserted in the guide member so as to be movable up and down. A cutoff pin guide groove is provided on one side of the cutoff member, and the cutoff pin guide groove is spatially The vertical guide groove is divided into a vertical guide groove and a horizontal guide groove which are connected to each other. The horizontal guide groove extends from the first point to the second point of the vertical guide groove. The cut-off pin is attached to one side of the cut-off pin. A guide pin is provided, and the cutoff pin guide pin is located in 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 the cutoff pin is moved, the cutoff pin moves down by the corresponding distance and the cutoff pin guide pin moves When the pin guide groove is moved horizontally from the second point to the third point, the cutoff pin moves from the second point to the third point. Rotate the cutoff pin by the angle between the three points, and the bottom of the cutoff pin has a smaller radius than the cutoff pin. The cam roller separation protrusion is provided with a cylindrical shape having a cutout at the center thereof. The cut-off pin guide pin is eccentric to the center of the cut-off pin. When the cutoff pin is moved horizontally from the second point to the third point of the guide groove, the cover on the bottom of the cutoff pin The roller separation protrusion rotates at a certain angle.

[0026] A cutoff pin is inserted into one side of the cam roller drive shaft case. The cut-off pin is inserted into the integral connecting member, which is fitted with a cam roller separation guide. When the cutoff pin guide pin is located at the second position, the cutoff pin The cam roller separation protrusion at the lower end of the cam is positioned within the cam roller separation guide groove of the integrated connecting member, In the cam roller separation guide groove, the cam roller separation protrusion is not in contact with the integral connecting member. When the cutoff pin protrusion is moved from the second point to the third point of the cutoff pin guide groove, The cutoff pin rotates horizontally, and the cam roller separation protrusion rotates horizontally to connect the integral connecting member. The cam roller separation protrusion moves the integral connecting member. The cam roller and the cam nose are spaced apart.

[0027] Coupling case, a coupling case that is provided at the connection part between the drive shaft and the piston The piston is connected to the drive shaft and fixed in the inner space of the base, or the drive shaft and the piston are connected to each other. A rack member connected to and fixed on the outer surface of the rack member, and a tooth-shaped rack a pinion provided on the other side of the pinion to provide a driving force to the pinion; and a pinion guide member for transmitting the When the pinion is rotated counterclockwise, the drive The rack member connected to the shaft moves upward, and the upward movement of the rack member causes the cam The cam roller is spaced apart.

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

[0029] A drive shaft is provided between the drive shaft and the piston to selectively apply the driving force of the drive shaft to the piston. and a pressure chamber for applying pressure to the pressure chamber, the amount of lubricating oil being adjusted by adjusting the amount of lubricating oil in the pressure chamber. This makes it possible to control the amount of liquefied gas discharged from the liquefied gas compression device.

[0030] A first surface of the pressure chamber abuts against the drive shaft, and a second surface of the pressure chamber abuts against the piston. 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 by

[0031] With the pressure chamber filled with lubricant, the driving force of the drive shaft is applied to the first When the force is applied to the surface, the drive shaft is driven by the lubricant in the pressure chamber. The pressure of the piston is transmitted to the liquefied gas compressor, and the liquefied gas is discharged. .

[0032] When there is no lubricant 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 to the pressure chamber, the first surface of the pressure chamber moves to the second surface side because the pressure chamber is empty space. The length of the drive shaft that moves with the camshaft drive changes between the first and second faces of the pressure chamber. If the length between the faces is smaller than the distance between the faces, the driving force of the drive shaft will not be transmitted to the second face of the pressure chamber. Therefore, the liquefied gas compressor does not discharge liquefied gas.

[0033] The pressure chamber is filled with lubricant and the lubricant in the pressure chamber flows through the lubricant supply passage. When the drive force of the drive shaft is applied to the first surface of the pressure chamber, the pressure As the lubricant in the force chamber is discharged, the first surface moves by the amount of the discharged lubricant, and the drum Of the total stroke length Ds of the drive shaft, the length of the pressure chamber for discharging the lubricating oil is When no longer being powered, the piston travels through the pressure chamber for the entire stroke length Ds. It will move only the scroll length minus the length for which the oil is discharged.

[0034] A lubrication valve that allows the supply of lubricant to or the discharge of lubricant from the pressure chamber. The lubricant supply passage and the amount of lubricant supplied to the pressure chamber and the amount of lubricant discharged from the pressure chamber are It may further include a lubricant supply device for setting the amount of lubricant. Effect of the Invention

[0035] The gas supply pump for a marine dual fuel engine according to the present invention has the following advantages.

[0036] Each cylinder of the high pressure pump can be independently driven and controlled. This allows for redundant pumps in case a particular cylinder fails or requires service. There is no need to install.

[0037] In addition, the moment of inertia caused by the rotation of the camshaft acts on the drive shaft and piston. The impact of the liquefied gas valve can be minimized, and the valve is composed of an intake valve and an exhaust valve. The compressor can effectively compress the liquefied gas and prevent the backflow of the liquefied gas. can.

[0038] In addition, the optimum sealing structure in the area where the piston moves prevents the liquefied gas from entering the This prevents cavitation caused by the inflow of gas and prevents overheating of the internal space of the cylinder. It can be effectively suppressed. [Brief description of the drawings]

[0039] [Figure 1] FIG. 2 is a perspective view of a gas supply pump for a marine dual fuel engine in accordance with one embodiment of the present invention. [Diagram 2] 2 is a cross-sectional view taken along line AA' in FIG. [Figure 3a] FIG. 11 is a reference diagram for explaining the linear reciprocating motion of a cam roller according to the position of a cam nose. [Figure 3b] FIG. 11 is a reference diagram for explaining the linear reciprocating motion of a cam roller according to the position of a cam nose. [Figure 4] FIG. 4 is a reference diagram showing a connection portion between a drive shaft and a piston. [Diagram 5] FIG. 4 is a perspective view showing a connecting portion between a drive shaft and a piston. [Figure 6] FIG. 1 is a configuration diagram of a liquefied gas compression device. [Figure 7] FIG. 2 is a perspective view of a liquefied gas compression device. [Figure 8] FIG. 11 is a reference diagram showing a state in which the opening / closing member of the intake valve is open. [Figure 9a] FIG. 11 is a reference diagram for explaining the operation of a discharge valve. [Figure 9b] FIG. 11 is a reference diagram for explaining the operation of a discharge valve. [Figure 10] FIG. 11 is a reference diagram showing the cylinder side sealing structure and the rod side sealing structure. [Figure 11a] FIG. 13 is a perspective view of the sealing structure on the cylinder side. [Figure 11b] FIG. 13 is a perspective view of the sealing structure on the cylinder side. [Figure 12] FIG. 13 is a perspective view of the rod side sealing structure. [Figure 13] FIG. 4 is a reference diagram for explaining the separation between the cam roller and the cam nose when the cutoff bolt of the first embodiment is used. [Figure 14] FIG. 4 is a reference diagram for explaining the separation between the cam roller and the cam nose when the cutoff bolt of the first embodiment is used. [Figure 15] FIG. 11 is a reference diagram for explaining the separation between the cam roller and the cam nose when a cutoff pin is used in the second embodiment. [Figure 16] FIG. 11 is a reference diagram for explaining the separation between the cam roller and the cam nose when a cutoff pin is used in the second embodiment. [Figure 17a] 13A to 13C are reference views showing the separation operation of the cam roller and the cam nose according to the second embodiment. [Figure 17b] 13A to 13C are reference views showing the separation operation of the cam roller and the cam nose according to the second embodiment. [Figure 17c] 13A to 13C are reference views showing the separation operation of the cam roller and the cam nose according to the second embodiment. [Figure 18] FIG. 13 is a reference diagram for explaining the separation between the cam roller and the cam nose when the rack and pinion of the third embodiment is used. [Figure 19] FIG. 1 is a diagram showing the configuration of a gas supply pump to which a pressure chamber is applied. [Figure 20a] 11 is a reference diagram for explaining a method of separating a drive shaft from a piston using a pressure chamber. FIG. [Figure 20b] 11 is a reference diagram for explaining a method of separating a drive shaft from a piston using a pressure chamber. FIG. [Figure 20c] 11 is a reference diagram for explaining a method of separating a drive shaft from a piston using a pressure chamber. FIG. [Figure 21] FIG. 2 is a system diagram of a gas supply pump. [Figure 22] 11 is a graph showing the pulsation of the discharge pressure according to the number of pistons. [Diagram 23] 6 is a graph showing pulsation of the discharge pressure according to the phase of the cam nose. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0040] The present invention provides a technique for a high-pressure pump in which each cylinder can be driven independently. The high-pressure pump serves to supply high-pressure gas to the dual fuel engine and FGSS (fuel gas supply system) that supplies high pressure gas to the fuel engine em).

[0041] The high-pressure pump has multiple cylinders and injects high-pressure gas through each cylinder. Each cylinder must be prepared for failure or inspection, and if a particular cylinder fails, If a particular cylinder needs to be inspected, only that cylinder should be inspected. It is efficient to keep the remaining cylinders operating normally. As mentioned in the "Background Art" section, in the case of the high pressure pump according to the prior art, one crank The shaft is equipped with multiple cylinders, each of which is fitted with a connecting rod and a piston. Since the cylinders are connected to each other, it is not possible to control the drive of each cylinder independently. .

[0042] The present invention allows independent drive control for each cylinder of the high pressure pump. Specifically, the present invention provides a technology that can be used to provide a camshaft with multiple cylinders, A technique is presented that allows selective control of the actuation of each cylinder.

[0043] In addition, the present invention is characterized in that the moment of inertia of the camshaft is proportional to the drive shaft and the piston. We propose the optimal connection structure between the drive shaft and piston that can minimize the impact on the piston. The present invention also provides a liquefied gas compressor comprising a suction valve and a discharge valve. Presenting a technology that can effectively compress liquefied gas while preventing backflow of liquefied gas Furthermore, the present invention provides an optimal sealing structure in the area where the piston moves. This prevents cavitation caused by the inflow of liquefied gas and reduces the internal space of the cylinder. The present invention presents a technology that can effectively suppress overheating between the power supply and the power source.

[0044] Hereinafter, a gas supply port of a marine dual fuel engine according to an embodiment of the present invention will be described with reference to the accompanying drawings. I will now explain the pump in detail.

[0045] Referring to FIG. 1 and FIG. 2, a gas turbine engine for a marine dual fuel engine according to an embodiment of the present invention is The supply pump includes a camshaft, a cam roller 30, a drive shaft 40, a piston 50, and a liquefier The gas compressor comprises:

[0046] The rotational motion of the camshaft 10 induces the linear reciprocating motion of the drive shaft 40 and the piston 50. The pressure generated by the linear reciprocating motion of the piston 50 is applied to the liquefied gas compressor, and the liquefied gas pressure This is a method in which liquefied gas is discharged at high pressure using a compressor.

[0047] The camshaft 10 is rotated by the power of a driving means. A plurality of cam noses (cam noses) are provided at regular intervals along the longitudinal direction of the camshaft 10. A drive shaft 40 is provided for each cam nose 20. The drive shaft 40 is provided perpendicular to the longitudinal direction of the camshaft 10. A cam roller 30 is provided between the drive shaft 40 and the cam roller 30. A plurality of drive shafts 40 are arranged in a direction perpendicular to the camshaft 10. A cam roller 30 is provided between the cam nose 20 and the drive shaft 40.

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

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

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

[0051] In addition, a drive shaft 40 and a piston 50 are connected adjacent to one side of the cam roller 30. When the cam roller 30 moves linearly back and forth, the drive shaft 40 and the piston 50 also move linearly back and forth. It moves back and forth in a straight line.

[0052] Specifically, as shown in FIG. 3a, the rotation of the camshaft 10 causes the cam nose 20 When the cam roller 30 is positioned at an angle of 90 degrees with respect to the vertical direction, the pressure of the piston 50 As shown in FIG. 3b, the cam nose is moved in the contraction direction by the rotation of the camshaft 10. When the cam roller 20 is positioned at an angle of 270 degrees, the cam roller 30 moves the piston 50 in the compression release direction. In this way, when the camshaft 10 rotates, the cam roller 30 moves within a certain distance. The distance that the cam roller 30 moves back and forth in a straight line is the distance that the cam nose 20 moves back and forth at an angle of 90 degrees. This corresponds to a position between when the cam nose 20 is positioned at an angle of 270 degrees and when the cam nose 20 is positioned at an angle of 270 degrees. When the cam nose 20 is positioned at an angle of 270 degrees, the cam roller 30 contacts the piston 50. The movement in the compression release direction is made possible by a compression spring 120, which will be described later. In the specification, the compression direction of the piston 50 refers to the direction in which the piston 50 moves inwardly of the cylinder 80. The compression release direction of the piston 50 means the direction in which the piston 50 moves out of the cylinder 80. It means the direction of movement towards

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

[0054] The cam roller 30 and the drive shaft 40 are integrally connected by an integral connecting member 110. One end of the compression spring 120 is fixed to the integral connecting member 110. The connecting member 110 is hollow, and a cam roller 30 is attached to one end of the integral connecting member 110. The drive shaft 40 is attached to the other end of the housing, and the housing is provided in such a way as to surround the drive shaft 40. A compression spring 120 is secured to the inside of the integral connecting member 110 .

[0055] In this manner, the cam roller 30, the drive shaft 40 and the integral connecting member 110 are integrally connected. Since the camshaft 10 is connected to the cam nose 20, the camshaft 10 is in close contact with the cam nose 20 when the camshaft 10 rotates. Not only the roller 30 but also the drive shaft 40 and the integral connecting member 110 move linearly back and forth. These movements cause the compression spring 120 to compress and return to its original state. Or something like that.

[0056] Meanwhile, a cam roller drive shaft case 130 is provided on the outer side of the integrated connecting member 110. The cam roller drive shaft case 130 is provided with the integral connecting member 110 and the compression spring 12. 0 from the external environment and to prevent the movement of the integral connecting member 110 and the compression spring 120. It plays the role of guiding.

[0057] The drive shaft 40 and the piston 50 are coupled in the following manner.

[0058] Since the piston 50 is a device designed to move linearly back and forth within the cylinder 80, The direction of the force applied to the piston 50 must exactly match the linear reciprocating motion of the piston 50. The direction of the force applied to the piston 50 is the same as the direction of the linear reciprocating motion of the piston 50. If not, this means that some of the force applied to the piston 50 is lost, and This means that the linear reciprocating motion of the piston 50 is obstructed.

[0059] On the other hand, the force applied to the piston 50 is the linear reciprocating motion of the drive shaft 40. The linear reciprocating motion of the shaft 40 is induced by the rotational motion of the camshaft 10. The camshaft rotates in the process of converting the rotational motion of the shaft 10 into the linear reciprocating motion of the drive shaft 40. The moment of inertia of the drive shaft 10 acts on the drive shaft 40 and interferes with the linear reciprocating motion of the drive shaft 40. The moment of inertia refers to the rotational inertia that accompanies the rotary reciprocating motion of the cam roller. In order to prevent this rotational inertia from affecting the reciprocating motion of the piston, To achieve this, an inertia moment buffer member 230 is provided.

[0060] The coupling structure of the drive shaft 40 and the piston 50 according to the present invention is the above-mentioned camshaft 10. The design was made with the moment of inertia of the camshaft 10 in mind. The drive shaft 40 and the pin are connected so that the effect of the moment of inertia on the drive shaft 40 is minimized. Stone 50 has the optimal bonding structure.

[0061] Specifically, referring to FIG. 4 and FIG. 5, a certain space is provided on one end of the drive shaft 40. The first storage section 210 is provided with a drive shaft 4. 0, and the second storage portion 220 is provided facing the outside of the drive shaft 40. The diameter of the second storage portion 220 is larger than the diameter of the first storage portion 210. The diameter corresponds to the diameter of the piston 50 .

[0062] The first receiving portion 210 is provided with an inertia moment buffer member 230. The exposed surface of the buffer member 230 is in close contact with the piston 50. One surface of the inertia moment buffer member 230 that is attached to the base 21 has a gently convex shape with a large radius of curvature. Eggplant.

[0063] One surface of the inertia moment buffer member 230 that comes into close contact with the piston 50 is formed with a large radius of curvature. The reason for designing the gradual convex shape is to reduce the moment of inertia of the camshaft 10 on the drive shaft 40. When a torque is applied, the moment of inertia applied to the drive shaft 40 acts on the piston 50. The moment of inertia applied to the drive shaft 40 is the inertia moment. The force is distributed by the convex surface of the force buffer member 230 and applied to the piston 50. The moment of inertia applied to the tons 50 is minimized.

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

[0065] In addition, a protective cover is provided at the joint between the drive shaft 40 and the piston 50 to protect the joint. A clamp 250 may be provided, i.e., a two-piece clamp 250 member may be secured together with a bolt or the like. By fastening the drive shaft 40 and the piston 50, the joint portion between the drive shaft 40 and the piston 50 can be protected from the external environment. do.

[0066] The piston 50 moves linearly back and forth within the cylinder 80. As a result, pressure is applied to the liquefied gas compressor. The liquefied gas compressor is operated by a piston 50. This is a device that uses the pressure applied to discharge liquefied gas at high pressure.

[0067] As shown in FIG. 6 and FIG. 7, the liquefied gas compressor includes a liquefied gas supply passage 320, a suction It comprises a valve 60 and a discharge valve 70.

[0068] The liquefied gas supply passage 320 is a passage that supplies the liquefied gas to the suction valve 60. One end of the supply flow path 320 is connected to a liquefied gas supply port 310 provided on one side of the gas supply pump. The other end is connected to a liquefied gas intake port 62 provided on one side of an intake valve 60. The liquefied gas to be compressed is liquefied through a liquefied gas supply port 310 and a liquefied gas supply passage 320. The gas is supplied to the internal space of the intake valve 60 through the intake port 62. The liquefied gas supply passage 320 is connected to the housing of the suction valve 60 which surrounds the suction valve 60. It is formed into a ring.

[0069] An opening / closing member 61 is provided around the intake valve 60 to selectively open and close the liquefied gas intake port 62. The opening and closing member 61 is connected to a spring member 63 provided around the lower end side of the intake valve 60. The spring member 63 is compressed and restored, allowing for linear reciprocating motion. 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 restoration direction due to the restoration of 63, the liquefied gas intake port 62 is blocked. The spring member 63 is compressed and restored by the force acting on the opening and closing member 61. .

[0070] With the opening / closing member 61 blocking the liquefied gas intake port 62, When liquefied gas is supplied, the piston 50 moves back and the pressure in the internal space of the intake valve 60 increases. When the force becomes smaller than the supply pressure of the liquefied gas, the opening and closing member 61 moves in the compression direction of the spring member 63. As a result, the liquefied gas intake port 62 is opened, and the liquefied gas flows into the intake valve 60. In this manner, the liquefied gas is supplied from the liquefied gas supply passage 320 to the suction valve 60. A chemical gas is supplied.

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

[0072] Discharge valve 70 is located within discharge chamber 71. 1, it moves linearly back and forth for a certain distance by applying pressure. The intake valve 60 is provided with a spring member 75, and the spring member 75 is compressed and restored. The discharge valve 70 is allowed to move linearly back and forth. The compression and restoration of the spring member 75 causes the discharge valve 70 to move linearly back and forth. 0, and the force acting on the discharge valve 70 is determined by the pressure of the piston 50. This is the pressure of the liquefied gas discharged from the intake valve 60.

[0073] The discharge valve 70 is positioned so as to block the suction valve exhaust pipe 60a when the spring member 75 is restored. When the discharge valve 70 moves in the compression direction of the spring member 75, the upper A space is formed at the end of the discharge pipe 60a, and the discharge pipe 60a is opened. An auxiliary chamber 72 having a certain space is provided around the upper end side of the chamber 71. 72 is connected to a space formed on the upper end side of the discharge chamber 71 and is connected to the discharge valve 7 0 is also connected to a discharge inlet pipe 73 provided on one side of the

[0074] That is, a space is formed on the upper end side of the discharge chamber 71 by the movement of the discharge valve 70. When this happens, the space is spatially connected to the intake valve exhaust pipe 60a and the auxiliary chamber 7 2. In addition, since the auxiliary chamber 72 is structured to be connected to the discharge inlet pipe 73, The liquefied gas discharged through the suction valve discharge pipe 60a is discharged into the space 7 at the upper end of the discharge chamber. 4 and is supplied 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 FIG. 9a), When the pressure of the tons 50 acts, the liquefied gas in the intake valve 60 flows through the intake valve exhaust pipe 60a. At this time, the pressure of the liquefied gas discharged through the suction valve discharge pipe 60a is The pressure is applied to the discharge valve 70. The spring 70 moves in the compression direction of the spring member 75, thereby A space 74 is formed on the upper end side of the intake valve 1, and liquefied gas is discharged through the intake valve exhaust pipe 60a. is moved to the auxiliary chamber 72 through the space 74 on the upper end side of the discharge chamber 71 (FIG. 9b Since the auxiliary chamber 72 is connected to the discharge suction pipe, The liquefied gas in the discharge suction pipe is supplied to the internal space, and finally the pressurized liquefied gas It is discharged to the outside via the discharge valve 70.

[0076] The movement of the piston 50 in the decompression direction causes the liquefied gas in the intake valve 60 to enter the intake valve When the discharge through the discharge pipe 60a is no longer possible, the discharge chamber 71 is restored by the spring member 75. Then, the space 74 on the upper end side of the discharge chamber 71 disappears, and the discharge chamber 71 returns to its original state. The chamber 71 now blocks the intake valve exhaust pipe 60a.

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

[0078] In addition, when the liquefied gas is discharged through the suction valve discharge pipe 60a, the piston The working pressure of 50 is much higher than the supply pressure of the liquefied gas supplied to the liquefied gas supply passage 320. Because it is large, the liquefied gas intake port 62 is blocked by the opening and closing member 61 .

[0079] As described above, the pressure of the piston 50 moving linearly back and forth in the cylinder 80 The gas pressure is applied to the liquefied gas pressure device through the intake valve 60 and the discharge valve 70 of the liquefied gas pressure device. Liquefied gas is discharged under high pressure.

[0080] On the other hand, in the process of pressurizing and discharging the liquefied gas by the liquefied gas pressure device, The liquefied gas of the device enters the inside of the cylinder 80 through a minute gap between the piston 50 and the cylinder 80. If the inflow of liquefied gas is blocked by sealing, The pump efficiency is increased by discharging the liquefied gas without leakage. However, the sealing When the inflow of the liquefied gas is blocked by the piston, the liquefied gas that has flowed into the internal space of the cylinder 80 is Cavitation caused by frictional heat during linear reciprocating motion of the 50 This induces the formation of pits and causes mechanical damage to the piston 50, the cylinder 80, the drive shaft 40, etc. This can sometimes result in

[0081] Therefore, it is possible to completely block the inflow of liquefied gas into the internal space of the cylinder 80 or to partially block the inflow of liquefied gas into the internal space of the cylinder 80. There are pros and cons to each type of tolerance.

[0082] The present invention provides a seal for the piston 50 that blocks or allows the inflow of liquefied gas. ng) A method to increase the efficiency of the pump by structure and the inflow of liquefied gas This paper presents a method to prevent the occurrence of cavitation due to the above-mentioned reasons.

[0083] The sealing structure of the piston 50 is roughly divided into the cylinder side and the rod side. The sealing structure on the inner side is a sealing structure provided on the piston 50 inserted into the cylinder. The sealing structure on the rod side is the piston part that is not inserted into the cylinder 80, i.e. That is, it is a sealing structure provided on the rod.

[0084] In the present invention, the sealing structure on the cylinder side is designed to allow a certain amount of liquefied gas to flow in. The rod side sealing structure is designed to prevent the inflow of liquefied gas and other substances. Furthermore, the present invention provides a sealing structure on the cylinder side and a sealing structure on the rod side. Both are presented with configurations that prevent the inflow of liquefied gas and other substances.

[0085] In the case of the cylinder side sealing structure, as shown in Fig. 10 and Fig. 11a, the cylinder 8 The spring member receiving groove 51a and the guide ring 51b are spatially connected around the piston portion inserted in the piston rod 50. The spring member receiving groove 51a and the guide ring receiving groove 51b are provided. It has a stepped shape, and the width of the guide ring receiving groove 51b is designed to be wider than the width of the spring member receiving groove 51a. A spring member 410 having a hollow shape and elasticity is attached to the spring member receiving groove 51a. In the guide ring receiving groove 51b adjacent to the spring member receiving groove 51a, a strip-shaped plate-shaped guide ring is provided. The width of the spring member 410 accommodated in the spring member accommodation groove 51a is equal to the guide The width is narrower than the width of the guide ring 420 that is accommodated in the guide ring accommodation groove.

[0086] The guide ring 420 guides the movement of the piston 50 when the piston reciprocates within the cylinder. The spring member is inserted into the spring member receiving groove 51a while contacting the guide ring 420. The screw member 410 serves to buffer the force applied to the guide ring when the piston 50 moves. The spring member 410 keeps the position of the guide ring 420 constant. As a result, the movement of the piston 50 can be stably guided.

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

[0088] The cylinder side system is composed of the guide ring 420 and the spring member 410 as described above. The ring structure is designed to allow a certain amount of liquefied gas to flow in, and such a design is This is a configuration for effectively preventing overheating of the internal space of the heater 80.

[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 the structure so that it does not allow the inflow of liquefied gas. The sealing structure on the cylinder side is not suitable for the original purpose of sealing. I can say.

[0090] The cylinder side sealing structure that does not allow the inflow of liquefied gas is shown in detail in Figure 11b. As shown in the figure, the piston seal 430 is a guide ring 420. Specifically, a guide ring receiving groove is provided along the circumference of the piston portion, and the guide ring receiving groove is A band-shaped plate-like guide ring 420 is attached in the guide ring receiving groove. A piston seal receiving groove is provided around the piston portion at a longitudinally spaced position. A piston seal 430 is fitted in the piston seal receiving groove.

[0091] The guide rings 420 are arranged on the left and right sides of the piston seal 430. The piston seal 430 is a piston 50 that is inserted into the piston 50. It plays a role in suppressing the inflow of bacteria.

[0092] The piston seal 430 is configured as follows in detail. The contact member 43 is composed of a contact member 431, a spring member 432, and a stopper 433. 1. The spring member 432 and the stopper 433 are formed to surround the piston 50.

[0093] The contact member 431 has one surface that is in contact with the outer surface of the piston 50 and the other surface that is in contact with the inner surface of the cylinder 80. The spring member 432 is in close contact with the wall and has a receiving groove in which the spring member 432 can be received. The spring member 432 is inserted in the receiving groove of the contact member 431 and the contact member 431 is supported by the restoring force of the spring member 432. It serves to apply a force to the outer surface of the stone 50 and the inner wall of the cylinder 80 so that the stone 50 and the inner wall of the cylinder 80 are in close contact with each other. The combination of the attachment member 431 and the spring member 432 allows the liquefied gas to flow from one side of the cylinder to the other. The stopper 433 is formed by sealing the spring member 432. This prevents the mounting member 431 from coming out of the receiving groove.

[0094] Next, looking at the sealing structure on the rod side, 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 Air, foreign matter, and other substances that may enter through the joint between the drive shaft 40 and the piston 50 Designed to prevent quality influx.

[0095] A piston cover 52 is disposed around the rod portion of the piston 50, The piston cover 52 is fitted with a rod seal 520, a guide ring 510 and a 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 drive shaft 40 direction. , adjacent to the rod seal 520 and the wiper seal 530, respectively, the piston cover 52 A guide ring is disposed on the rod portion, and the guide ring is positioned toward the inside of the rod portion. The wiper seal 53 is attached to the piston cover 52 from the drive shaft 40 to the cylinder 80. 0, a guide ring, a guide ring, and a rod seal 520 are arranged in this order.

[0096] The wiper seal 530 is adapted to prevent air, foreign matter, and other substances from entering from the drive shaft 40 direction. The rod seal 520 prevents the inflow of liquefied gas from the cylinder 80 side. The guide ring also serves to prevent the rod portion from moving on the piston cover 52. It serves as a guide for the above.

[0097] The rod seal 520 and wiper seal 530 are applied to the sealing structure on the cylinder side. The piston seal has the same structure as the rod seal 520 and the wiper seal 53. Each of the piston seals 430 includes a sealing member 531, a spring member 532, and a stroke member 533. It consists of 533 pieces.

[0098] In addition, the guide ring 510 applied to the sealing structure on the rod side is the same as the sealing structure 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 serves to guide the movement of the rod part during reciprocating motion of the rod part. The spring member 511 is in contact with the guide ring 510 when the rod portion moves. The spring member 511 serves to buffer the force applied to the guide. The position of the ring 510 can be kept constant, and the movement of the rod part can be stably guided. It is possible.

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

[0100] As described above, the camshaft 10 is provided with a plurality of cam noses 20 spaced apart from each other. Each cam nose 20 is provided with a cam roller 30 in close contact therewith. 0 is connected to a drive shaft 40, a piston 50, a cylinder 80, and a liquefied gas compressor. This structure allows multiple liquefied gas compressions to be performed by the operation of one camshaft 10. The structure is such that the device can be operated.

[0101] Under such a structure, the driving of each of the plurality of cylinders 80, i.e., The drive of each liquefied gas compressor can be controlled independently. As a method for this purpose, the present invention forcibly separates the cam roller 30 from the cam nose 20, A drive shaft 40 connected to the spaced cam rollers 30, a piston 50, a cylinder 80, and We present a technology to stop the operation of a liquefied gas compressor. Specifically, we will demonstrate this technology through three examples. In the first embodiment, the cam roller 30 is cut using a cutoff bolt 140. The second embodiment uses a cutoff pin 620 to separate the lid from the lid 20. The cam roller 30 is spaced from the cam nose 20. The third embodiment is a rack-pinion type. This is a method of separating the cam roller 30 from the cam nose 20 by using the on 730.

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

[0103] 13 and 14, a cam roller drive shaft case 130 has a cup on one side. The cut-off bolt 140 is inserted through a cut-off bolt insertion hole 131. On one side of the member 110, a cutoff bolt 140 can be inserted to a certain depth. A bolt insertion groove 111 is provided.

[0104] The cut-off is performed when the cut-off bolt 140 is inserted through the cut-off bolt insertion hole 131. The bolt 140 is inserted into the cutoff bolt insertion groove 111, and the cam nose 2 0 and the cam roller 30 can be induced to separate.

[0105] The cam nose 20 and the cam roller 30 are spaced apart from each other, so that the camshaft 1 Even if the cam nose 20 is rotated, the cam roller 30 does not come into contact with the cam nose 20. The operation of the drive shaft 40 and the piston 50 connected to the drive shaft 30 can be stopped. In this manner, the drive of each piston 50 provided on the camshaft 10 is It can be selectively controlled.

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

[0107] The cutoff bolt insertion hole 131 and the cutoff bolt insertion groove 111 are arranged adjacent to each other. The centers of these shapes do not coincide with each other and are separated from each other.

[0108] The cam roller drive shaft case 130 is provided with a cutoff bolt insertion hole 131. In both cases, the integral connecting member 110 is provided with a cutoff bolt insertion groove 111, and the cutoff bolt The bolt 140 is inserted through the cutoff bolt insertion hole 131 and into the cutoff bolt insertion groove 111. The cutoff bolt insertion hole 131 and the cutoff bolt insertion groove 111 are the same. It may be designed by diameter.

[0109] At this time, the center of the cutoff bolt insertion hole 131 and the center of the cutoff bolt insertion groove 111 The piston 50 is arranged vertically on the camshaft 10. Based on this, the center of the cutoff bolt insertion groove 111 is the cutoff bolt insertion opening 13. The cutoff bolt insertion groove 111 is located slightly lower than the center of the cutoff bolt 1. The deeper the depth, the smaller the radius becomes. The radius of the inlet side and the radius of the bottom side of the cut-off bolt insertion groove 111 are different by "d" ( See Figure 14).

[0110] Under such conditions, the cutoff bolt inserted through the cutoff bolt insertion hole 131 The bolt 140 is inserted into the cutoff bolt insertion groove 111. The center of the cutoff bolt is located slightly lower than the center of the cutoff bolt insertion hole 131. Therefore, the cutoff bolt 140 is inserted into the cutoff bolt insertion groove 111 having a tapered shape. It comes into contact with the surface.

[0111] If you continue to screw in the cutoff bolt 140 in the insertion direction, the cutoff bolt The cut-off bolt insertion groove 111 is inserted into the cut-off bolt insertion groove 111 along the side of the cut-off bolt insertion groove 111. The cutoff bolt 140 moves further inward. The movement to the inside of the cutoff bolt insertion groove 111 is due to the fact that the cutoff bolt insertion groove 111 is provided This means that the body connecting member 110 moves upward.

[0112] In this manner, one end of the cutoff bolt 140 is inserted into the bottom of the cutoff bolt insertion groove 111. When the integral connecting member 110 abuts against the surface, the radius of the inlet side of the cutoff bolt insertion groove 111 and The cut-off bolt moves upward by the length "d", which is the difference in radius with the bottom radius. 40 may also have a tapered shape at certain portions for ease of insertion. In this case, the integral connecting member The travel distance of 110 is equal to the value obtained by subtracting the taper thickness of the cutoff bolt 140 from "d". Correct.

[0113] The above process allows the integral connecting member 110 to move upward by a length "d". This means that the cam nose 20 and the cam roller 30 are spaced apart by a distance "d". This principle is used to keep the cam nose 20 and the cam roller 30 apart. The distance between the cam nose 20 and the cam roller 30 causes the camshaft 10 to rotate. Even if the cam roller 30 is rotated, the drive shaft 40 and the piston 50 connected to the cam roller 30 do not move. stomach.

[0114] In the above, the cutoff bolt 14 is attached to one side of the cam roller drive shaft case 130. The cut-off bolt insertion hole 131 through which the cut-off bolt 130 is inserted is provided on one side of the integral connecting member 110. The cut-off bolt insertion groove 11 has a cut-off bolt 140 inserted therein to a certain depth. 1, the cut-off bolt insertion hole 131 and the cut-off bolt The position where the insertion groove 111 is provided is not specified. The cutoff bolt insertion hole 131 and the cutoff bolt insertion groove are provided in the space inside the cutoff bolt insertion hole 131. 111 may be provided (see Figs. 4a and 4b), which is located on the outside of the camshaft 10 case. The cut-off bolt insertion hole 131 and the cut-off bolt insertion groove 111 are provided at various places. This may also be the case.

[0115] The second embodiment utilizing the cutoff pin 620 is configured as follows.

[0116] 15 and 16, one side of the cam roller drive shaft case 130 is provided with an internal A cutoff pin guide member 610 having a hollow cylindrical shape is provided. A cutoff pin 620 is inserted into the material 610. The cutoff pin 620 is It can be raised and lowered within the toe-off pin guide member 610.

[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. The guide groove and the horizontal guide groove are spatially connected to each other. The vertical guide groove is a first ground on a vertical line. The horizontal guide groove extends from the second point of the vertical guide groove to the horizontal direction. The second and third points of the horizontal guide groove are at 0 degrees and 3 degrees, respectively. Preferably provided at the 180 degree point.

[0118] A cutoff pin guide pin 621 is provided on one side of the cutoff pin 620. The cutoff pin guide pin 621 is positioned in the cutoff pin guide groove 611. The cutoff pin guide pin 621 can move along the cutoff pin guide groove 611. The cutoff pin guide pin 621 is inserted from the first point of the cutoff pin guide groove 611. When the cut-off pin 620 moves vertically from the cut-off position to the second point, the cut-off pin 620 moves down the corresponding distance. The pin guide pin 621 is moved horizontally from the second point to the third point of the cutoff pin guide groove 611. When moved, the cutoff pin 620 moves by an angle between the second point and the third point, e.g., 1 Only rotate 80 degrees.

[0119] The bottom surface of the cutoff pin 620 is provided with a cylinder having a smaller radius than the cutoff pin 620. The center of the cam roller spacing protrusion 622 is a cup shape. The cutoff pin guide pin 621 is eccentric to the center of the circle of the cutoff pin 620. When the cut-off pin guide groove 611 is moved horizontally from the second point to the third point, the cut-off pin The cam roller separation protrusion 622 provided on the bottom surface of 620 also rotates at a certain angle, for example, 180 degrees. To rotate.

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

[0121] When the cutoff pin guide pin 621 is located at the second position, The cam roller spacing protrusion 622 at the end fits into the cam roller spacing guide groove 112 of the integrated connecting member 110. The cam roller spacing protrusion 622 is integrally connected to the cam roller spacing guide groove 112. It is not in contact with the member 110 (see FIG. 17a).

[0122] In this state, the protrusion of the cutoff pin 620 is inserted into the second guide groove 611 of the cutoff pin. When the cut-off pin 620 is moved from the first position to the third position, the cut-off pin 620 rotates horizontally, and the cam The roller spacing protrusion 622 also rotates horizontally, so that the cam roller spacing protrusion 62 2 rotates horizontally at a certain angle within the cam roller separation guide groove 112 to form the integral connecting member 11 0 (see FIG. 17b). Then, the cam roller separation protrusion 622 abuts The integral connecting member 110 is physically pushed out. As the cam roller 30 moves, the cam roller 30 also moves together with the integral connecting member 110. Finally, the cam roller 30 and the cam nose 20 are separated (see FIG. 17c). .

[0123] Conversely, the cutoff pin guide pin 621 is inserted from the third point of the cutoff pin guide groove 611. When the one-piece connecting member 110 is moved from the first position to the second position, the one-piece connecting member 110 returns to its initial state, The cam roller 30 and the cam nose 20 are again in contact.

[0124] As previously mentioned, the cutoff pin 620 is used to separate the cam nose 20 and the cam The distance between the cam nose 20 and the cam roller 30 is induced, and a specific distance is obtained by the distance between the cam nose 20 and the cam roller 30. The actuation of the pistons 50, and thus of particular cylinders 80, can be selectively controlled.

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

[0126] In the first and second embodiments, the integral connecting member 110 is provided with a cutoff bolt 140 or a cut The cam roller 30 is separated from the cam nose 20 by inserting the toe-off pin 620. In the third embodiment, the drive shaft 40 moves to rotate the cam roller 30. This is a method for inducing separation from the cam nose 20.

[0127] According to the third embodiment, as shown in FIG. 18, the drive shaft 40 and the piston 50 are connected. The coupling case 710 is further provided at the portion to be connected to the coupling member 710 in order to protect the coupling member 710 from the external environment. In addition, a rack and pinion 730 device operated by a hydraulic cylinder 80 is also provided. 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 one side of the drive shaft 40 and fixed thereto, or The drive shaft 40 and the piston 50 are connected and fixed to each other. When the drive shaft 40 moves, the rack member 720 also moves. When 20 moves, the drive shaft 40 and piston 50 also move.

[0129] The rack member 720 has a tooth-shaped rack on its outer surface. The rack of the rack member 720 is provided with a pinion 730 in meshing engagement therewith. As a result, the rack member 720 moves up and down in accordance with the rotation of the pinion 730. On the other side of the pinion 730, a pinion gear is provided to transmit a driving force to the pinion 730. A pinion guide member 740 is provided, and the pinion guide member 740 is selected by a hydraulic cylinder 80. The pinion guide member 740 also has a rack on its surface, and the pinion 7 30 meshes with the rack of the pinion guide member 740 .

[0130] Under such a structure, the pinion guide member 740 is lowered via the hydraulic cylinder 80. When the pinion 730 is moved in the opposite direction, the pinion 730 rotates counterclockwise. The rotation of the drive shaft 40 causes the rack member 720 connected to the drive shaft 40 to move upward. The upward movement of the member 720 means the upward movement of the drive shaft 40. The cam nose 20 and the cam roller 30 can be induced to move apart by the cam nose 20 and the cam roller 30. You will be able to do it.

[0131] The above is a description of the manner in which the cam roller 30 and the cam nose 20 are spaced apart from each other according to the first to third embodiments. On the other hand, the cam using the first to third embodiments as described above When the roller 30 and the cam nose 20 are separated, the cam nose 20 is in a positive contact with the cam roller 30. The cam roller 30 and the cam nose 20 must be moved away from each other in this state. A certain rotating gear may be provided for this purpose. The rotating gear finely adjusts the rotation of the camshaft 10. This allows adjustment so that the cam nose 20 faces the cam roller 30 directly.

[0132] The above-mentioned first to third embodiments induce the separation between the cam roller and the cam nose. This makes it 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 spaced apart. Therefore, when the cam roller and the cam nose are separated, the piston stops and liquefied gas is not discharged.

[0133] The present invention provides a technique for adjusting the discharge amount of liquefied gas. According to an example, the stroke length of the piston 50 is adjusted to control the liquefied gas discharge. The amount of discharge can be controlled.

[0134] Specifically, as shown in FIG. 19, a pressure chamber is provided between the drive shaft 40 and the piston 50. The pressure chamber 810 has a first surface 811 that abuts against the drive shaft 40 and is Another second surface 812 of the force chamber 810 forms a fixed abutment with the piston 50. Therefore, when the drive shaft 40 moves toward the piston 50, the pressure chamber 810 The driving force of the drive shaft 40 is applied to the first surface 811 and transmitted to the pressure chamber 810 . At this time, if the pressure chamber 810 is filled with lubricating oil, the drive shaft 40 is driven. The power should be transmitted directly to the piston 50 via the pressure chamber 810 (first In the first case, when the pressure chamber 810 is an empty space, the driving force of the drive shaft 40 is a pressure In the second case, the pressure When the driving force of the drive shaft 40 is applied with the chamber 810 filled with lubricant, When the lubricating oil in the pressure chamber 810 is partially discharged, only a part of the driving force of the drive shaft 40 is It should be transmitted to the piston 50 (third case).

[0135] One embodiment of the present invention uses the above-mentioned principle to stop the discharge of liquefied gas or to discharge the liquefied gas. The discharge amount can be controlled.

[0136] Here, a lubricant supply passage 830 is provided on one side of the pressure chamber 810. A supply of lubricating oil 820 to the pressure chamber 810 via an oil supply passage 830 or The lubricant 820 can be discharged from the drain 810. The lubricant supply passage 830 is also The lubricant supply 840 is connected to the pressure chamber 810. Set the amount of lubricant 820 dispensed and the amount of lubricant 820 discharged from the pressure chamber 810 It is possible.

[0137] The above-mentioned three cases will now be described in detail.

[0138] As shown in FIG. 20a, the pressure chamber 810 is filled with the lubricant 820, and the drum 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 of 0 is applied to the piston 50 through the lubricant 820 filled in the pressure chamber 810. Finally, the pressure of the piston 50 is transmitted to the liquefied gas compressor, and the normal liquefied gas is discharged. At this time, the lubricant supply passage 830 is blocked, and the lubricant supply to the pressure chamber 810 is stopped. The oil is not discharged to the outside.

[0139] On the other hand, when no lubricant 820 is present in the pressure chamber 810 as shown in FIG. When the driving force of the drive shaft 40 is applied to the first surface 811 of the pressure chamber 810, the pressure chamber Since the pressure chamber 810 is an empty space, the first surface 811 of the pressure chamber 810 is moved toward the second surface 812. At this time, the stroke length of the drive shaft 40 caused by the driving of the camshaft is changed by the pressure chamber. When the driving force of the drive shaft 40 is between the first surface 811 and the second surface 812 of the member 810, The pressure is not transmitted to the second surface 812 of the pressure chamber 810. Therefore, the camshaft is not driven. As a result, 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, in the third case, as shown in FIG. 20c, the lubricant is pumped into the pressure chamber 810. With the lubricant supply passage 830 open, the driving force of the drive shaft 40 is When a pressure is applied to the first surface 811 of the pressure chamber 810, the lubricant in the pressure chamber 810 The lubricating oil is discharged through the lubricating oil supply passage 830 and the first surface 811 moves toward the piston 50. At this time, the amount of lubricant discharged through the lubricant supply passage 830 is adjusted. By doing so, it is possible to control the moving distance of the first surface 811. The travel distance of 11 is determined by the lubricant discharged from the pressure chamber 810 through the lubricant supply passage 830. The amount of lubricant discharged from the pressure chamber 810 through the lubricant supply passage 830 is proportional to the amount of oil. By adjusting the amount of oil, the stroke length of the piston can be controlled.

[0141] The length of the total stroke length Ds of the drive shaft 40 that is the length of the lubricant discharged from the pressure chamber 810 Since no driving force is applied to the piston 50, the piston 50 also moves through the entire stroke. The stroke length is the stroke length obtained by subtracting the length of the pressure chamber 810 for discharging the lubricant from the stroke length Ds. In this way, the stroke length of the piston 50 is shortened. As a result, the amount of liquefied gas discharged through the liquefied gas compressor decreases compared to normal. .

[0142] As previously described, the pressure chamber 810 is set to a free space state to stop the discharge of liquefied gas. The pressure chamber 810 can be filled with lubricant 820 to allow the drive shaft 4 to rotate. The driving force of 0 is completely transmitted to the piston 50 to maintain the normal discharge of liquefied gas. The amount of lubricant discharged from the pressure chamber 810 can be adjusted accordingly. By this, it is possible to selectively control the amount of liquefied gas discharged from the liquefied gas compressor. Cut.

[0143] On the other hand, the gas supply pump according to the present invention has a plurality of pistons on one camshaft. Each piston is either of the cut-off type according to the first to third embodiments described above or They can be independently driven by the pressure chamber method described above.

[0144] The liquefied gas compressor linked to each piston rotates with the camshaft, The liquefied gas discharged through each liquefied gas compressor is integrated. They join together in the exhaust pipe and are finally supplied to the engine combustion chamber.

[0145] When liquefied gas is supplied to the engine combustion chamber through the integrated exhaust pipe, the liquefied gas is discharged. The discharge pressure pulsation (hereinafter referred to as "discharge pressure pulsation") occurs (see Figure 21). The discharge pressure pulsation of the liquefied gas supplied to the engine combustion chamber through the combined exhaust pipe is It has a physical effect on the engine, not just efficiency. If the discharge pressure pulsation is large, the combustion of the liquefied gas is This reduces combustion efficiency and puts a physical shock on the engine.

[0146] The discharge pressure pulsation of the liquefied gas depends on the number and the number of pistons that operate in conjunction with the camshaft. The more pistons in operation, the greater the displacement. When output pressure pulsation is reduced and the phases of the cam noses to which the pistons are connected are spaced equally apart It was confirmed through experiments that the discharge pressure pulsation was reduced.

[0147] Figures 22 and 23 show the discharge pressure pulsation according to the number of pistons and the phase of the cam nose. As shown in Figure 22, there are four pistons connected to a camshaft. In one case, when the number of pistons in operation is two, the discharge pressure pulsation is 7.5ba On the other hand, when the number of pistons in operation is three, the discharge pressure pulsation is 5.5 When the number of pistons in operation is four, the discharge pressure pulsation is 3.5 bar. It can be seen that the more pistons there are, the less the discharge pressure pulsation is. The more pistons there are, the more liquefied gas is compressed and discharged through each piston. This is because the discharge pressure pulsation is cancelled out.

[0148] Also, referring to FIG. 23, the phases of the cam noses are spaced equally and the phases of the cam noses are spaced apart. If there is no change and one piston is cut off, the number of pistons in operation will be two. When there are three cams, and when there are three cams, the phases of the cams are equally spaced. It can be seen that the output pressure pulsation is reduced. Specifically, there are three moving pistons and the cam nose When the phases are equally spaced, the discharge pressure pulsation is 5.5 bar, whereas when the cam nose position is If there is no phase change and one piston is cut off and three pistons are operated, the discharge The pressure pulsation increased to 10 bar. Also, the phase of the cam nose was shifted due to the two moving pistons. When the intervals are equal, the discharge pressure pulsation is 7.5 bar, whereas when the phase of the cam nose changes, If there is no discharge pressure pulse and one piston is cut off and two pistons are operated, The pressure increased to 10 bar.

[0149] As can be seen from the above, the more pistons that are linked to the camshaft drive, the When the phases of the cam noses are equally spaced, the discharge pressure pulsation can be reduced. .

[0150] In addition, from the experimental results mentioned above, the discharge pressure can be controlled by 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 is The number of pistons and the phase of the cam nose may be arranged taking into account the range of the discharge. If the upper limit of the allowable pressure pulsation range is 8 bar or less, the cam nose phase is arranged at equal intervals. The minimum number of pistons that may be placed and operated is two. [Explanation of symbols]

[0151] 10 Camshaft, 20 Cam nose, 30 Cam roller, 40 Drive shaft, 50 piston, 50a intake valve exhaust pipe, 51a spring member receiving groove, 51b guide ring receiving groove, 52 Piston cover, 60 Intake valve, 61 Opening and closing member, 62 liquefied gas intake port, 63 spring member, 70 discharge valve, 71 discharge chamber, 72 auxiliary chamber, 73 discharge inlet pipe, 74 discharge chamber upper end space, 75 spring member, 80 cylinders, 110 integral 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 hole, 132 Cut-off pin insertion hole, 140 Cut-off bolt, 210 first storage section, 220 second storage section, 230 inertia moment buffer member, 240 stopper, 250 clamp, 310 liquefied gas supply port, 320 liquefied gas supply passage, 410 spring member, 420 guide ring, 510 guide ring, 520 Rod Seal, 530 Wiper Seal, 610 cutoff pin guide member, 611 cutoff pin guide groove, 620 Cut-off pin, 621 Cut-off pin guide pin, 622 cam roller separation protrusion, 710 coupling case, 720 Rack member, 730 Pinion, 740 Pinion guide parts.

Claims

1. A camshaft capable of being driven in rotation; a plurality of cam noses spaced at regular intervals along the length of the camshaft and having an eccentric shape relative to the center of the camshaft; and a plurality of cylinder units for discharging liquefied gas, each of which is provided corresponding to each of the plurality of cam noses and discharges liquefied gas when the gas supply pump is driven; Each of the plurality of cylinder units is a cam roller provided in intimate contact with a corresponding cam nose; a drive shaft and a piston provided adjacent to one side of the cam roller; A cylinder in which the piston moves linearly back and forth within an internal space; and a liquefied gas compressor for compressing and discharging liquefied gas in accordance with the linear reciprocating motion of the piston; wherein the cam nose rotates and moves in accordance with the rotation of the cam shaft, causing the linear reciprocating motion of the piston; and a separation mechanism that separates the cam roller from the corresponding cam nose when the cam shaft rotates, and maintains a separated state between the cam roller and the cam nose such that a rotational driving force of the corresponding cam nose is not transmitted to the piston; A gas supply pump for a marine dual fuel engine, characterized in that the multiple cylinder units have a first cylinder unit and a second cylinder unit, and when the gas supply pump is driven, it is possible to control in parallel the driving of the first cylinder unit and the non-driving of the second cylinder unit by the isolation mechanism.

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

3. 2. The gas supply pump for a marine dual fuel engine as claimed in claim 1, wherein 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 in close contact with the cam nose moves linearly back and forth within a certain distance when the cam shaft rotates.

4. 2. A gas supply pump for a marine dual fuel engine as described in claim 1, wherein when the cam nose is positioned at a 90 degree angle based on the vertical direction due to the rotation of the cam shaft, 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 based on the vertical direction due to the rotation of the cam shaft, the cam roller moves in a direction in which the liquefied gas is decompressed by the piston.

5. Each of the plurality of cylinder units is An integral connecting member is further provided to integrally connect the cam roller and the drive shaft, The cam roller is accommodated in one end of the integral connecting member, the drive shaft is attached to the other end, and a compression spring is provided to surround the drive shaft and is fixed to the inside of the integral connecting member, 2. The gas supply pump for a marine dual fuel engine according to claim 1, wherein the cam roller in close contact with the cam nose and the drive shaft and the integral connecting member all reciprocate linearly when the camshaft rotates.

6. Each of the plurality of cylinder units is This is the part where the drive shaft and piston are connected. A first receiving portion and a second receiving portion are provided on one end side of the drive shaft to provide a certain space, the first receiving portion is located on the inner side of the drive shaft, and the second receiving portion is provided toward the outer side of the drive shaft, 2. The gas supply pump for a marine dual fuel engine according to claim 1, wherein the first housing is provided with an inertia moment buffer member, and one exposed surface of the inertia moment buffer 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; 7. The gas supply pump for a marine dual fuel engine as claimed in claim 6, wherein a stopper is fitted in a space between the second receiving portion and the piston, and the stopper is provided in close contact with an inner diameter of the piston and the second receiving portion to prevent the piston from rotating.

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

9. The liquefied gas compression device includes: a liquefied gas supply passage that supplies the liquefied gas to be compressed to the suction valve; a suction valve that draws in liquefied gas from a liquefied gas supply passage and supplies the drawn-in liquefied gas to a discharge valve side when a piston pressure is applied; 2. The gas supply pump for a marine dual fuel engine according to claim 1, further comprising a discharge valve for discharging the liquefied gas supplied from the suction valve under pressure.

10. One end of the liquefied gas supply passage is connected to a liquefied gas supply port provided on one side of the gas supply pump, and the other end is connected to a liquefied gas suction port provided on one side of the suction valve, The gas supply pump for a marine dual fuel engine as described in claim 9, characterized in that the liquefied gas to be compressed is supplied to the internal space of the intake valve through the liquefied gas intake port via the liquefied gas supply port and the liquefied gas supply passage.

11. An opening / closing member is provided around the suction valve to selectively open and close the liquefied gas suction port, and the opening / closing member is connected to a spring member provided around the lower end side of the suction valve and can perform 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 suction port is opened, and when the opening / closing member moves in the restoration direction as the spring member restores, the liquefied gas suction port is closed.

10. A gas supply pump for a marine dual fuel engine as described in claim 9, characterized in that when liquefied gas is supplied through the liquefied gas supply flow path while the opening / closing member is blocking the liquefied gas suction port, the opening / closing member moves in the compression direction of the spring member due to the supply pressure of the liquefied gas, opening the liquefied gas suction port, and supplying liquefied gas into the internal space of the suction valve.

12. the discharge valve is located within the discharge chamber; A spring member is provided at the lower end of the discharge valve, and the linear reciprocating motion of the discharge valve is enabled by the compression and restoration of the spring member. An auxiliary chamber having a certain space is provided around the upper end side of the discharge chamber, and a discharge inlet pipe is provided between the auxiliary chamber and the discharge valve, 10. The gas supply pump for a marine dual fuel engine as claimed in claim 9, wherein the liquefied gas discharged from the suction valve is supplied to the discharge valve through the auxiliary chamber and the discharge inlet pipe in sequence.

13. Each of the plurality of liquefied gas discharge cylinder units is A cam roller drive shaft case is further provided on the outside of the integral connecting member to protect the integral connecting member and to guide the movement of the integral connecting member, A cutoff bolt insertion hole through which the cutoff bolt is inserted is provided on one side of the cam roller drive shaft case, and a cutoff bolt insertion groove into which the cutoff bolt can be inserted to a certain depth is provided on one side of the integrated connecting member, 6. The gas supply pump for a marine dual fuel engine as claimed in claim 5, wherein the separation between the cam nose and the cam roller is induced by a 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 hole, thereby forming the separation mechanism.

14. The center of the cutoff bolt insertion hole and the center of the cutoff bolt insertion groove are spaced apart, and the center of the cutoff bolt insertion groove is located slightly lower than the center of the cutoff bolt insertion hole when the piston is vertically disposed on the camshaft, 14. The gas supply pump for a marine dual fuel engine as claimed in claim 13, wherein the cutoff bolt insertion groove has a tapered shape in which the radius decreases as the depth increases, and the taper shape causes a radius difference of "d" between an inlet side radius and a bottom side radius of the cutoff bolt insertion groove.

15. In the process of inserting the cutoff bolt through the cutoff bolt insertion hole into the cutoff bolt insertion groove, The cutoff bolt comes into contact with the side surface of the tapered cutoff bolt insertion groove and moves along the side surface of the cutoff bolt insertion groove into the inside of the cutoff bolt insertion groove, 14. The gas supply pump for a marine dual fuel engine according to claim 13, wherein the cutoff bolt is moved inwardly into the cutoff bolt insertion groove, and the integral connecting member having the cutoff bolt insertion groove is moved upward, so that the cam roller is separated from the cam nose.

16. Each of the plurality of cylinder units is A cam roller drive shaft case is further provided on the outside of the integral connecting member to protect the integral connecting member and to guide the movement of the integral connecting member, A cutoff pin guide member having a hollow cylindrical shape 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 movable up and down; A cutoff pin guide groove is provided on one side of the cutoff pin guide member, and the cutoff pin guide groove is divided into a vertical guide groove and a horizontal guide groove which 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 a horizontal direction, A cutoff pin guide pin is provided on one side of the cutoff pin, and the cutoff pin guide pin is located in 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 a distance between the first point and the second point, and when the cutoff pin guide pin moves horizontally from the second point to a third point in the cutoff pin guide groove, the cutoff pin rotates by an angle between the second point and the third point, A cylindrical cam roller separation protrusion having a radius smaller than that of the cutoff pin is provided on the bottom surface of the cutoff pin, and the center of the cam roller separation protrusion is eccentric from the circular center of the cutoff pin; 6. The gas supply pump for a marine dual fuel engine as claimed in claim 5, wherein when the cutoff pin guide pin moves horizontally from the second point to the third point of the cutoff pin guide groove, a cam roller spacing protrusion provided on a bottom surface of the cutoff pin rotates at a certain angle to form the spacing mechanism.

17. A cutoff pin insertion hole through which the cutoff pin is inserted is provided on one side of the cam roller drive shaft case, and a cam roller separation guide groove is provided on the integrated connecting member corresponding to the cutoff pin insertion hole, When the cutoff pin guide pin is located at the second position, the cam roller separation protrusion at the lower end of the cutoff pin is located in the cam roller separation guide groove of the integrated connecting member, and the cam roller separation protrusion does not abut against the integrated connecting member in the cam roller separation guide groove; When the cutoff pin protrusion is moved from the second point to the third point of the cutoff pin guide groove, the cam roller separation protrusion rotates horizontally in accordance with the horizontal rotation of the cutoff pin, physically pushing out and moving the integral connecting member, 17. The gas supply pump for a marine dual fuel engine according to claim 16, wherein the cam roller and the cam nose are separated by the movement of the integral connecting member by the cam roller separating protrusion, thereby forming the separating mechanism.

18. Each of the plurality of cylinder units is A coupling case provided at the coupling portion between the drive shaft and the piston; a rack member connected and fixed to the drive shaft in the inner space of the coupling case, or connected and fixed to both the drive shaft and the piston; A pinion that meshes with a tooth-shaped rack provided on the outer surface of the rack member; and a pinion guide member provided on the other side of the pinion to transmit a driving force to the pinion; 2. The gas supply pump for a marine dual fuel engine according to claim 1, wherein when the pinion guide member is moved downward, the pinion is rotated counterclockwise, and 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, forming the separation mechanism.

19. 20. The marine dual fuel engine gas supply pump according to claim 18, wherein the pinion guide member is reciprocated by a cylinder.

20. When the gas supply pump is driven, each of the plurality of cam noses rotates and moves in accordance with the rotation of a camshaft, The first cylinder unit includes a first cam roller, and the first cam roller transmits a rotational driving force of a cam nose corresponding to the first cam roller to a corresponding piston to cause a linear reciprocating motion, and is driven.

2. The gas supply pump for a marine dual fuel engine as described in claim 1, wherein the second cylinder unit includes a second cam roller, and the separation mechanism maintains the second cam roller separated from the corresponding cam nose, so that the rotational driving force of the cam nose is not transmitted to the corresponding piston, and the piston is not driven because it does not cause linear reciprocating motion.

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