KR20230143636A - Radial Piston Pump for ship - Google Patents

Abstract

The present invention includes a base portion (20), a valve assembly (25) that is screwed to the upper surface of the base portion (20) in a plurality of circumferential directions, and through which oil flows inward, and rotates in one direction in the center of the base portion (20). A shaft 40 that can be coupled, an operating bearing 45 that is coupled to the center of the shaft 40 and rotates eccentrically about the central axis of the shaft 40 by the shaft 40, and the valve assembly. It is provided between (25) and the operating bearing 45, and is periodically moved in the direction opposite to the center of the operating bearing 45 by the operating bearing 45, so that oil flows into the valve assembly 25. It includes a stopper 50 that blocks the base portion 20 and a cover 55 screwed to the upper part of the base portion 20, and a lower body portion 40a is formed on the lower part of the shaft 40 in the direction of gravity. , a rotating part (40b) is formed on the upper part of the lower body part (40a) to protrude eccentrically with respect to the central axis of the lower body part (40a), and an upper body part (40c) is formed on the upper part of the rotating part (40b) by gravity. It is formed in the opposite direction, and the plate insertion part 40d is formed recessed in the lower part of the rotating part 40b in the opposite direction of gravity.

Description

Radial Piston Pump for ship {Radial Piston Pump for ship}

The present invention relates to a radial piston pump, and more specifically, to a radial piston pump for ships, which supplies oil according to a preset cycle to the actuator for opening and closing the fluid supply valve of the ship so that the actuator can be driven according to a certain stroke distance. It's about radial piston pumps.

The Valve Remote Control System (VCRS) refers to a system for remotely controlling fluid supply valves that are placed in areas that are difficult for people to access or that are difficult to operate with human power.

In addition, the SCP unit (Self Contained Power Unit) is a small modular module that includes a valve for supplying fluids such as fuel oil, ballast water, and bilge to the ship, an actuator for opening and closing the valve, and a micro power pack installed on top of the actuator. It means a system constructed by:

In addition, the micro power pack includes a radial piston pump that supplies oil to the actuator according to a preset cycle so that the actuator can be driven according to a constant stroke distance, a drive motor and oil to rotate the radial piston pump. It consists of an oil tank where it is stored.

The SCP unit is mainly applied to large container ships where it is difficult to install a valve remote control system because the internal space is narrow because a large number of containers must be loaded inside.

However, the conventional radial piston pump is difficult to supply the oil flow rate in a variable manner according to the preset cycle to the actuator for opening and closing the fluid supply valve of the ship, and the problem is that the actuator is not driven accurately according to the constant stroke distance. There was this.

KR 10-2316904 B1

The present invention was created to solve the above problems, and the purpose of the present invention is to operate the actuator for opening and closing the fluid supply valve of the ship at a preset cycle so that the actuator can be driven according to a certain stroke distance. The aim is to provide a marine radial piston pump that supplies oil according to the requirements.

In order to solve the above technical problems, the marine radial piston pump according to the present invention includes a base portion 20, a plurality of screws coupled to the upper surface of the base portion 20 in the circumferential direction, and oil flowing into the inside. A valve assembly 25, a shaft 40 rotatably coupled to the center of the base portion 20 in one direction, coupled to the center of the shaft 40, and connected to the shaft 40 by the shaft 40. An operating bearing 45, which rotates eccentrically about the central axis, is provided between the valve assembly 25 and the operating bearing 45, and periodically rotates the operating bearing 45 by the operating bearing 45. It includes a stopper 50 that blocks oil from flowing into the valve assembly 25 by moving in the opposite direction of the center, and a cover 55 screwed to the upper part of the base portion 20, and the shaft ( A lower body portion 40a is formed at the lower portion of 40) in the direction of gravity, and a rotating portion 40b is formed at the upper portion of the lower body portion 40a to protrude eccentrically with respect to the central axis of the lower body portion 40a. An upper body portion 40c is formed on the upper part of the rotating part 40b in the opposite direction of gravity, and a plate insertion part 40d is formed on the lower part of the rotating part 40b in the opposite direction of gravity. Do it as

In addition, a first bearing 60 is provided on the outer upper part of the lower body part 40a to facilitate rotation of the lower body part 40a, and a border provided on the lower part of the first bearing 60 Part 61 is inserted and coupled to the lower part of the rotating part 40b, and is provided on the outside of the shaft plate 62 and the upper body part 40c, which rotates by the shaft 40, and the upper body part ( It further includes a second bearing 63 for smooth rotation of 40c, and a mounting portion 20a on which the shaft plate 62 is disposed is recessed in the upper part of the base portion 20, and the mounting portion ( A seating portion 20b on which the first bearing 60 is seated is recessed in the lower part of 20a), and an insertion portion 20c into which the edge portion 61 is inserted is formed on the lower part of the seating portion 20b. It is recessed, and a through hole 61a through which the lower body part 40a is inserted is formed on the upper surface of the edge portion 61, and the plate insertion portion 40d on the upper surface of the shaft plate 62. ) is formed through a coupling hole (62a) inserted through the It is characterized by rotating eccentrically to the standard.

In addition, the valve assembly 25 has a spring fastening portion 26a on one side protruding toward the center of the operating bearing 45, and a sliding portion 26b on one side of the spring fastening portion 26a for the operation. It includes an inlet valve 26 formed in a direction opposite to the center of the bearing 45, and an inlet portion 26c is formed on the rear side of the inlet valve 26 and is recessed in the direction of the center of the operating bearing 45. In front of the inlet part 26c, a horizontal moving part 26d is connected to the inlet part 26c and the sliding part 26b, respectively, and moves the oil flowing in from the outside in the center direction of the operating bearing 45. It is recessed, and the stopper 50 includes a pump pin 51 movably inserted and coupled to the sliding portion 26b, a spring washer 52 fastened to one side of the pump pin 51, and one end of the spring It is characterized in that it includes a first spring 53 that is fastened to the rear of the washer 52 and the other end is fastened to the spring fastening portion 26a.

In addition, a head portion 51a is formed on one side of the pump pin 51 by the operating bearing 45 and moves in a direction opposite to the center of the operating bearing 45, and the other side of the pump pin 51 is formed. A leg portion 51b inserted into the sliding portion 26b is formed on the side, and a washer fastening portion 51c to which the spring washer 52 is fastened is formed recessed at the rear of the head portion 51a. It is characterized by:

In addition, the valve assembly 25 is screwed to the inside of the inlet portion 26c, and has a fastening member 27 through which oil flows inward, and a fastening member 27 inside the fastening member 27 of the operating bearing 45. It further includes a moving pin 28 coupled to be movable in the center direction or in a direction opposite to the center of the operating bearing 45, and on one side of the moving pin 28 is a leg portion 51b of the pump pin 51. ), a head portion 28a that moves in the direction opposite to the center of the operating bearing 45 is formed, and a body portion 28b is integrally coupled to the head portion 28a on the other side of the moving pin 28. ) is formed, and on the other side of the body portion 28b, a groove portion 28c is recessed in the circumferential direction of the body portion 28b, and a first inlet hole through which oil flows is formed on the rear side of the fastening member 27. (27a) is recessed in the direction opposite to the center of the operating bearing 45, and in front of the first inlet hole (27a) is a second inlet hole through which oil passing through the first inlet hole (27a) moves. (27b) is recessed, and a third inlet hole (27c) through which the oil passing through the second inlet hole (27b) moves is recessed in front of the second inlet hole (27b), and the third inlet hole (27c) is recessed. An insertion hole 27d into which the head 28a is inserted is formed in front of the hole 27c, and the head 28a is connected to the operating bearing by the leg 51b of the pump pin 51. It is characterized in that it moves in the direction opposite to the center of (45) and is fastened to the insertion hole (27d), thereby blocking oil from moving from the insertion hole (27d) to the horizontal moving part (26d).

In addition, the valve assembly 25 includes a second spring 29 that is compressibly or expandably inserted and coupled to the body portion 28b, and is inserted into one side of the body portion 28b to form the second spring 29. A first flat washer 30, which makes surface contact with one inner surface of the first inlet hole 27a and supports one end of the second spring 29, is inserted into the other side of the body portion 28b, A snap ring 32 fastened to the second flat washer 31 supporting the other end of the second spring 29 and the groove portion 28c to prevent the second flat washer 31 from coming outward. ) is characterized in that it further includes.

In addition, an O-ring fastening portion 26e is recessed on the lower surface of the inlet valve 26 in the opposite direction of gravity, and an outlet portion communicating with the O-ring fastening portion 26e is formed on the inner upper surface of the O-ring fastening portion 26e. (26f) is formed by depression in the opposite direction of gravity, and a vertical moving part (26g) through which oil passing through the horizontal moving part (26d) moves is formed in the upper part of the discharge part (26f) in the opposite direction of gravity. , the valve assembly 25 is inserted into the discharge portion 26f and fastened to the inner peripheral surface of the coupling member 33 through which the oil passing through the discharge portion 26f moves and the O-ring fastening portion 26e. , It further includes an O-ring 34 to maintain airtightness between the inlet valve 26 and the base part 20, and the oil passing through the vertical moving part 26g moves on the upper surface of the coupling member 33. The fastening hole 33a is recessed in the direction of gravity, and a plurality of through holes 33b through which the oil passing through the fastening hole 33a passes are formed on the inner lower surface of the fastening hole 33a in the direction of gravity. It is characterized by being

In addition, on both rear sides of the upper surface of the base portion 20, first inflow passages through which oil passing through the plurality of holes 33b of the coupling member 33 flows are formed in the direction of gravity, respectively, and the base portion 20 ) At the front center of the upper surface, a second inflow passage (20e) through which oil flows is formed in the direction of gravity, and at the bottom of the first inflow passage (20d), oil passing through the first inflow passage (20d) moves. A first moving passage (20f) is formed in the front and rear direction, and at one end of the first moving passage (20f), a second moving passage (20g) through which the oil passing through the first moving passage (20f) moves is left and right. It is formed in a direction, and a discharge passage (20h) through which oil passing through the second inlet passage (20e) or the second movement passage (20g) is discharged is formed recessed in front of the outer peripheral surface of the base portion (20), At the other ends of the first movement passage (20f) and the second movement passage (20g), a headless bolt (21) is installed to prevent the oil that has passed through the first movement passage (20f) and the second movement passage (20g) from being discharged to the outside. ) is characterized in that each is fastened.

The marine radial piston pump according to the present invention can supply oil according to a preset cycle to an actuator for opening and closing a vessel's fluid supply valve, which has the effect of accurately driving the actuator according to a certain stroke distance. .

Figure 1 is a perspective view of a marine radial piston pump according to the present invention.
Figure 2 is a perspective view of a marine radial piston pump with the cover removed.
Figure 3 is an exploded view of the marine radial piston pump shown in Figure 2.
FIG. 4 is a plan view of the marine radial piston pump shown in FIG. 2.
Figure 5 is a cross-sectional view of the marine radial piston pump shown in Figure 4 taken along line AA.
Figure 6 is a cross-sectional view for explaining the coupling relationship between the valve assembly and the stopper shown in Figure 5.
Figure 7 is a cross-sectional view for explaining the coupling relationship between the fastening member, the moving pin, the second spring, and the flat washer shown in Figure 6.
Figure 8 is a plan view of the base portion shown in Figure 4.
FIG. 9 is a cross-sectional view of the base portion shown in FIG. 8 cut along line BB.
Figure 10 is a diagram for explaining the oil movement process when the moving pin moves toward the center of the operating bearing.
Figure 11 is a cross-sectional view for explaining the coupling relationship between the valve assembly including the third spring and the stopper.
Figure 12 is a plan view of the base portion including the curved passage.

Hereinafter, in order to explain the present invention in detail so that a person skilled in the art can easily implement the technical idea of the present invention, embodiments of the present invention will be described with reference to the accompanying drawings.

However, the following example is only an example to aid understanding of the present invention, and the scope of the present invention is not reduced or limited thereby. Additionally, the present invention may be implemented in many different forms and is not limited to the embodiments described herein.

Figure 1 is a perspective view of a marine radial piston pump 10 according to the present invention, and Figure 2 is a perspective view of the marine radial piston pump 10 with the cover 55 removed. FIG. 3 is an exploded view of the marine radial piston pump 10 shown in FIG. 2.

Referring to Figures 1 to 3, the marine radial piston pump 10 according to the present invention includes a base portion 20, a valve assembly 25, a shaft 40, an operating bearing 45, a stopper 50, and It consists of a cover (55).

First, the base portion 20 is provided at the lower part of the marine radial piston pump 10.

And, the valve assembly 25 is coupled to the upper surface of the base portion 20 with a plurality of screws in the circumferential direction. And, oil flows into the inside of the valve assembly 25. Oil flowing into the valve assembly 25 passes through the inside of the base portion 20 and is discharged to the outside.

Additionally, the shaft 40 is rotatably coupled to the center of the base portion 20 in one direction.

Additionally, the operating bearing 45 is coupled to the center of the shaft 40 and rotates eccentrically with respect to the central axis of the shaft 40 by the rotational force of the shaft 40. At this time, the operating bearing 45 is preferably formed in the form of a deep groove ball bearing.

In addition, the stopper 50 is provided between the valve assembly 25 and the operating bearing 45, and periodically moves in the direction opposite to the center of the operating bearing 45 by the rotational force of the operating bearing 45, thereby moving the valve. It serves to block oil from flowing into the assembly (25).

Then, the cover 55 is screwed to the upper part of the base portion 20.

Referring to FIG. 3, a lower body portion 40a is formed to be long in the direction of gravity at the lower portion of the shaft 40, and a rotating portion 40b is formed at the upper portion of the lower body portion 40a at the center of the lower body portion 40a. It is formed to protrude eccentrically relative to the axis. At this time, the diameter of the rotating part 40b is formed to be larger than the diameter of the lower body part 40a.

Additionally, an upper body portion 40c is formed at the top of the rotating portion 40b in a direction opposite to gravity, and a plate insertion portion 40d is formed at the bottom of the rotating portion 40b in a direction opposite to gravity. At this time, the diameter of the upper body portion 40c is formed to be the same as the diameter of the lower body portion 40a.

FIG. 4 is a plan view of the marine radial piston pump 10 shown in FIG. 2, and FIG. 5 is a cross-sectional view of the marine radial piston pump 10 shown in FIG. 4 taken along line AA.

3 to 5, the marine radial piston pump 10 according to the present invention further includes a first bearing 60, an edge portion 61, a shaft plate 62, and a second bearing 63. It is composed by:

First, the first bearing 60 is provided on the outer upper part of the lower body portion 40a of the shaft 40 and serves to smoothly rotate the lower body portion 40a. At this time, the first bearing 60 is preferably formed in the form of a deep groove ball bearing.

And, the edge portion 61 is provided at the lower part of the first bearing 60.

Then, the shaft plate 62 is inserted and coupled to the lower part of the rotating portion 40b of the shaft 40 and rotates in one direction by the rotational force of the shaft 40. At this time, the shaft plate 62 is formed in the shape of a flat plate with a predetermined thickness.

Additionally, the second bearing 63 is provided on the outside of the upper body portion 40c of the shaft 40 and serves to smoothly rotate the upper body portion 40c. At this time, the second bearing 63 is preferably formed in the form of a deep groove ball bearing.

Referring to FIGS. 3 to 5, the mounting portion 20a on which the shaft plate 62 is disposed is recessed in the upper part of the base portion 20, and the first bearing 60 is seated in the lower portion of the mounting portion 20a. The seating portion 20b is recessed.

And, an insertion portion 20c into which the edge portion 61 is inserted and coupled is formed recessed in the lower part of the seating portion 20b.

And, a through hole 61a through which the lower body portion 40a is inserted is formed on the upper surface of the edge portion 61.

Additionally, a coupling hole 62a is formed through the upper surface of the shaft plate 62 and is inserted into the plate insertion portion 40d.

Meanwhile, the operating bearing 45 is provided on the outside of the rotating part 40b of the shaft 40, and rotates eccentrically about the central axis of the lower body part 40a by the rotating force of the shaft 40.

Figure 6 is a cross-sectional view for explaining the coupling relationship between the valve assembly 25 and the stopper 50 shown in Figure 5, and Figure 7 shows the fastening member 27, the moving pin 28, and the second shown in Figure 6. This is a cross-sectional view to explain the coupling relationship between the spring 29 and the flat washer.

Referring to Figures 6 and 7, the valve assembly 25 has a spring fastening portion 26a on one side protruding in the center direction of the operating bearing 45, and a sliding portion ( 26b) is configured to include an inlet valve 26 formed long in the direction opposite to the center of the operating bearing 45.

And, at the rear of the inlet valve 26, an inlet portion 26c is recessed toward the center of the operating bearing 45.

In addition, in front of the inlet valve 26, a horizontal moving part 26d, which is in communication with the inlet part 26c and the sliding part 26b, respectively, and through which the oil flowing in from the outside moves, moves in the direction of the center of the operating bearing 45. A depression is formed.

Referring to FIG. 6, the stopper 50 includes a pump pin 51, a spring washer 52, and a first spring 53.

First, the pump pin 51 is movably inserted and coupled to the sliding portion 26b of the inlet valve 26.

And, the spring washer 52 is fastened to one side of the pump pin 51.

And, one end of the first spring 53 is fastened to the rear of the spring washer 52, and the other end of the first spring 53 is fastened to the spring fastening portion 26a of the inflow valve 26.

Meanwhile, a head portion 51a is formed on one side of the pump pin 51, which contacts the outer peripheral surface of the operating bearing 45 and moves in a direction opposite to the center of the operating bearing 45 by the operating bearing 45. And, a leg portion 51b that is inserted into the sliding portion 26b of the inlet valve 26 is formed on the other side of the pump pin 51.

And, a washer fastening portion 51c to which the spring washer 52 is fastened is formed recessed at the rear of the head portion 51a.

When the pump pin 51 moves in a direction opposite to the center of the operating bearing 45 by the operating bearing 45, the first spring 53 is moved to the center of the operating bearing 45 by the pump pin 51. compressed in the opposite direction.

Referring to Figures 6 and 7, the valve assembly 25 further includes a fastening member 27 and a moving pin 28.

First, the fastening member 27 is screwed to the inside of the inlet portion 26c. Then, external oil flows into the fastening member 27.

In addition, the moving pin 28 is coupled to the inside of the fastening member 27 to be movable in the direction of the center of the operating bearing 45 or in the direction opposite to the center of the operating bearing 45.

And, on one side of the movable pin 28, a head portion 28a is formed that moves in the direction opposite to the center of the operating bearing 45 by the leg portion 51b of the pump pin 51, and the movable pin 28 On the other side, a long body portion 28b is formed integrally with the head portion 28a.

And, on the other side of the body portion 28b, a groove portion 28c is recessed in the circumferential direction of the body portion 28b.

Meanwhile, at the rear of the fastening member 27, a first inlet hole (27a) through which external oil flows is recessed in the direction opposite to the center of the operating bearing 45, and in front of the first inlet hole (27a) is a first inlet hole (27a) through which external oil flows. 1 The second inlet hole (27b) is in communication with the inlet hole (27a) and is formed as a depression through which the oil passing through the first inlet hole (27a) moves.

In addition, in front of the second inlet hole 27b, a third inlet hole 27c is formed in a depression that communicates with the second inlet hole 27b and through which the oil passing through the second inlet hole 27b moves. 3 An insertion hole 27d into which the head 28a of the moving pin 28 is inserted is formed in front of the inlet hole 27c.

At this time, the head portion 28a moves in the direction opposite to the center of the operating bearing 45 by the leg portion 51b of the pump pin 51 and is fastened to the insertion hole 27d of the fastening member 27, It serves to block oil from moving from the insertion hole (27d) of the fastening member (27) to the horizontal moving part (26d).

Referring to FIG. 7, the valve assembly 25 further includes a second spring 29, a first flat washer 30, a second flat washer 31, and a snap ring 32.

First, the second spring 29 is inserted and coupled to the body portion 28b of the moving pin 28 so as to be compressible or expandable.

In addition, the first flat washer 30 is inserted into one side of the body portion 28b of the moving pin 28 and makes surface contact with one inner surface of the first inlet hole 27a by the second spring 29, Supports one end of the second spring (29).

And, the second flat washer 31 is inserted into the other side of the body portion 28b of the moving pin 28 and supports the other end of the second spring 29.

Additionally, the snap ring 32 is fastened to the groove portion 28c of the moving pin 28 and serves to prevent the second flat washer 31 from being separated to the outside.

Referring to FIG. 6, an O-ring fastening portion 26e is recessed in the lower surface of the inlet valve 26 in the direction opposite to gravity.

And, on the inner upper surface of the O-ring fastening portion 26e, a discharge portion 26f communicating with the O-ring fastening portion 26e is recessed in the direction opposite to gravity.

In addition, the upper part of the discharge part 26f is in communication with the O-ring fastening part 26e and the horizontal moving part 26d, and the vertical moving part 26g through which the oil passing through the horizontal moving part 26d moves is gravity. It is formed long in the opposite direction.

Referring to Figures 6 and 7, the valve assembly 25 further includes a coupling member 33 and an O-ring 34.

First, the coupling member 33 is inserted and coupled to the discharge part 26f of the inlet valve 26, and becomes a passage through which oil passing through the discharge part 26f moves.

In addition, the O-ring 34 is fastened to the inner peripheral surface of the O-ring fastening portion 26e of the inlet valve 26, and serves to maintain airtightness between the inlet valve 26 and the base portion 20.

In addition, on the upper surface of the coupling member 33, a fastening hole 33a through which the oil passing through the vertical moving part 26g of the inlet valve 26 moves is formed to be depressed in the direction of gravity, and the inner side of the fastening hole 33a A plurality of through holes 33b through which oil passing through the fastening hole 33a passes are formed on the lower surface.

FIG. 8 is a plan view of the base portion 20 shown in FIG. 4, and FIG. 9 is a cross-sectional view of the base portion 20 shown in FIG. 8 taken along line BB.

Referring to FIGS. 8 and 9, on both rear sides of the upper surface of the base portion 20, a first inlet passage 20d through which oil passing through the plurality of holes 33b of the coupling member 33 flows is formed in the direction of gravity. It is formed long.

In addition, at the front center of the upper surface of the base portion 20, a second inlet passage 20e through which oil passing through the plurality of holes 33b of the coupling member 33 flows is formed to be long in the direction of gravity.

And, at the lower part of the first inflow passage 20d, a first movement passage 20f through which the oil passing through the first inflow passage 20d moves is formed long in the front-back direction.

And, at one end of the first movement passage (20f), a second movement passage (20g) through which the oil that has passed through the first movement passage (20f) moves is formed long in the left and right directions.

In addition, the front of the outer peripheral surface of the base portion 20 is in communication with the second inflow passage 20e and the second movement passage 20g, respectively, so that the water passing through the second inflow passage 20e or the second movement passage 20g is connected. The discharge passage 20h through which oil is discharged is recessed.

Meanwhile, at the other ends of the first movement passage (20f) and the second movement passage (20g), a headless bolt (21) is installed to prevent the oil that has passed through the first movement passage (20f) and the second movement passage (20g) from being discharged to the outside. ) are concluded respectively.

Oil flowing into the first inflow passage 20d passes through the first movement passage 20f and the second movement passage 20g, and is discharged to the outside through the discharge passage 20h. And, the oil flowing into the second inlet passage (20e) is discharged to the outside through the discharge passage (20h).

Figure 10 is a diagram for explaining the oil movement process when the moving pin moves toward the center of the operating bearing.

Referring to FIG. 10, a central hole 30a is formed through the center of one surface of the first flat washer 30. At this time, the inner diameter of the central hole (30a) is formed to be larger than the outer diameter of the body portion (28b) of the moving pin (28).

Additionally, an external force is always applied to the end of the body portion 28b of the moving pin 28 in the direction toward the center of the operating bearing 45. And, when the external force caused by the leg portion 51b of the pump pin 51 does not act on the head 28 of the movable pin 28, the movable pin 28 moves in the direction of the center of the operating bearing 45. do. As a result, the insertion hole 27d is opened to allow movement of oil.

Therefore, the oil passes through the first inlet hole (27a), the center (30a) hole of the first flat washer (30), the second inlet hole (27b), the third inlet hole (27c), and the insertion hole (27d). Afterwards, it can be moved to the vertical movement unit 26g via the horizontal movement unit 26d.

Figure 11 is a cross-sectional view for explaining the coupling relationship between the valve assembly including the third spring and the stopper.

Referring to FIG. 11, a first protrusion 51d may be formed to protrude at the center of one surface of the leg portion 51b of the pump pin 51.

In addition, a second protrusion 28d may be formed to protrude at the center of one surface of the head portion 28a of the movable pin 28 opposite to one surface of the leg portion 51b of the pump pin 51.

In addition, the valve assembly 25 has a third spring 35 whose one end is inserted and coupled to the first protrusion 51d of the pump pin 51 and the other end is inserted and coupled to the second protrusion 28d of the moving pin 28. ) may be further included.

When the pump pin 51 moves in the direction opposite to the center of the operating bearing 45, the third spring 35 is compressed by the pump pin 51 and is attached to the pump head 28a of the moving pin 28. The pressing force of the pin 51 can be transmitted more effectively.

In addition, even when the pump pin 51 moves in the center direction of the operating bearing 45, the separation distance between the head portion 28a of the moving pin 28 and the leg portion 51b of the pump pin 51 is the third spring. It can be maintained more effectively through (35).

Figure 12 is a plan view of the base portion 20 including the curved passage 20i.

Referring to FIG. 12, a curved passage 20i may be formed between the first movement passage 20f and the second movement passage 20g.

A curved passage (20i) rather than an angled passage is formed between the first movement passage (20f) and the second movement passage (20g), so that oil flows from the first movement passage (20f) to the second movement passage (20g). You can move more smoothly.

The marine radial piston pump 10 according to the present invention is capable of supplying oil according to a preset cycle to an actuator for opening and closing a vessel's fluid supply valve, allowing the actuator to be accurately driven according to a certain stroke distance. It works.

As described above, the main technical idea of the present invention is to provide a radial piston pump 10 for ships, and the embodiment described above with reference to the drawings is only one embodiment, and the true scope of the present invention is is based on the scope of the patent claims, but also extends to equivalent embodiments that may exist in various ways.

10: Marine radial piston pump
20: base part 20a: mounting part
20b: Seating part 20c: Insertion part
20d: first inflow passage 20e: second inflow passage
20f: first movement passage 20g: second movement passage
20h: discharge passage 20i: curved passage
21: Headless bolt 25: Valve assembly
26: Inlet valve 26a: Spring fastening part
26b: sliding part 26c: inlet part
26d: horizontal moving part 26e: O-ring fastening part
26f: discharge part 26g: vertical moving part
27: fastening member 27a: first inlet hole
27b: second inlet hole 27c: third inlet hole
27d: Insertion hole 28: Moving pin
28a: head 28b: body
28c: groove 28d: second protrusion
29: second spring 30: first flat washer
30a: Central hole 31: Second flat washer
32: snap ring 33: coupling member
33a: fastening hole 33b: through hole
34: O-ring 35: Third spring
40: Shaft 40a: Lower body part
40b: Rotating part 40c: Upper body part
40d: plate insertion part 45: operating bearing
50: Stopper 51: Pump pin
51a: head part 51b: leg part
51c: washer fastening portion 51d: first protrusion
52: spring washer 53: first spring
55: Cover 60: First bearing
61: Edge portion 61a: Through hole
62: shaft plate 62a: coupling hole
63: second bearing

Claims (8)

Base portion (20);
A plurality of valve assemblies (25) are screwed to the upper surface of the base portion (20) in the circumferential direction and allow oil to flow inside;
A shaft 40 rotatably coupled to the center of the base portion 20 in one direction;
An operating bearing 45 coupled to the center of the shaft 40 and rotated eccentrically about the central axis of the shaft 40 by the shaft 40;
It is provided between the valve assembly 25 and the operating bearing 45, and is periodically moved in the direction opposite to the center of the operating bearing 45 by the operating bearing 45, thereby moving to the valve assembly 25. A stopper (50) that blocks oil from flowing in; and
It includes a cover 55 screwed to the upper part of the base portion 20,
At the lower part of the shaft 40
The lower body portion 40a is formed in the direction of gravity,
At the top of the lower body portion (40a)
The rotating part 40b is formed to protrude eccentrically with respect to the central axis of the lower body part 40a,
At the top of the rotating part (40b)
The upper body portion 40c is formed in the opposite direction of gravity,
At the bottom of the rotating part (40b)
A radial piston pump for ships, characterized in that the plate insertion portion (40d) is recessed in the opposite direction of gravity. According to clause 1,
A first bearing 60 provided on the outer upper portion of the lower body portion 40a to facilitate rotation of the lower body portion 40a;
An edge portion 61 provided at the lower portion of the first bearing 60;
A shaft plate 62 inserted into the lower part of the rotating part 40b and rotated by the shaft 40; and
It further includes a second bearing 63 provided on the outside of the upper body portion 40c to facilitate rotation of the upper body portion 40c,
At the top of the base portion 20
The mounting portion 20a on which the shaft plate 62 is disposed is recessed,
At the bottom of the mounting portion (20a)
The seating portion 20b on which the first bearing 60 is seated is recessed,
At the lower part of the seating portion (20b)
The insertion portion 20c into which the edge portion 61 is inserted and coupled is formed recessed,
On the upper surface of the edge portion 61
A through hole (61a) through which the lower body portion (40a) is inserted is formed through,
On the upper surface of the shaft plate 62
A coupling hole (62a) is formed through and inserted into the plate insertion portion (40d),
The operating bearing 45 is
A radial piston pump for ships, which is provided on the outside of the rotating part (40b) and rotates eccentrically about the central axis of the lower body part (40a) by the shaft (40). According to clause 1,
The valve assembly (25) is
A spring fastening portion 26a is formed on one side to protrude toward the center of the operating bearing 45, and a sliding portion 26b is formed on one side of the spring fastening portion 26a in a direction opposite to the center of the operating bearing 45. It includes an inlet valve (26) formed of,
At the rear of the inlet valve (26),
The inlet portion 26c is recessed toward the center of the operating bearing 45,
In front of the inlet portion 26c,
A horizontal moving part (26d), which is in communication with the inlet part (26c) and the sliding part (26b), respectively, and through which oil flowing in from the outside moves, is depressed in the direction of the center of the operating bearing (45),
The stopper 50 is
A pump pin (51) movably inserted and coupled to the sliding portion (26b);
A spring washer (52) fastened to one side of the pump pin (51); and
A marine radial piston pump comprising a first spring (53), one end of which is fastened to the rear of the spring washer (52), and the other end of which is fastened to the spring fastening portion (26a). According to clause 3,
On one side of the pump pin (51)
A head portion 51a is formed by the operating bearing 45 and moves in a direction opposite to the center of the operating bearing 45,
On the other side of the pump pin (51)
A leg portion 51b inserted into the sliding portion 26b is formed,
At the rear of the head portion 51a
A radial piston pump for ships, characterized in that the washer fastening portion (51c) to which the spring washer (52) is fastened is depressed. According to clause 3,
The valve assembly (25) is
A fastening member (27) screwed to the inside of the inlet portion (26c) and allowing oil to flow inside; and
It further includes a moving pin (28) coupled to the inside of the fastening member (27) to be movable in the direction of the center of the operating bearing (45) or in a direction opposite to the center of the operating bearing (45),
On one side of the moving pin (28)
A head portion 28a moving in a direction opposite to the center of the operating bearing 45 is formed by the leg portion 51b of the pump pin 51,
On the other side of the moving pin (28)
A body portion (28b) is formed integrally coupled to the head portion (28a),
On the other side of the body portion 28b,
A groove portion 28c is recessed in the circumferential direction of the body portion 28b,
At the rear of the fastening member 27,
The first inlet hole (27a) through which oil flows is recessed in the direction opposite to the center of the operating bearing (45),
In front of the first inlet hole (27a)
The second inlet hole (27b) through which the oil passing through the first inlet hole (27a) moves is depressed,
In front of the second inlet hole (27b)
The third inlet hole (27c) through which the oil passing through the second inlet hole (27b) moves is depressed,
In front of the third inlet hole (27c)
An insertion hole 27d into which the head 28a is inserted is formed through,
The head portion 28a is
The leg portion 51b of the pump pin 51 moves in the direction opposite to the center of the operating bearing 45 and is fastened to the insertion hole 27d, so that oil flows from the insertion hole 27d to the horizontal A marine radial piston pump, characterized in that it blocks movement to the moving part (26d). According to clause 5,
The valve assembly (25) is
a second spring (29) that is inserted and coupled to the body portion (28b) in a way that can be compressed or expanded;
It is inserted into one side of the body portion 28b, makes surface contact with one inner surface of the first inlet hole 27a by the second spring 29, and supports one end of the second spring 29. 1 flat washer (30);
a second flat washer (31) inserted into the other side of the body portion (28b) and supporting the other end of the second spring (29); and
A radial piston pump for a ship, characterized in that it further includes a snap ring (32) fastened to the groove portion (28c) to prevent the second flat washer (31) from being separated to the outside. According to clause 3,
On the lower surface of the inlet valve (26)
The O-ring fastening portion (26e) is depressed in the opposite direction of gravity,
On the inner upper surface of the O-ring fastening portion (26e),
The discharge portion (26f) communicating with the O-ring fastening portion (26e) is depressed in the direction opposite to gravity,
At the top of the discharge portion (26f)
A vertical moving part (26g) through which the oil passing through the horizontal moving part (26d) moves is formed in the opposite direction of gravity,
The valve assembly (25) is
A coupling member (33) inserted into and coupled to the discharge portion (26f), through which the oil passing through the discharge portion (26f) moves; and
It further includes an O-ring (34) fastened to the inner peripheral surface of the O-ring fastening portion (26e) to maintain airtightness between the inlet valve (26) and the base portion (20),
On the upper surface of the coupling member 33
The fastening hole (33a) through which the oil passing through the vertical moving part (26g) moves is depressed in the direction of gravity,
On the inner lower surface of the fastening hole (33a)
A radial piston pump for ships, characterized in that a plurality of through holes (33b) through which the oil passing through the fastening hole (33a) passes are formed in the direction of gravity. According to clause 1,
On both rear sides of the upper surface of the base portion 20,
A first inflow passage through which oil passing through the plurality of holes 33b of the coupling member 33 flows is formed in the direction of gravity, respectively,
At the front center of the upper surface of the base portion 20
A second inflow passage 20e through which oil flows is formed in the direction of gravity,
At the bottom of the first inlet passage (20d)
A first movement passage (20f) through which the oil passing through the first inflow passage (20d) moves is formed in the front-back direction,
At one end of the first movement passage (20f), a second movement passage (20g) through which the oil passing through the first movement passage (20f) moves is formed in the left and right directions,
In front of the outer peripheral surface of the base portion 20,
A discharge passage (20h) through which the oil passing through the second inlet passage (20e) or the second movement passage (20g) is discharged is formed depressed,
At the other ends of the first movement passage (20f) and the second movement passage (20g), a headless bolt (21) is installed to prevent the oil that has passed through the first movement passage (20f) and the second movement passage (20g) from being discharged to the outside. ) A marine radial piston pump, characterized in that each is fastened.