JP6703868B2 - Valve gear and crosshead internal combustion engine - Google Patents

Description

The present invention relates to a valve operating device for driving an exhaust valve in an internal combustion engine such as a diesel engine or a gas engine, and a crosshead internal combustion engine including the valve operating device.

In a crosshead internal combustion engine, a valve train that opens and closes an exhaust valve includes a lower valve train and an upper valve train. The valve operating device supplies the hydraulic oil compressed by the lower valve operating device to the upper valve operating device, and pushes the exhaust valve downward against the urging force of the air spring by using the driving force of the transmitted hydraulic oil to close the valve. It opens and closes the exhaust valve. In this lower valve operating device, a sliding cylinder biased downward by a spring is supported in a casing so as to be movable in the vertical direction. The sliding cylinder is pushed up by the cam to raise the piston and compress the hydraulic oil to be supplied.

As a conventional valve gear, for example, there is one described in Patent Document 1 below.

JP, 2005-098795, A

In the above-described lower valve operating device, the rotating cam needs to supply the lubricating oil to the sliding surface between the cam and the roller because the cam portion pushes up the slide cylinder via the roller. Conventionally, a part of the hydraulic oil used to drive the exhaust valve by supplying it to the upper valve gear has been supplied to the cams and rollers as lubricating oil. That is, a pipe for supplying hydraulic oil (lubricating oil) from outside is provided through a camshaft box in which a sliding cylinder or cam is housed, and a pipe for supplying hydraulic oil from outside is connected to a cylinder in which a piston is housed. Was there. Therefore, there are problems that a plurality of pipes are required, the structure becomes complicated, and the manufacturing cost increases.

The present invention solves the above-mentioned problems, and an object of the present invention is to provide a valve train and a crosshead type internal combustion engine that can simplify the structure.

A valve operating device of the present invention for achieving the above object is a device main body including a lower casing and an upper casing, a slide cylinder movably supported in the axial direction with respect to the lower casing, and the upper portion. A piston that is movably supported with respect to the casing in the axial direction and that moves integrally with the sliding cylinder, a cam that moves the sliding cylinder, and a hydraulic oil that is provided in the upper casing and is provided in the apparatus main body. A hydraulic fluid supply section for supplying the hydraulic fluid, a compression chamber for compressing a part of the hydraulic fluid supplied from the hydraulic fluid supply section by the movement of the piston in the upper casing, and the compression chamber for compressing the hydraulic fluid from the hydraulic oil supply section. A first hydraulic oil supply path for supplying a part of the hydraulic oil to the chamber and a second hydraulic oil supply path for supplying the other part of the hydraulic oil from the hydraulic oil supply section to the lower casing are formed. It is characterized by that.

Therefore, when the cam rotates, the sliding cylinder reciprocates in the axial direction by the rotational force of the cam, and the piston reciprocates integrally with the sliding cylinder. Then, the hydraulic oil supplied from the hydraulic oil supply unit to the compression chamber through the first hydraulic oil supply path is compressed and discharged. Further, the hydraulic oil supplied from the hydraulic oil supply unit through the second hydraulic oil supply path is supplied to the cam, and the cam is lubricated. Here, by providing a first hydraulic oil supply path for supplying hydraulic oil from one hydraulic oil supply section to the compression chamber, and by providing a second hydraulic oil supply path for supplying hydraulic oil to the cam, the hydraulic oil supply section is provided. It is possible to simplify the structure of the piping to the device, and also to simplify the processing of the oil passage for the main body of the device. As a result, the structure can be simplified.

In the valve gear of the present invention, the upper casing is provided in an upper part of the camshaft box, an opening communicating with the cam is provided on a side surface of the camshaft box, and the hydraulic oil is supplied to the hydraulic oil supply section. A hydraulic oil supply pipe for supplying the hydraulic oil is arranged above the opening.

Therefore, by disposing the hydraulic oil supply pipe for supplying the hydraulic oil to the hydraulic oil supply unit above the opening, the hydraulic oil supply pipe interferes with an operator who performs various operations from the opening to the cam. Rather, the workability can be improved.

In the valve operating system of the present invention, the first hydraulic oil supply passage allows the flow of the hydraulic oil from the hydraulic oil supply section to the compression chamber to allow the operation from the compression chamber to the hydraulic oil supply section. A check valve for prohibiting the flow of oil is provided, and a hydraulic oil discharge section for discharging the hydraulic oil compressed in the compression chamber is provided between the compression chamber and the check valve in the first hydraulic oil supply path. It is characterized by being communicated.

Therefore, when the hydraulic oil is supplied to the hydraulic oil supply unit, the hydraulic oil is supplied to the compression chamber through the first hydraulic oil supply path, the hydraulic oil is compressed in the compression chamber when the piston moves up, and is discharged from the hydraulic oil discharge unit. At this time, since the check valve is provided in the first hydraulic oil supply path, the hydraulic oil compressed in the compression chamber does not flow back to the hydraulic oil supply section, and can be appropriately discharged from the hydraulic oil discharge section. it can.

In the valve gear of the present invention, the opening on the side of the lower casing in the second hydraulic oil supply path is connected to the hydraulic oil supply path in the lower casing, and the hydraulic oil supply path in the lower casing is It is characterized in that it is provided in the lower casing along the axial direction so that the upper end portion is opened toward the upper casing side and the lower end portion is opened toward the cam.

Therefore, by providing the upper supply path of the upper casing and the lower supply path of the lower casing as the second hydraulic oil supply path, the supply path formed in the apparatus main body can be simplified.

In the valve gear of the present invention, the sliding cylinder has a key groove provided on an outer peripheral surface along the axial direction, and a key fixed to the lower casing is inserted into the key groove, and a hydraulic oil supply path in the lower casing is provided. Is provided with the key groove and a communication groove provided in the key.

Therefore, by inserting the key fixed to the lower casing into the key groove of the sliding cylinder, it is possible to easily prevent the sliding cylinder from rotating, and by providing the key groove and the communication groove in the key as the lower supply path. , The structure can be simplified.

Further, the crosshead internal combustion engine of the present invention includes a lower valve operating device to which the valve operating device is applied, and an upper valve operating device that drives an exhaust valve with hydraulic oil from the lower valve operating device. It is characterized by.

Therefore, when the cam rotates in the lower valve operating device, the sliding cylinder reciprocates in the axial direction by the rotational force of the cam, and the piston reciprocates integrally with the sliding cylinder. Then, the hydraulic oil supplied from the hydraulic oil supply unit to the compression chamber through the first hydraulic oil supply path is compressed and discharged. Further, the hydraulic oil supplied from the hydraulic oil supply unit through the second hydraulic oil supply path is supplied to the cam, and the cam is lubricated. Here, by providing a first hydraulic oil supply path for supplying hydraulic oil from one hydraulic oil supply section to the compression chamber, and by providing a second hydraulic oil supply path for supplying hydraulic oil to the cam, the hydraulic oil supply section is provided. It is possible to simplify the structure of the piping to the device, and also to simplify the processing of the oil passage for the main body of the device. As a result, the structure can be simplified.

According to the valve gear and the crosshead internal combustion engine of the present invention, the structure can be simplified.

FIG. 1 is a sectional view showing a lower valve operating system of the present embodiment. FIG. 2 is a sectional view showing a sliding cylinder in the lower valve operating device. FIG. 3 is a right side view of the sliding cylinder. FIG. 4 is a left side view of the sliding cylinder. FIG. 5 is a V-V sectional view of FIG. 2 showing a horizontal section of the sliding cylinder. FIG. 6 is a front view showing the lower valve operating device. FIG. 7 is a schematic diagram showing a diesel engine. FIG. 8 is a schematic diagram showing the valve gear of the present embodiment.

Hereinafter, preferred embodiments of a valve train and a crosshead type internal combustion engine according to the present invention will be described in detail with reference to the accompanying drawings. It should be noted that the present invention is not limited to this embodiment, and when there are a plurality of embodiments, the present invention also includes those configured by combining the respective embodiments.

FIG. 7 is a schematic diagram showing a diesel engine.

In the present embodiment, as shown in FIG. 7, the diesel engine 10 is, for example, a two-stroke, one-cycle uniflow scavenging crosshead internal combustion engine that is used as a main engine for marine propulsion. The diesel engine 10 includes a base plate 11 located below, a frame 12 provided on the base plate 11, and a cylinder jacket 13 provided on the frame 12. The base plate 11, the frame 12, and the cylinder jacket 13 are integrally fastened and fixed by a plurality of tension bolts 14 and nuts 15 extending in the vertical direction.

A space portion is defined by the cylinder liner 16 and the cylinder cover 17, and a combustion chamber 19 is formed by a piston 18 being reciprocally movable in the space portion. The cylinder cover 17 is provided with an exhaust valve 20 and can be opened and closed by a valve operating device 21. The exhaust valve 20 opens and closes the combustion chamber 19 and the exhaust pipe 22. Here, the cylinder jacket 13, the cylinder liner 16, and the cylinder cover 17 constitute a combustion device.

Therefore, fuel (for example, low-quality oil, natural gas, or mixed fuel thereof) supplied from a fuel injection pump (not shown) and combustion gas (for example, air) compressed by a compressor (not shown) are supplied to the combustion chamber 19. , EGR gas, or mixed gas thereof is supplied to burn. The piston 18 moves up and down by the energy generated by this combustion. Further, at this time, when the combustion chamber 19 is opened by the exhaust valve 20, the exhaust gas generated by the combustion is pushed out to the exhaust pipe 22, while the combustion gas is introduced into the combustion chamber 19 from a scavenging port (not shown).

The upper end of the piston rod 23 is connected to the lower end of the piston 18. The base plate 11 constitutes a crankcase and is provided with a bearing 25 that rotatably supports the crankshaft 24. The lower end portion of the connecting rod 27 is rotatably connected to the crankshaft 24 via a crank 26. The frame 12 has a pair of vertically extending guide plates 28 fixed at predetermined intervals, and a crosshead 29 is vertically movably supported between the pair of guide plates 28. In the crosshead 29, the lower end of the piston rod 23 and the upper end of the connecting rod 27 are connected to each other.

Therefore, the piston 18 to which the energy is transmitted from the combustion chamber 19 pushes down together with the piston rod 23 in the installation surface direction of the diesel engine 10 (the direction toward the base plate 11 side, that is, the downward direction in the vertical direction). Then, the piston rod 23 pushes down the crosshead 29 in the same direction and rotates the crankshaft 24 via the connecting rod 27 and the crank 26.

FIG. 8 is a schematic diagram showing the valve gear of the present embodiment.

As shown in FIG. 8, the valve train 21 includes a lower valve train 31 and an upper valve train 32. The valve operating device 21 supplies the hydraulic oil compressed by the lower valve operating device 31 to the upper valve operating device 32, and pushes down the exhaust valve 20 by using the driving force of the hydraulic oil transmitted to the exhaust valve 20 in the closed state. To open and close.

In the upper valve operating device 32, the exhaust valve 20 is composed of a shaft portion 20a and an umbrella portion 20b, and is movably supported by a casing 33 fixed to the cylinder cover 17. The upper valve gear 32 closes the space between the combustion chamber 19 and the exhaust pipe 22 by the exhaust valve 20 when the biasing force of the air spring 34 acts so that the shaft portion 20a faces upward. In addition to the air spring 34, the upper valve operating device 32 includes a cylinder portion 35 that receives hydraulic oil supplied from the lower valve operating device 32, and a piston 36 movably provided in the cylinder portion 35. ing. The piston 36 is integrally fixed to the upper end portion of the shaft portion 20a, and thus vertically moves together with the exhaust valve 20.

In the lower valve operating device 31, a sliding cylinder 42 is supported in a casing (lower casing, device main body) 41 so as to be movable in the vertical direction (axial direction), and the sliding cylinder 42 includes a compression coil spring 43. It is biased and supported downward by the biasing force. The casing 41 is provided with a cylinder portion (upper casing, apparatus main body) 44 on the upper portion, and both are fastened by a plurality of bolts (not shown). A roller (roller portion) 45 is rotatably provided at a lower end portion of the sliding cylinder 42, and a piston 46 is connected to an upper end portion thereof, and the piston 46 moves in the cylinder portion 44 in the vertical direction (axial direction). It is provided freely. On the other hand, in the casing 41, a cam 47 that contacts the roller 45 is arranged below the sliding cylinder 42. The cam 47 rotates in synchronization with the crankshaft 24 (see FIG. 7). The cylinder portion 44 of the lower valve operating device 31 and the cylinder portion 35 of the upper valve operating device 32 are connected by a hydraulic oil pipe 48.

Therefore, when the sliding cylinder 42 is pushed up by the rotating cam 47 via the roller 45 in the lower valve operating device 31, the piston 46 compresses the hydraulic oil in the cylinder portion 44. Then, the hydraulic oil compressed in the cylinder portion 44 is supplied to the upper valve operating device 32 through the hydraulic oil pipe 48. When hydraulic oil is supplied to the cylinder portion 35 in the upper valve operating device 32, the piston 36 is pushed down, the exhaust valve 20 is lowered against the urging force of the air spring 34, and the combustion chamber 19 in the closed state is closed. And the exhaust pipe 22.

Hereinafter, the lower valve operating device 31 will be described in detail. FIG. 1 is a sectional view showing a lower valve operating system of the present embodiment.

In the lower valve operating device 31, as shown in FIG. 1, the casing 41 has a cylindrical shape, and a sliding portion 51 along the up-down direction (axial direction) is provided so as to open vertically. The sliding cylinder 42 is fitted into the sliding portion 51 of the casing 41, and is supported so as to be movable in the vertical direction (axial direction). A roller 45 is rotatably attached to the lower end of the slide cylinder 42 by a support shaft 52 extending in a direction orthogonal to the axial direction. The slide cylinder 42 and the roller 45 are integrally formed in the vertical direction (axial direction). It is possible to move along. Further, the slide cylinder 42 has a key groove 53 formed on the outer peripheral surface along a vertical direction (axial direction) over a predetermined length. On the other hand, the casing 41 is formed with a mounting hole 54 extending in the horizontal direction, the key 55 is fitted into the mounting hole 54 from the outside of the casing 41, and the tip end is fitted into the key groove 53 of the sliding cylinder 42. .. Therefore, the sliding cylinder 42 cannot rotate in the circumferential direction with respect to the casing 41 by the key 55. In this case, the length of the key groove 53 is formed longer than the maximum stroke of the sliding cylinder 42.

The cylinder 41 is integrally fixed to the upper portion of the casing 41. The cylinder portion 44 is provided with a sliding portion 56 that opens downward in the vertical direction (axial direction). The sliding portion 56 has a smaller diameter than the sliding portion 51, but is provided concentrically. The slide cylinder 42 is provided with a protruding portion 57 extending upward in the center thereof, and the protruding portion 57 has an upper end portion to which the piston 46 is integrally connected via a connecting member 58. The piston 46 is fitted into the sliding portion 56 of the casing 41 so as to be vertically movable, so that the compression chamber 59 is defined above the piston 46. Therefore, when the slide cylinder 42 rises, the piston 46 rises via the connecting member 58, and the hydraulic oil in the compression chamber 59 can be compressed.

In the present embodiment, a first hydraulic oil supply path for supplying hydraulic oil to the compression chamber 59 and a second hydraulic oil supply path for supplying hydraulic oil as lubricating oil to the cam 47 are provided.

The cylinder part 44 is provided with a hydraulic oil supply port (a hydraulic oil supply part) 61 on its side part, and the hydraulic oil supply port 61 is connected to a chamber 62. Further, the cylinder portion 44 has a working oil discharge port (working oil discharge part) 63 formed at the upper end thereof, and the working oil discharge port 63 and the compression chamber 59 are arranged in the first connecting flow path 64 along the vertical direction (axial direction). Are communicated by. Further, the cylinder portion 44 is provided so that a second connecting passage 65 passing through the center of the cylinder portion 44 and extending in the radial direction intersects with the first connecting passage 64. The second connection channel 65 has one end communicating with the chamber 62 and the other end communicating with an oil hole 66 penetrating the cylinder portion 44 in the vertical direction (axial direction). Further, a check valve 67 is provided between the second connection flow channel 65 and the chamber 62, and a relief valve 68 is provided between the second connection flow channel 65 and the oil hole 66. The check valve 67 blocks the flow of hydraulic oil from the compression chamber 59 side to the hydraulic oil supply port 61 side, and the relief valve 68 is opened when the pressure in the compression chamber 59 exceeds a predetermined pressure.

The sliding cylinder 42 is provided with a spring accommodation space 69 around the protrusion 57 and accommodates the compression coil spring 43. The compression coil spring 43 has an upper end contacting the lower surface of the cylinder portion 44 and a lower end contacting the sliding cylinder 42. Therefore, the slide cylinder 42 is biased and supported downward by the biasing force of the compression coil spring 43 with respect to the casing 41 and the cylinder portion 44. The lower end of the oil hole 66 formed in the cylinder portion 44 is open to the spring accommodating space 69. Further, the slide cylinder 42 is formed with a drain hole 70 penetrating from the spring accommodating space 69 to the roller 45 side.

Therefore, when the hydraulic oil is supplied to the hydraulic oil supply port 61, the hydraulic oil is supplied to the compression chamber 59 via the chamber 62, the check valve 67, the second connection flow path 65, and the first connection flow path 64. On the other hand, when the cam 47 rotates, the rotational force of the cam 47 is transmitted to the sliding cylinder 42 via the roller 45 as a reciprocating force. When the slide cylinder 42 reciprocates, the piston 46 also reciprocates, and compresses the hydraulic oil in the compression chamber 59 when the piston 46 rises. Then, the compressed hydraulic oil is discharged from the first connecting flow path 64 to the hydraulic oil discharge port 63.

Further, the cylinder portion 44 has a first lubricating oil supply hole (upper supply path) 71 having an upper end communicating with the chamber 62, a lower end extending downward, and opening to the casing 41 side. On the other hand, in the casing 41, the lower end communicates with the key groove 53 of the slide cylinder 42 through the communication hole 55a formed in the key 55, and the upper end extends upward to open to the cylinder portion 44 side. An oil supply hole (lower supply path) 72 is formed. The lower end of the first lubricating oil supply hole 71 communicates with the upper end of the second lubricating oil supply hole 72. The sliding cylinder 42 can supply the lubricating oil from the key groove 53 to the roller 45 and the cam 47 (see FIG. 8).

2 is a sectional view showing a sliding cylinder in the lower valve operating device, FIG. 3 is a right side view of the sliding cylinder, FIG. 4 is a left side view of the sliding cylinder, and FIG. 5 is a horizontal sectional view of the sliding cylinder. 2 is a sectional view taken along line V-V of FIG. 2, and FIG. 6 is a front view showing the lower valve operating device.

As shown in FIGS. 2 to 5, the sliding cylinder 42 is provided with a lubricating oil storage portion 80, a first lubricating oil supply passage 81, and a second lubricating oil supply passage 82.

As described above, the slide cylinder 42 has a cylindrical shape, the roller housing portion 91 for housing the roller 45 (see FIG. 1) is formed at the lower end portion thereof, and the support shaft (not shown) of the roller 45 penetrates therethrough. A support hole 92 is formed. In this case, the center line O1 of the slide cylinder 42 is provided along the vertical direction (axial direction), and the axis O2 of the roller 45 is provided along the direction orthogonal to the paper surface of FIG. The center line O1 of the roller 45 and the axis O2 of the roller 45 are substantially orthogonal to each other. The axis O2 of the roller 45 and the axis of the cam 47 coincide with each other, and thus are parallel to each other.

Further, the sliding cylinder 42 has a key groove 53 along the vertical direction formed on the outer peripheral surface thereof along the center line O1 of the sliding cylinder 42. The lubricating oil storage portion 80 is provided on the outer peripheral surface of the sliding cylinder 42 along the circumferential direction at the length of the key groove 53 (the length of the sliding cylinder 42 in the center line O1 direction). That is, the lubricating oil storage portion 80 is configured as a concave portion that dents the outer peripheral surface of the sliding cylinder 42 along the circumferential direction of the key groove 53. Therefore, when the sliding cylinder 42 is assembled to the sliding portion 51 of the casing 41, a space is formed between the recess of the sliding cylinder 42 and the inner wall surface (sliding portion 51) of the casing 41. Becomes the lubricating oil reservoir 80.

The first lubricating oil supply passage 81 is a groove portion provided in a plurality (four in the present embodiment) along the center line O1 of the sliding cylinder 42 on the outer peripheral portion of the sliding cylinder 42. In the first lubricating oil supply passage 81, an upper end portion (one end portion) in the axial direction communicates with the lubricating oil storage portion 80, and a lower end portion (the other end portion) in the axial direction extends to a midway portion of the lower end portion of the sliding cylinder 42. Has been issued. The four first lubricating oil supply passages 81 are provided at positions displaced outward from the width W of the roller 45 in the direction of the axis O2. Then, each first lubricating oil supply passage 81 is provided at a symmetrical position in the radial direction of the sliding cylinder 42 with respect to the axis O2 of the roller 45.

That is, when the direction orthogonal to the axis O2 on the plane including the axis O2 of the roller 45 is defined as the axis O3, each of the first lubricating oil supply passages 81 extends from the axis O3 to the axis O2. It is formed at a position offset by a predetermined angle θ. The positions of the first lubricating oil supply passages 81 are formed at symmetrical positions in the radial direction of the sliding cylinder 42 with respect to the shaft center line O2 of the roller 45, and also with respect to the shaft center line 3. Are formed at symmetrical positions in the radial direction.

The second lubricating oil supply passage 82 is a circumferential groove portion provided on the outer peripheral portion of the sliding cylinder 42 along the circumferential direction. A lower end of each of the first lubricating oil supply passages 81 intersects with the second lubricating oil supply passage 82 and communicates with each other, and extends further downward to form a dead end.

Therefore, as shown in FIGS. 1 and 2, when the hydraulic oil is supplied to the hydraulic oil supply port 61, the hydraulic oil is supplied to the second connection flow path 65 side through the chamber 62 and the first lubricating oil supply hole. It is supplied as lubricating oil to the 71 side. The lubricating oil (working oil) supplied to the first lubricating oil supply hole 71 side is supplied to the key groove 53 from the second lubricating oil supply hole 72, and the lubricating oil supplied to the key groove 53 is the lubricating oil reservoir. It is stored in 80. Then, the lubricating oil stored in the lubricating oil storage section 80 is supplied from each of the first lubricating oil supply passages 81 to the second lubricating oil supply passage 82 and then to the roller 45 and the cam 47.

Here, the first hydraulic oil supply path that supplies the above-described hydraulic oil to the compression chamber 59 is configured by the hydraulic oil supply port 61, the chamber 62, the second connection flow path 65, and the first connection flow path 64. On the other hand, the second hydraulic oil supply path that supplies the hydraulic oil to the cam 47 as the lubricating oil is connected to the hydraulic oil supply path in the casing 41, and the hydraulic oil supply path in the casing 41 extends along the axial direction of the casing 41. The upper end is provided so as to open toward the casing 41, and the lower end opens toward the cam 47. That is, the second hydraulic oil supply path includes the hydraulic oil supply port 61, the chamber 62, the first lubricating oil supply hole 71, the second lubricating oil supply hole 72, the key 55, the key groove 53, the lubricating oil reservoir 80, the first It comprises a lubricating oil supply passage 81 and a second lubricating oil supply passage 82.

Further, as shown in FIG. 6, the lower casing 41 and the cylinder portion 44 are fixed side by side on the upper portion of the camshaft box 101. This camshaft box 101 is provided with maintenance openings 102 for maintaining the cam 47 (see FIG. 1) and the camshaft (not shown) on the side surface corresponding to each lower casing 41 and cylinder portion 44. And is closed by the opening/closing lid 103. A hydraulic oil supply pipe 104 for supplying hydraulic oil is arranged laterally of the camshaft box 101 along the horizontal direction in which the lower casings 41 and the cylinder portions 44 are arranged. The hydraulic oil supply pipe 104 is connected to the hydraulic oil supply port 61 of each cylinder portion 44 via a supply pipe along the axial direction and each branch pipe 105 for branching the hydraulic oil from this supply pipe to each cylinder 44. ing. In this case, the hydraulic oil supply pipe 104 is arranged above each maintenance opening 102, so that it does not interfere with the maintenance work of the cam 47, the cam shaft, and the like.

As described above, in the valve gear according to the present embodiment, the casing 41 and the cylinder portion 44, the sliding cylinder 42 movably supported by the casing 41, and the piston 46 connected to the upper end of the sliding cylinder 42. A cam 47 that acts on the roller 45 at the lower end of the sliding cylinder 42 to move the sliding cylinder 42, a compression chamber 59 that compresses hydraulic oil by the movement of the piston 46, and a hydraulic oil supply port 61 provided in the cylinder portion 44. And a first hydraulic oil supply path for supplying a part of the hydraulic oil from the hydraulic oil supply opening 61 to the compression chamber 59, and a second hydraulic oil supply path for supplying the remaining hydraulic oil from the hydraulic oil supply opening 61 to the cam 47. And are provided.

Therefore, the hydraulic oil can be supplied from the single hydraulic oil supply port 61 to the compression chamber 59 and the lubricating oil as the hydraulic oil can be supplied to the cam 47, and the hydraulic oil supply pipe 104 to the hydraulic oil supply port 61, etc. The piping configuration is simplified, and the oil passage for the casing 41 and the cylinder portion 44 is also simplified. As a result, the structure can be simplified.

In the valve gear of the present embodiment, the lower casing 41 and the cylinder portion 44 are fixed to the upper portion of the camshaft box 101, and the side surface of the camshaft box 101 is provided with a maintenance opening 102 for maintaining the cam 47, and the operation is performed. A hydraulic oil supply pipe 104 for supplying hydraulic oil to the oil supply port 61 is arranged above the maintenance opening 102. Therefore, the hydraulic oil supply pipe 104 does not interfere with the operator performing the maintenance work of the cam 47 through the maintenance opening 102, and the workability can be improved.

In the valve gear of the present embodiment, the check valve 67 is provided in the second connection flow path 65 connected from the hydraulic oil supply port 61 to the compression chamber 59. Therefore, the hydraulic oil is supplied from the hydraulic oil supply port 61 to the compression chamber 59 through the second connection flow path 65, the hydraulic oil is compressed in the compression chamber 59 when the piston 46 moves up, and is discharged from the hydraulic oil discharge port 63. At this time, the working oil compressed by the check valve 67 in the compression chamber 59 does not flow back to the working oil supply port 61, and can be properly discharged from the working oil discharge port 63.

In the valve gear of the present embodiment, the cylinder portion 44 is provided with the first hydraulic oil supply hole 71 and the casing 41 is provided with the second hydraulic oil supply hole 72 as the second hydraulic oil supply path. Therefore, the supply path formed in the casing 71 and the cylinder portion 44 can be simplified.

In the valve gear of the present embodiment, the key groove 53 is provided on the outer peripheral surface of the slide cylinder 42, the key 55 fixed to the casing 41 is inserted into the key groove 53, and the key groove 53 and the communication provided in the key 55 are connected. The groove 55a is configured as a second hydraulic oil supply path. Accordingly, by inserting the key 55 fixed to the casing 41 into the key groove 53 of the slide cylinder 42, the rotation of the slide cylinder 42 can be easily stopped, and the key groove 53 and the key groove 53 serve as the second hydraulic oil supply path. By providing the communication groove 55a in 55, the structure can be simplified.

Further, in the crosshead internal combustion engine of the present embodiment, the lower valve operating device 31 and the upper valve operating device 32 that drives the exhaust valve 20 by the hydraulic oil from the lower valve operating device 31 are provided. Therefore, when the lower valve operating device 31 operates, the hydraulic oil can be supplied to the compression chamber 59 and the lubricating oil can be supplied to the cam 17. Then, the hydraulic oil can be supplied from one hydraulic oil supply port 61 to the compression chamber 59 and the lubricating oil as the hydraulic oil can be supplied to the cam 47, and the hydraulic oil supply pipe 104 to the hydraulic oil supply port 61 and the like. Is simplified, and the oil passage for the casing 41 and the cylinder portion 44 is also simplified. As a result, the structure can be simplified and the reliability of the valve train 21 is improved. be able to.

10 Diesel engine (crosshead type internal combustion engine)
11 Base Plate 12 Frame 13 Cylinder Jacket 18 Piston 19 Combustion Chamber 20 Exhaust Valve 21 Valve Operating Device 31 Lower Valve Operating Device 32 Upper Valve Operating Device 41 Casing (Device Main Body)
42 Slide cylinder 43 Compression coil spring 44 Cylinder part (apparatus body)
45 roller (roller part)
46 piston 47 cam 48 hydraulic oil pipe 53 key groove (second hydraulic oil supply path)
55 key (second hydraulic oil supply path)
59 compression chamber 61 hydraulic oil supply port (first hydraulic oil supply path, second hydraulic oil supply path)
62 chambers (first hydraulic oil supply path, second hydraulic oil supply path)
63 Hydraulic Oil Discharge Port 64 First Connection Flow Path (First Hydraulic Oil Supply Path)
65 Second connection flow path (first hydraulic oil supply path)
67 Check valve 71 First lubricating oil supply hole (second hydraulic oil supply path, upper supply path)
72 Second lubricating oil supply hole (second hydraulic oil supply path, lower supply path)
80 Lubricating Oil Reservoir (Second Hydraulic Oil Supply Path)
81 First Lubricating Oil Supply Path (Second Hydraulic Oil Supply Path)
82 Second lubricating oil supply path (second hydraulic oil supply path)
101 Cam Shaft Box 102 Maintenance Opening 103 Open/Close Lid 104 Hydraulic Oil Supply Pipe

Claims (6)

A device body including a lower casing and an upper casing,
A slide cylinder supported movably along the axial direction with respect to the lower casing,
A piston that is movably supported along the axial direction with respect to the upper casing and that moves integrally with the sliding cylinder;
A cam for moving the slide cylinder,
A hydraulic oil supply unit provided in the upper casing to supply hydraulic oil to the apparatus main body;
A compression chamber which is provided in the upper casing and which compresses a part of the hydraulic oil supplied from the hydraulic oil supply unit by the movement of the piston;
A first hydraulic oil supply path which is provided in the upper casing and supplies a part of the hydraulic oil from the hydraulic oil supply section to the compression chamber;
A second working oil supply path for supplying part of the working oil to said cam from said fluid supply portion provided to said sliding tube through the lower casing from the top casing,
Equipped with
The second hydraulic oil supply path includes a path provided along the axial direction in the upper casing and the lower casing, and a path provided in an outer peripheral portion of the sliding cylinder.
A valve operating device characterized in that The upper casing is provided on an upper portion of a camshaft box, an opening communicating with the cam is provided on a side surface of the camshaft box, and a hydraulic oil supply pipe for supplying the hydraulic oil to the hydraulic oil supply unit. The valve operating device according to claim 1, wherein is arranged above the opening. The first hydraulic oil supply path allows the flow of the hydraulic oil from the hydraulic oil supply unit to the compression chamber and prohibits the flow of the hydraulic oil from the compression chamber to the hydraulic oil supply unit. A valve is provided, and a hydraulic oil discharge portion that discharges the hydraulic oil compressed in the compression chamber is connected between the compression chamber and the check valve in the first hydraulic oil supply path. The valve operating device according to claim 1 or 2. The second hydraulic oil supply path is provided in the upper casing along the axial direction, the upper end communicates with the hydraulic oil supply section, and the lower end opens to the lower casing side; A lower supply path that is provided in the casing along the axial direction and has an upper end opening to the upper casing side so as to communicate with the upper supply path, and an outer peripheral portion of the sliding cylinder that communicates with the lower supply path. The valve operating device according to any one of claims 1 to 3, wherein the valve operating device has a path, and the path provided on the outer peripheral portion is formed so as to open toward the cam. The slide cylinder is provided with a key groove along an axial direction on an outer peripheral surface, a key fixed to the lower casing is inserted into the key groove, and the second hydraulic oil supply path in the lower casing is the key groove. The valve operating device according to any one of claims 1 to 4, further comprising a communication groove provided in the key. A lower valve operating device to which the valve operating device according to any one of claims 1 to 5 is applied,
An upper valve operating device that drives an exhaust valve with hydraulic oil from the lower valve operating device,
A crosshead internal combustion engine, comprising:

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