CN108779690B - Valve gear and crosshead internal combustion engine - Google Patents
Valve gear and crosshead internal combustion engine Download PDFInfo
- Publication number
- CN108779690B CN108779690B CN201780003716.9A CN201780003716A CN108779690B CN 108779690 B CN108779690 B CN 108779690B CN 201780003716 A CN201780003716 A CN 201780003716A CN 108779690 B CN108779690 B CN 108779690B
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- Prior art keywords
- oil supply
- working oil
- hydraulic oil
- housing
- supply path
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
- F01M9/10—Lubrication of valve gear or auxiliaries
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
A valve gear and a crosshead internal combustion engine are provided with: a housing (41) and a cylinder section (44); a slide cylinder (42), wherein the slide cylinder (42) is movably supported by the housing (41); a piston (46), wherein the piston (46) is connected with the upper end part of the sliding cylinder (42); a cam (47), wherein the cam (47) can act on the roller (45) at the lower end part of the sliding cylinder (42) to move the sliding cylinder (42); a compression chamber (59) in which the working oil can be compressed by the movement of the piston (46); a working oil supply port (61), the working oil supply port (61) being provided in the upper housing (41); a first working oil supply path for supplying working oil from a working oil supply port (61) to the compression chamber (59); and a second working oil supply path for supplying working oil from the working oil supply port (61) to the cam (47).
Description
Technical Field
The present invention relates to a valve gear 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 having the valve gear.
Background
In a crosshead type internal combustion engine, a valve train device that opens and closes an exhaust valve includes a lower valve train device and an upper valve train device. The valve operating system supplies the hydraulic oil compressed in the lower valve operating system to the upper valve operating system, and presses the exhaust valve downward against the biasing force of the air spring by the driving force of the transmitted hydraulic oil to open and close the exhaust valve in the closed state. In the lower valve train device, a slide cylinder is supported to be movable in the vertical direction, and the slide cylinder is biased downward by a spring in a housing. The slide cylinder is pushed up by the cam to raise the piston, thereby compressing and supplying the working oil.
A conventional valve operating system has a structure described in patent document 1 below, for example.
Documents of the prior art
Patent document 1: japanese patent laid-open publication No. 2015-098795
Problems to be solved by the invention
In the lower valve gear, since the cam portion of the rotating cam pushes up the slide cylinder via the roller, it is necessary to supply lubricating oil to the sliding surface between the cam and the roller. Conventionally, a part of the hydraulic oil supplied to the upper valve train device for driving the exhaust valve is supplied as lubricating oil to the cam or the roller. That is, a pipe for supplying hydraulic oil (lubricant oil) from the outside is provided in a camshaft housing that houses a slide cylinder, a cam, and the like, and the pipe for supplying hydraulic oil from the outside is connected to a cylinder that houses a piston. Therefore, a plurality of pipes are required, and there is a problem that the structure becomes complicated and the manufacturing cost increases.
Disclosure of Invention
The present invention has been made to solve the above-described problems, and an object thereof is to provide a valve operating system and a crosshead internal combustion engine that simplify the structure.
Means for solving the problems
The valve operating device of the present invention for achieving the above object includes: a device body including a lower case and an upper case; a slide cylinder supported by the lower housing so as to be movable in an axial direction; a piston supported by the upper housing so as to be movable in an axial direction and moving integrally with the slide cylinder; a cam that moves the slide cylinder; and a hydraulic oil supply unit that is provided in the upper housing and supplies hydraulic oil to the apparatus main body, wherein a compression chamber that compresses a part of the hydraulic oil supplied from the hydraulic oil supply unit by movement of the piston, a first hydraulic oil supply path that supplies the part of the hydraulic oil from the hydraulic oil supply unit to the compression chamber, and a second hydraulic oil supply path that supplies the other part of the hydraulic oil from the hydraulic oil supply unit to the lower housing are formed in the upper housing.
Therefore, when the cam rotates, the slide cylinder reciprocates in the axial direction due to the rotational force of the cam, and the piston reciprocates integrally with the slide cylinder. Then, the working oil supplied from the working oil supply unit to the compression chamber through the first working oil supply path is compressed and discharged. The working oil supplied from the working oil supply unit through the second working oil supply path is supplied to the cam to lubricate the cam. Here, by providing the first hydraulic oil supply path for supplying the hydraulic oil from the one hydraulic oil supply unit to the compression chamber and providing the second hydraulic oil supply path for supplying the hydraulic oil to the cam, the piping structure connected to the hydraulic oil supply unit is simplified, and the oil passage processing to the apparatus main body is also simplified, and as a result, the structure can be simplified.
In the valve operating device according to the present invention, the upper housing is provided at an upper portion of the camshaft housing, an opening portion communicating with the cam is provided at a side surface of the camshaft housing, and a hydraulic oil supply pipe for supplying the hydraulic oil to the hydraulic oil supply portion is disposed above the opening portion.
Therefore, by disposing the hydraulic oil supply pipe for supplying the hydraulic oil to the hydraulic oil supply portion above the opening, the hydraulic oil supply pipe does not interfere with an operator who performs various operations on the cam from the opening, and the operability can be improved.
In the valve operating device according to the present invention, the first hydraulic oil supply path is provided with a check valve that permits 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, and the compression chamber and the check valve in the first hydraulic oil supply path communicate with a hydraulic oil discharge unit that discharges the hydraulic oil compressed in the compression chamber.
Therefore, when the working oil is supplied to the working oil supply unit, the working oil is supplied to the compression chamber through the first working oil supply path, and when the piston rises, the working oil is compressed in the compression chamber and discharged from the working oil discharge unit. In this case, by providing the check valve in the first hydraulic oil supply path, the hydraulic oil compressed in the compression chamber can be appropriately discharged from the hydraulic oil discharge unit without returning to the hydraulic oil supply unit.
In the valve gear of the present invention, wherein the lower housing side opening portion in the second working oil supply path is connected to a working oil supply path in the lower housing, the working oil supply path in the lower housing is formed to be provided in the axial direction in the lower housing, and an upper end portion of the working oil supply path is opened in the upper housing side, and a lower end portion of the working oil supply path is opened toward the cam.
Therefore, by providing the upper supply path of the upper housing and the lower supply path of the lower housing as the second hydraulic oil supply path, the supply path formed in the apparatus main body can be simplified.
In the valve operating device according to the present invention, a key groove is provided along an axial direction on an outer peripheral surface of the sliding tube, a key fixed to the lower housing is inserted into the key groove, and the working oil supply path in the lower housing has the key groove and a communication groove provided in the key.
Therefore, the rotation of the slide cylinder can be easily stopped by inserting the key fixed to the lower housing into the key groove of the slide cylinder, and the structure can be simplified by providing the key groove and the communicating groove in the key as the lower supply path.
Further, a crosshead internal combustion engine according to the present invention includes: a lower valve gear to which the valve gear is applied; and an upper valve gear that drives an exhaust valve by working oil from the lower valve gear.
Therefore, in the lower valve gear, when the cam rotates, the slide cylinder reciprocates in the axial direction due to the rotational force of the cam, and the piston reciprocates integrally with the slide cylinder. Then, the working oil supplied from the working oil supply unit to the compression chamber through the first working oil supply path is compressed and discharged. The working oil supplied from the working oil supply unit through the second working oil supply path is supplied to the cam to lubricate the cam. Here, by providing the first hydraulic oil supply path for supplying the hydraulic oil from the one hydraulic oil supply unit to the compression chamber and providing the second hydraulic oil supply path for supplying the hydraulic oil to the cam, the piping structure connected to the hydraulic oil supply unit is simplified, and the oil passage processing to the apparatus main body is also simplified, and as a result, the structure can be simplified.
Effects of the invention
According to the valve gear and the crosshead internal combustion engine of the present invention, simplification of the structure can be achieved.
Drawings
Fig. 1 is a sectional view showing a lower valve gear of the present embodiment.
Fig. 2 is a sectional view showing a slide cylinder of the lower valve gear.
Fig. 3 is a right side view of the slide cylinder.
Fig. 4 is a left side view of the slide cartridge.
Fig. 5 is a V-V sectional view of fig. 2 showing a horizontal section of the slide cylinder.
Fig. 6 is a front view showing the lower valve gear.
Fig. 7 is a schematic diagram showing a diesel engine.
Fig. 8 is a schematic diagram showing a valve operating system according to the present embodiment.
Detailed Description
Preferred embodiments of a valve gear and a crosshead internal combustion engine according to the present invention will be described in detail below with reference to the accompanying drawings. The present invention is not limited to this embodiment, and when there are a plurality of embodiments, the present invention also includes a combination of the embodiments.
Fig. 7 is a schematic diagram showing a diesel engine.
In the present embodiment, the diesel engine 10 is, for example, a two-stroke one-cycle one-way scavenging crosshead type internal combustion engine used as a main engine for propelling a ship, as shown in fig. 7. The diesel engine 10 includes: a platen 11 located below, a frame 12 provided on the platen 11, and a cylinder jacket 13 provided on the frame 12. The platen 11, the frame 12, and the cylinder jacket 13 are integrally fastened and fixed by a plurality of tie bolts 14 and nuts 15 extending in the vertical direction.
The cylinder liner 16 and the cylinder head 17 define a space, and a piston 18 is provided in the space so as to be vertically reciprocated, thereby forming a combustion chamber 19. The cylinder head 17 is provided with an exhaust valve 20 which can be opened and closed by a valve gear 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 head 17 constitute a combustion apparatus.
Therefore, the fuel (for example, low-quality oil, natural gas, or a mixture thereof) supplied from a fuel injection pump (not shown) and the combustion gas (for example, air, EGR gas, or a mixture thereof) compressed by a compressor (not shown) are supplied to the combustion chamber 19 to be combusted. The piston 18 is moved up and down by the energy generated by this combustion. At this time, when the combustion chamber 19 is opened by the exhaust valve 20, exhaust gas generated by combustion is pushed out to the exhaust pipe 22, and 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 platen 11 constitutes a crankcase, and is provided with a bearing 25 for rotatably supporting the crankshaft 24. The crankshaft 24 is rotatably connected to a lower end portion of a connecting rod 27 via a crank 26. In the frame 12, a pair of guide plates 28 extending in the vertical direction are fixed at a predetermined interval, and a crosshead 29 is supported between the pair of guide plates 28 so as to be movable in the vertical direction. The crosshead 29 is connected to the lower end portion of the piston rod 23 and the upper end portion of the connecting rod 27.
Therefore, the piston 18 to which energy is transmitted from the combustion chamber 19 is pressed down in the direction of the installation surface of the diesel engine 10 (the direction toward the platen 11, that is, downward in the vertical direction) together with the piston rod 23. Then, the piston rod 23 presses the crosshead 29 downward 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 a valve operating system according to the present embodiment.
As shown in fig. 8, the valve gear 21 has a lower valve gear 31 and an upper valve gear 32. The valve operating system 21 supplies the hydraulic oil compressed in the lower valve operating system 31 to the upper valve operating system 32, and pushes down the exhaust valve 20 using the driving force of the transmitted hydraulic oil to open and close the exhaust valve 20 in the closed state.
In the upper valve gear 32, the exhaust valve 20 is composed of a shaft portion 20a and an umbrella portion 20b, and is movably supported by a housing 33 fixed to the cylinder head 17. In the upper valve operating system 32, the shaft portion 20a is urged upward by the air spring 34, and the exhaust valve 20 closes the space between the combustion chamber 19 and the exhaust pipe 22. The upper valve train device 32 includes a cylinder portion 35 and a piston 36 in addition to the air spring 34, the cylinder portion 35 receives the hydraulic oil supplied from the lower valve train device 31, and the piston 36 is provided to be movable in the cylinder portion 35. The piston 36 is integrally fixed to the upper end portion of the shaft portion 20a, whereby the piston 36 moves up and down integrally with the exhaust valve 20.
In the housing (lower housing, device body) 41 of the lower valve operating device 31, a slide cylinder 42 is supported to be movable in the vertical direction (axial direction), and the slide cylinder 42 is supported to be biased downward by the biasing force of a compression coil spring 43. A cylinder portion (upper housing, device body) 44 is provided at an upper portion of the housing 41, and both are fastened by a plurality of bolts (not shown). The slide cylinder 42 is provided with a roller (roller portion) 45 at a lower end portion thereof so as to be rotatable, and a piston 46 is connected to an upper end portion thereof, and the piston 46 is provided in a cylinder portion 44 so as to be movable in the vertical direction (axial direction). On the other hand, in the housing 41, a cam 47 that contacts the roller 45 is disposed below the slide 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, in the lower valve operating device 31, when the rotating cam 47 pushes up the sliding cylinder 42 via the roller 45, the piston 46 compresses the working 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. In the upper valve operating system 32, when the hydraulic oil is supplied to the cylinder portion 35, the piston 36 is pressed down, and the exhaust valve 20 is lowered against the biasing force of the air spring 34, thereby communicating the combustion chamber 19 in a closed state with the exhaust pipe 22.
The lower valve train device 31 will be described in detail below. Fig. 1 is a sectional view showing a lower valve gear of the present embodiment.
In the lower valve gear 31, as shown in fig. 1, the housing 41 has a cylindrical shape, and a slide portion 51 along the vertical direction (axial direction) is provided so as to be opened vertically. The slide cylinder 42 is fitted to the slide portion 51 of the housing 41, and the slide cylinder 42 is supported to be movable in the vertical direction (axial direction). The roller 45 is rotatably attached to the lower end portion of the slide cylinder 42 along the support shaft 52 in the direction orthogonal to the axial direction, and the slide cylinder 42 and the roller 45 can move in the vertical direction (axial direction) integrally. A key groove 53 is formed in an outer peripheral surface of the slide cylinder 42 by a predetermined length, and the key groove 53 extends in the vertical direction (axial direction). On the other hand, the housing 41 is formed with a mounting hole 54 along the horizontal direction, a key 55 is fitted into the mounting hole 54 from the outside of the housing 41, and the tip end portion of the key 55 is fitted into the key groove 53 of the slide cylinder 42. Therefore, the slide cylinder 42 cannot rotate in the circumferential direction with respect to the housing 41 due to the key 55. In this case, the length of the key groove 53 is formed longer than the maximum stroke of the slide cylinder 42.
A cylinder portion 44 is integrally fixed to an upper portion of the housing 41. The sliding portion 56 of the cylinder portion 44 in the up-down direction (axial direction) is provided so as to open downward. The sliding portion 56 has a smaller diameter than the sliding portion 51, but the sliding portion 56 is provided concentrically with the sliding portion 51. A projection 57 extending upward is provided at the center of the slide cylinder 42, and the piston 46 is integrally connected to the upper end of the projection 57 via a connecting member 58. The piston 46 is fitted to the sliding portion 56 of the housing 41 so as to be movable up and down, and a compression chamber 59 is defined above the piston 46. Therefore, when the slide cylinder 42 is raised, the piston 46 is raised via the coupling 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.
A working oil supply port (working oil supply portion) 61 is provided at a side portion of the cylinder portion 44, and the working oil supply port 61 is connected to the chamber 62. A working oil discharge port (working oil discharge portion) 63 is formed at an upper end portion of the cylinder portion 44, and the working oil discharge port 63 and the compression chamber 59 communicate with each other through a first connecting passage 64 extending in the vertical direction (axial direction). Further, the cylinder portion 44 is provided such that a second connecting passage 65 passing through the center of the cylinder portion 44 in the radial direction intersects the first connecting passage 64. One end of the second connecting passage 65 communicates with the chamber 62, the other end communicates with the oil hole 66, and the oil hole 66 penetrates the cylinder portion 44 in the vertical direction (axial direction). A check valve 67 is provided between the second connection flow path 65 and the chamber 62, and a relief valve 68 is provided between the second connection flow path 65 and the oil hole 66. The check valve 67 prevents the flow of the hydraulic oil from the compression chamber 59 side to the hydraulic oil supply port 61 side, and opens the relief valve 68 when the pressure of the compression chamber 59 exceeds a predetermined pressure.
The slide cylinder 42 is provided with a spring housing space 69 around the projection 57, and houses the compression coil spring 43. The compression coil spring 43 has an upper end portion in contact with the lower surface of the cylinder portion 44 and a lower end portion in contact with the slide cylinder 42. Therefore, the slide tube 42 is biased downward with respect to the housing 41 and the cylinder portion 44 by the biasing force of the compression coil spring 43. Further, the lower end portion of the oil hole 66 formed in the cylinder portion 44 is opened in the spring housing space portion 69. The slide cylinder 42 is formed with a discharge hole 70 penetrating from the spring housing space 69 to the roller 45 side.
Therefore, when the working oil is supplied to the working oil supply port 61, the working 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 slide cylinder 42 as a reciprocating force via the roller 45. When the slide cylinder 42 reciprocates, the piston 46 likewise reciprocates, and the working oil in the compression chamber 59 is compressed when the piston 46 ascends. The compressed hydraulic oil is discharged from the first connecting passage 64 to the hydraulic oil discharge port 63.
An upper end portion of the cylinder portion 44 communicates with the chamber 62, and a lower end portion of the cylinder portion 44 is formed with a first lubricant supply hole (upper supply passage) 71 extending downward and opening on the housing 41 side. On the other hand, the lower end portion of the housing 41 communicates with the key groove 53 of the slide cylinder 42 via the communication groove 55a formed in the key 55, the upper end portion of the housing 41 is formed with a second lubricant oil supply hole (lower supply path) 72, and the second lubricant oil supply hole 72 extends upward and opens on the side of the cylinder portion 44. The lower end of the first lubricant oil supply hole 71 communicates with the upper end of the second lubricant oil supply hole 72. Then, the sliding tube 42 can supply the lubricating oil from the key groove 53 to the roller 45 and the cam 47 (see fig. 8).
Fig. 2 is a sectional view showing a slide cylinder of the lower valve gear, fig. 3 is a right side view of the slide cylinder, fig. 4 is a left side view of the slide cylinder, fig. 5 is a V-V sectional view of fig. 2 showing a horizontal section of the slide cylinder, and fig. 6 is a front view showing the lower valve gear.
As shown in fig. 2 to 5, the slide cylinder 42 is provided with a lubricant reservoir 80, a first lubricant supply passage 81, and a second lubricant supply passage 82.
As described above, the slide cylinder 42 has a cylindrical shape, the roller housing 91 for housing the roller 45 (see fig. 1) is formed at the lower end of the slide cylinder 42, and the support hole 92 through which the support shaft (not shown) of the roller 45 passes is formed in the slide cylinder 42. In this case, the center line O1 of the slide cylinder 42 is provided along the vertical direction (axial direction), the axis line O2 of the roller 45 is provided along the direction perpendicular to the paper surface of fig. 2, and the center line O1 of the slide cylinder 42 is substantially perpendicular to the axis line O2 of the roller 45. The axis O2 of the roller 45 is parallel to the axis of the cam 47.
The key groove 53 along the vertical direction on the outer peripheral surface of the slide cylinder 42 is formed along the center line O1 of the slide cylinder 42. The lubricant oil reservoir 80 is provided on the outer peripheral surface of the slide cylinder 42 along the circumferential direction by the length of the key groove 53 (the length in the direction of the center line O1 of the slide cylinder 42). That is, the lubricant oil reservoir 80 is configured as a concave portion that is recessed in the outer peripheral surface of the slide cylinder 42 along the circumferential direction of the key groove 53. Therefore, when the slide cylinder 42 is assembled to the slide portion 51 of the housing 41, a space portion is formed between the recess of the slide cylinder 42 and the inner wall surface (slide portion 51) of the housing 41, and this space portion serves as the lubricating oil reservoir portion 80.
The first lubricant oil supply passage 81 is formed by a plurality of (four in the present embodiment) groove portions provided along the center line O1 of the slide cylinder 42 in the outer peripheral portion of the slide cylinder 42. An axial upper end portion (one end portion) of the first lubricant supply passage 81 communicates with the lubricant reservoir 80, and an axial lower end portion (the other end portion) of the first lubricant supply passage 81 extends to a middle portion of the lower end portion of the slide cylinder 42. The four first lubricating oil supply passages 81 are provided at positions shifted outward from the width W in the direction of the axis O2 of the roller 45. The first lubricating oil supply passages 81 are provided at positions symmetrical in the radial direction of the slide cylinder 42 with respect to the axial line O2 of the roller 45.
That is, when the direction perpendicular to the shaft axis O2 is defined as the shaft axis O3 on the plane including the shaft axis O2 of the roller 45, each first lubricating oil supply passage 81 is formed at a position shifted by a predetermined angle θ from the shaft axis O3 to the shaft axis O2 side. The positions of the first lubricating oil supply passages 81 are formed at positions symmetrical in the radial direction of the slide cylinder 42 with respect to the axial line O2 of the roller 45, and also at positions symmetrical in the radial direction of the slide cylinder 42 with respect to the axial line 3.
The second lubricant oil supply path 82 is a circumferential groove portion provided along the circumferential direction on the outer circumferential portion of the slide cylinder 42. The lower end of each first lubricating oil supply passage 81 intersects with and communicates with the second lubricating oil supply passage 82, and extends to a position further below to be terminated.
Therefore, as shown in fig. 1 and 2, when the working oil is supplied to the working oil supply port 61, the working oil is supplied to the second connection flow path 65 side via the chamber 62, and the working oil is supplied as the lubricating oil to the first lubricating oil supply hole 71 side. The lubricating oil (working oil) supplied to the first lubricating oil supply hole 71 side is supplied from the second lubricating oil supply hole 72 to the key groove 53, and the lubricating oil supplied to the key groove 53 is stored in the lubricating oil reservoir portion 80. The lubricant oil stored in the lubricant oil storage portion 80 is supplied from each first lubricant oil supply passage 81 to the second lubricant oil supply passage 82 and to the roller 45 and the cam 47.
Here, the first hydraulic oil supply path for supplying the above-described hydraulic oil to the compression chamber 59 is constituted 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, a second working oil supply path that supplies working oil as lubricating oil to the cam 47 is connected to a working oil supply path in the housing 41, the working oil supply path in the housing 41 being formed so as to be provided in the axial direction in the housing 41 with an upper end portion opening on the housing 41 side and a lower end portion opening toward the cam 47. That is, the second working oil supply path is constituted by the working oil supply port 61, the chamber 62, the first lubricant oil supply hole 71, the second lubricant oil supply hole 72, the key 55, the key groove 53, the lubricant oil reservoir 80, the first lubricant oil supply passage 81, and the second lubricant oil supply passage 82.
As shown in fig. 6, the housing 41 and the cylinder portion 44 are fixed in line on the upper portion of the camshaft housing 101. On the side surface of the camshaft housing 101, maintenance openings 102 for maintaining the cams 47 (see fig. 1), the camshafts (not shown), and the like are provided corresponding to the housings 41 and the cylinder sections 44, and the maintenance openings 102 are closed by opening/closing covers 103. The hydraulic oil supply pipe 104 for supplying hydraulic oil is disposed on the side of the camshaft housing 101 along the horizontal direction in which the housings 41 and the cylinder sections 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 extending in the axial direction and each branch pipe 105 that branches the hydraulic oil from the supply pipe to each cylinder portion 44. In this case, the working oil supply pipe 104 is disposed above each of the maintenance openings 102, so that maintenance work of the cam 47, the camshaft, and the like is not hindered.
As described above, the valve operating device according to the present embodiment includes: a housing 41 and a cylinder portion 44; a slide cylinder 42 movably supported by the housing 41; a piston 46 connected to an upper end portion of the slide cylinder 42; a cam 47 acting on a roller 45 at the lower end of the slide cylinder 42 to move the slide cylinder 42; a compression chamber 59 for compressing the working oil by the movement of the piston 46; a working oil supply port 61 provided in the cylinder portion 44; a first working oil supply path for supplying a part of the working oil from the working oil supply port 61 to the compression chamber 59; and a second hydraulic oil supply path for supplying surplus hydraulic oil from the hydraulic oil supply port 61 to the cam 47.
Therefore, the working oil can be supplied from the single working oil supply port 61 to the compression chamber 59, and the lubricating oil as the working oil can be supplied to the cam 47, so that the piping structure of the working oil supply piping 104 and the like connected to the working oil supply port 61 is simplified, and the oil passage processing of the housing 41 and the cylinder portion 44 is also simplified, and as a result, the structure can be simplified.
In the valve operating device of the present embodiment, the housing 41 and the cylinder portion 44 are fixed to the upper portion of the camshaft housing 101, a maintenance opening 102 for maintaining the cam 47 is provided in the side surface of the camshaft housing 101, and a hydraulic oil supply pipe 104 for supplying hydraulic oil to the hydraulic oil supply port 61 is disposed above the maintenance opening 102. Therefore, the working oil supply pipe 104 does not interfere with the operator who performs the maintenance operation of the cam 47 through the maintenance opening 102, and the operability can be improved.
In the valve operating device of the present embodiment, a check valve 67 is provided in the second connecting passage 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 connecting passage 65, and is compressed in the compression chamber 59 and discharged from the hydraulic oil discharge port 63 when the piston 46 moves up. At this time, the working oil compressed in the compression chamber 59 can be appropriately discharged from the working oil discharge port 63 without flowing back to the working oil supply port 61 by the check valve 67.
In the valve gear system of the present embodiment, the cylinder portion 44 is provided with the first lubricating oil supply hole 71 and the housing 41 is provided with the second lubricating oil supply hole 72 as the second working oil supply path. Therefore, the supply paths formed in the housing 41 and the cylinder section 44 can be simplified.
In the valve operating device 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 housing 41 is inserted into the key groove 53, and the key groove 53 and the communication groove 55a provided in the key 55 constitute the second hydraulic oil supply path. Therefore, the key 55 fixed to the housing 41 is inserted into the key groove 53 of the slide cylinder 42, so that the slide cylinder 42 can be easily prevented from rotating, and the key groove 53 and the communication groove 55a in the key 55 are provided as the second hydraulic oil supply path, so that the structure can be simplified.
In the crosshead internal combustion engine of the present embodiment, a lower valve train device 31 and an upper valve train device 32 that drives the exhaust valve 20 with hydraulic oil from the lower valve train device 31 are provided. Therefore, when the lower valve gear 31 is operated, the working oil can be supplied to the compression chamber 59 and the lubricating oil can be supplied to the cam 47. Further, the working oil can be supplied from the single working oil supply port 61 to the compression chamber 59, and the lubricating oil as the working oil can be supplied to the cam 47, so that the piping structure of the working oil supply piping 104 and the like connected to the working oil supply port 61 is simplified, and the oil passage processing of the housing 41 and the cylinder portion 44 is also simplified, and as a result, the structure can be simplified, and the reliability of the valve train 21 can be improved.
Description of the symbols
10 Diesel engine (crosshead type internal combustion engine)
11 bedplate
12 framework
13 cylinder jacket
18 piston
19 combustion chamber
20 exhaust valve
21 valve gear
31 lower valve gear
32 upper valve gear
41 outer cover (device body)
42 sliding cylinder
43 compression coil spring
44 air cylinder part (device main body)
45 roller (roller part)
46 piston
47 cam
48 working oil piping
53 Key groove (second working oil supply path)
Key 55 (second working oil supply path)
59 compression chamber
61 working oil supply port (first working oil supply passage, second working oil supply passage)
62 Chamber (first working oil supply passage, second working oil supply passage)
63 working oil outlet
64 first connecting flow path (first working oil supply path)
65 second connecting passage (first working oil supply passage)
67 check valve
71 first lubricating oil supply hole (second working oil supply path, upper supply path)
72 second lubricating oil supply hole (second working oil supply path, lower supply path)
80 lubricating oil reservoir (second working oil supply path)
81 first lubricating oil supply passage (second working oil supply passage)
82 second lubricating oil supply passage (second working oil supply passage)
101 camshaft housing
102 opening for maintenance
103 open/close cover
104 working oil supply pipe
Claims (6)
1. A valve gear, characterized by comprising:
a device body including a lower case and an upper case;
a slide cylinder supported by the lower housing so as to be movable in an axial direction;
a piston supported by the upper housing so as to be movable in an axial direction and moving integrally with the slide cylinder;
a cam that moves the slide cylinder; and
a working oil supply unit provided in the upper case and configured to supply working oil to the apparatus main body,
a compression chamber, a first working oil supply path, and a second working oil supply path are formed in the upper housing,
the compression chamber compresses a part of the working oil supplied from the working oil supply unit by the movement of the piston,
the first working oil supply path supplies a part of the working oil from the working oil supply unit to the compression chamber,
the second working oil supply path supplies the other part of the working oil from the working oil supply portion to the lower casing,
the second hydraulic oil supply path includes: a path axially defined in said lower housing; and a groove portion provided on an outer peripheral surface of the slide cylinder in the axial direction and having one end portion communicating with a part of the path provided in the lower housing in the axial direction.
2. A valve gear according to claim 1,
the upper housing is provided at an upper portion of the camshaft housing, an opening portion communicating with the cam is provided at a side surface of the camshaft housing, and a hydraulic oil supply pipe for supplying the hydraulic oil to the hydraulic oil supply portion is disposed above the opening portion.
3. A valve gear according to claim 1 or 2,
the first hydraulic oil supply path is provided with a check valve that permits 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, and the first hydraulic oil supply path communicates between the compression chamber and the check valve with a hydraulic oil discharge unit that discharges the hydraulic oil compressed in the compression chamber.
4. A valve gear according to claim 1 or 2,
an opening portion on the lower casing side in the second working oil supply path is connected to a working oil supply path in the lower casing,
a working oil supply path in the lower housing is formed to be provided in the axial direction in the lower housing, and an upper end portion of the working oil supply path is opened at the upper housing side, and a lower end portion of the working oil supply path is opened toward the cam.
5. A valve gear according to claim 4,
a key groove is formed in an outer peripheral surface of the slide cylinder in an axial direction, a key fixed to the lower housing is inserted into the key groove, and the working oil supply path in the lower housing includes the key groove and a communication groove provided in the key.
6. A crosshead internal combustion engine, characterized by comprising:
a lower valve gear to which the valve gear of any one of claim 1 to claim 5 is applied; and
and an upper valve operating device that drives the exhaust valve by the working oil from the lower valve operating device.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016044944A JP6703868B2 (en) | 2016-03-08 | 2016-03-08 | Valve gear and crosshead internal combustion engine |
| JP2016-044944 | 2016-03-08 | ||
| PCT/JP2017/008116 WO2017154697A1 (en) | 2016-03-08 | 2017-03-01 | Valve gear and crosshead-type internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108779690A CN108779690A (en) | 2018-11-09 |
| CN108779690B true CN108779690B (en) | 2020-09-11 |
Family
ID=59789397
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780003716.9A Active CN108779690B (en) | 2016-03-08 | 2017-03-01 | Valve gear and crosshead internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6703868B2 (en) |
| KR (1) | KR102124752B1 (en) |
| CN (1) | CN108779690B (en) |
| WO (1) | WO2017154697A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7483492B2 (en) * | 2020-05-15 | 2024-05-15 | 株式会社ジャパンエンジンコーポレーション | Crankshafts and marine engines |
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|---|---|---|---|---|
| JPS55117015A (en) * | 1979-02-28 | 1980-09-09 | Yamaha Motor Co Ltd | Engine |
| JPS61265318A (en) * | 1985-05-20 | 1986-11-25 | Mitsubishi Heavy Ind Ltd | Valve driving device |
| JPH0614414U (en) * | 1991-05-30 | 1994-02-25 | 自動車部品工業株式会社 | Engine hydraulic valve drive |
| JP2000018013A (en) * | 1998-07-03 | 2000-01-18 | Mitsubishi Heavy Ind Ltd | Compression ratio regulator for internal combustion engine |
| CN101415936A (en) * | 2006-04-12 | 2009-04-22 | 曼狄赛尔公司 | Crosshead type large-sized uniflow type two-stroke diesel motor |
| CN102112708A (en) * | 2008-07-14 | 2011-06-29 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Cam driven exhaust valve actuation system for large two stroke diesel engine |
| CN102859125A (en) * | 2010-04-30 | 2013-01-02 | 瓦锡兰芬兰有限公司 | Control arrangement for a gas exchange valve in a piston engine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5412611U (en) * | 1977-06-29 | 1979-01-26 | ||
| JP6091008B2 (en) | 2013-11-18 | 2017-03-08 | 三菱重工業株式会社 | Exhaust valve valve mechanism, diesel engine, and exhaust valve cooling method for exhaust valve valve mechanism |
| KR101911102B1 (en) * | 2013-12-06 | 2018-10-23 | 현대중공업 주식회사 | Variable valve timing apparatus |
-
2016
- 2016-03-08 JP JP2016044944A patent/JP6703868B2/en active Active
-
2017
- 2017-03-01 KR KR1020187011038A patent/KR102124752B1/en active IP Right Grant
- 2017-03-01 WO PCT/JP2017/008116 patent/WO2017154697A1/en active Application Filing
- 2017-03-01 CN CN201780003716.9A patent/CN108779690B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55117015A (en) * | 1979-02-28 | 1980-09-09 | Yamaha Motor Co Ltd | Engine |
| JPS61265318A (en) * | 1985-05-20 | 1986-11-25 | Mitsubishi Heavy Ind Ltd | Valve driving device |
| JPH0614414U (en) * | 1991-05-30 | 1994-02-25 | 自動車部品工業株式会社 | Engine hydraulic valve drive |
| JP2000018013A (en) * | 1998-07-03 | 2000-01-18 | Mitsubishi Heavy Ind Ltd | Compression ratio regulator for internal combustion engine |
| CN101415936A (en) * | 2006-04-12 | 2009-04-22 | 曼狄赛尔公司 | Crosshead type large-sized uniflow type two-stroke diesel motor |
| CN102112708A (en) * | 2008-07-14 | 2011-06-29 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Cam driven exhaust valve actuation system for large two stroke diesel engine |
| CN102859125A (en) * | 2010-04-30 | 2013-01-02 | 瓦锡兰芬兰有限公司 | Control arrangement for a gas exchange valve in a piston engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108779690A (en) | 2018-11-09 |
| KR102124752B1 (en) | 2020-06-19 |
| WO2017154697A1 (en) | 2017-09-14 |
| KR20180054789A (en) | 2018-05-24 |
| JP6703868B2 (en) | 2020-06-03 |
| JP2017160824A (en) | 2017-09-14 |
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