WO2015182414A1 - Exhaust static tube support structure and internal combustion engine equipped with same - Google Patents

Exhaust static tube support structure and internal combustion engine equipped with same Download PDF

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Publication number
WO2015182414A1
WO2015182414A1 PCT/JP2015/064140 JP2015064140W WO2015182414A1 WO 2015182414 A1 WO2015182414 A1 WO 2015182414A1 JP 2015064140 W JP2015064140 W JP 2015064140W WO 2015182414 A1 WO2015182414 A1 WO 2015182414A1
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WO
WIPO (PCT)
Prior art keywords
plate
static pressure
exhaust static
pressure pipe
exhaust
Prior art date
Application number
PCT/JP2015/064140
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French (fr)
Japanese (ja)
Inventor
信幸 國弘
Original Assignee
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to KR1020167022182A priority Critical patent/KR101814317B1/en
Priority to CN201580008880.XA priority patent/CN106460640B/en
Publication of WO2015182414A1 publication Critical patent/WO2015182414A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to an exhaust static pressure pipe support structure that supports an exhaust static pressure pipe that guides exhaust gas to a turbocharger that is, for example, a static pressure type, and an internal combustion engine including the exhaust static pressure pipe support structure.
  • a static pressure supercharger is used for a large two-stroke diesel engine (internal combustion engine) used as a marine main engine.
  • the static pressure supercharger is connected to an exhaust static pressure pipe that temporarily stores the exhaust gas before being introduced into the supercharger.
  • the exhaust static pressure pipe is a container having a predetermined capacity in order to suppress pulsation of exhaust gas discharged from each cylinder of the diesel engine.
  • the exhaust static pressure pipe is also referred to as an exhaust gas receiver or an exhaust gas manifold. Since such an exhaust static pressure pipe receives a load due to its own weight and gas pressure generated from each cylinder side, the exhaust static pressure pipe is supported by a support plate and a flexible plate with respect to the diesel engine body (see Patent Document 1 below). .
  • the support plate mainly supports the weight of the exhaust static pressure tube by supporting the exhaust static pressure tube from below. Furthermore, since the support plate is disposed along the longitudinal direction of the exhaust static pressure pipe and has rigidity in the longitudinal direction, vibration in the longitudinal direction of the exhaust static pressure pipe can be suppressed.
  • a plurality of flexible plates are provided on both sides of the support plate with a predetermined interval in the longitudinal direction of the exhaust static pressure tube.
  • the flexible plate 50 is provided between the exhaust static pressure tube 14 and the scavenging trunk 20 and supports the exhaust static pressure tube 14 from below to Supports load due to weight and gas pressure.
  • the flexible plate 50 is constituted by a pair of plates 50a arranged in a lateral direction (perpendicular to the paper surface in FIG. 8) perpendicular to the longitudinal direction of the exhaust static pressure pipe 14, the lateral direction of the exhaust static pressure pipe 14 The vibration of the can be suppressed.
  • the flexible plate 50 since the flexible plate 50 is disposed in the lateral direction of the exhaust static pressure tube 14, it can be deformed by being bent in the longitudinal direction of the exhaust static pressure tube 14 as shown in FIG. It has become. As a result, the flexible plate 50 can allow expansion and contraction in the longitudinal direction due to heat of the exhaust static pressure tube 14.
  • the exhaust static pressure pipe and the fixed position of the diesel engine main body (for example, the scavenging trunk) that supports the exhaust static pressure pipe from below are The distance tends to be longer. For this reason, the length of the up-down direction of the support plate and flexible plate which support an exhaust static pressure pipe from the bottom becomes long. As a result, the rigidity of the support plate and the flexible plate that supports the exhaust static pressure pipe decreases, and the vibration of the exhaust static pressure pipe increases, and this vibration causes the mounting plate fixed to the exhaust static pressure pipe to attach the support plate and the deflection.
  • a mounting plate (see reference numeral 40 in FIG.
  • the present invention has been made in view of such circumstances, and includes a flexible plate that can increase the natural frequency and suppress the increase in bending moment transmitted to the mounting portion as much as possible.
  • Another object of the present invention is to provide an exhaust static pressure pipe support structure and an internal combustion engine provided with the same.
  • a first aspect of the present invention is an exhaust static pressure pipe that temporarily stores exhaust gas discharged from an internal combustion engine body and supports an exhaust static pressure pipe having a longitudinal axis extending in a horizontal direction with respect to the internal combustion engine body.
  • a support structure comprising a first plate-like body provided between the exhaust static pressure pipe and the internal combustion engine main body and supporting the exhaust static pressure pipe from below, wherein the first plate-like body is in the horizontal direction. Fixed to the exhaust static pressure pipe and attached to the upper end of the first plate-like body, and fixed to the internal combustion engine body. A lower attachment portion attached to a lower end portion of the first plate-like body, and the first plate-like body is connected with the upper attachment portion and the lower attachment portion interposed therebetween.
  • An exhaust static tube support structure composed of a contacting plate-like body.
  • the first support portion supports the weight of the exhaust static pressure tube by supporting the exhaust static pressure tube from below. Further, the first support portion suppresses vibration in the direction orthogonal to the horizontal direction, that is, in the horizontal direction, by the first plate-like body arranged to be orthogonal to the horizontal direction. Further, since the first plate-like body is arranged so as to be orthogonal to the horizontal direction, it can be bent and deformed in the longitudinal direction of the exhaust static pressure pipe. Accordingly, the first support portion is deformed so as to allow expansion and contraction in the longitudinal direction due to heat of the exhaust static pressure tube. According to this aspect, the first plate-like body is added to the pair of opposed plate-like bodies, and the adjacent plate-like body adjacent to the opposed plate-like body is provided.
  • the natural frequency in the lateral direction of the exhaust static pressure tube can be increased by using three or more plate-like bodies in total. Also, rather than increasing the thickness of one or both of the pair of opposing plates, the total thickness is increased by reducing the thickness per plate and increasing the number of plates. It was decided to increase the rigidity of the first support part. Thereby, since the increase in the bending moment transmitted from the edge part of the 1st plate-like body to an upper part attachment part and a lower part attachment part can be suppressed, the increase in the stress which arises in an upper part attachment part and a lower attachment part is suppressed. Thus, it is possible to avoid damage to the fixing portion that fixes the upper mounting portion and the lower mounting portion to the exhaust static pressure pipe or the internal combustion engine body.
  • a scavenging trunk is typically used as the internal combustion engine body to which the lower end of the first support portion is attached.
  • the longitudinal axis of the exhaust static pressure pipe does not need to extend exactly in the horizontal direction, and may be inclined from the horizontal direction within a predetermined range due to assembly accuracy and the like.
  • the opposing plate-like body and the adjacent plate-like body may have the same plate thickness.
  • the plate thicknesses of the opposing plate-like body and the adjacent plate-like body are preferably smaller than the plate thicknesses of the upper mounting portion and the lower mounting portion sandwiched between the opposing plate-like bodies.
  • the exhaust static pressure pipe includes a second plate-like body that is provided between the exhaust static pressure pipe and the internal combustion engine main body and supports the exhaust static pressure pipe from below, and the second plate-like body is You may provide the 2nd support part arrange
  • the second support part supports the weight of the exhaust static pressure pipe by supporting the exhaust static pressure pipe from below. Further, the second support portion suppresses vibration in the horizontal direction, that is, the longitudinal axis direction of the exhaust static pressure pipe, by the second plate-like body disposed along the horizontal direction.
  • a second aspect of the present invention is an internal combustion engine provided with the exhaust static pressure pipe support structure described above.
  • the exhaust static pressure pipe support structure described in the above invention is provided, even if the internal combustion engine has a long stroke and the second support portion becomes long, the lateral vibration of the exhaust static pressure pipe is suppressed.
  • the exhaust static pressure pipe can be supported while avoiding damage to the mounting portion.
  • the natural frequency in the transverse direction perpendicular to the longitudinal direction of the exhaust static pressure tube can be increased, and an increase in bending moment transmitted to the mounting portion can be suppressed as much as possible.
  • FIG. 1 is a schematic configuration diagram illustrating a diesel engine according to an embodiment of the present invention. It is the side view which looked at the diesel engine of Drawing 1 from the exhaust static pressure pipe side.
  • FIG. 3 is an enlarged side view showing the periphery of an exhaust static pressure pipe in FIG. 2. It is the front view which expanded and showed the flexible plate of FIG. It is the side view which expanded and showed the flexible board of the left end of FIG. It is the side view which expanded and showed the flexible board of FIG. It is the side view which showed the deformation
  • FIG. 1 shows an outline of a crosshead type diesel engine (internal combustion engine) 1 according to an embodiment of the present invention.
  • the diesel engine 1 shown in the figure is used as a marine main engine such as an LNG ship or a container ship, and is a low-flow 2-stroke 1-cycle uniflow scavenging system.
  • the diesel engine 1 includes a base plate 3 positioned below, a frame 5 provided on the base plate 3, and a jacket 7 provided on the frame 5.
  • the base plate 3, the frame 5, and the jacket 7 are integrally tightened and fixed by a plurality of tension bolts (not shown) extending in the vertical direction.
  • the jacket 7 is provided with a cylinder liner 9, and a plurality of scavenging ports 10 are formed on the lower end side of the cylinder liner 9.
  • a cylinder cover 11 is provided at the upper end of the cylinder liner 9.
  • the cylinder cover 11 is provided with an exhaust valve 12. In this way, a uniflow scavenging method is adopted in which air is introduced into the cylinder from below as scavenging gas from the scavenging port 10 provided on the lower end side of the cylinder liner 9 and exhaust gas is exhausted from the exhaust valve 12 located above the cylinder. Has been.
  • the exhaust gas discharged from the exhaust valve 12 of each cylinder is collected in the exhaust static pressure pipe 14 and then sent to the supercharger 16.
  • an exhaust turbine (not shown) is rotated by the introduced exhaust gas, and thereby a compressor (not shown) connected coaxially is rotated.
  • the compressor compresses air taken in from the outside, and the compressed air is cooled by the air cooler 18 and then guided to the scavenging trunk 20.
  • the compressed air guided to the scavenging trunk 20 is guided to the scavenging port 10 described above.
  • a piston 13 is provided so as to be able to reciprocate.
  • the upper end of the piston rod 15 is rotatably attached to the lower end of the piston 13.
  • the base plate 3 is a crankcase and is provided with a crankshaft 17.
  • the rotational output extracted from the crankshaft is transmitted to the propulsion propeller for the ship.
  • the lower end of the connecting rod 19 is rotatably connected to the upper end of the crankshaft 17.
  • the frame 5 is provided with a crosshead 21 that rotatably connects the piston rod 15 and the connecting rod 19. That is, the lower end of the piston rod 15 and the upper end of the connecting rod 19 are connected to the cross head 21.
  • the cross head 21 reciprocates in the vertical direction along a pair of sliding plates 23 extending in the vertical direction.
  • the exhaust static pressure pipe 14 has a cylindrical shape with a longitudinal axis extending in the horizontal direction. Note that the longitudinal axis of the exhaust static pressure pipe 14 does not need to extend exactly in the horizontal direction, and may be inclined from the horizontal direction within a predetermined range in relation to assembly accuracy.
  • the longitudinal direction of the exhaust static pressure pipe 14 coincides with the longitudinal direction of the diesel engine 1 (engine longitudinal direction). Note that the longitudinal direction of the exhaust static pressure pipe 14 does not need to be exactly the same as the longitudinal direction of the diesel engine 1 and may be inclined from the longitudinal direction of the diesel engine 1 within a predetermined range in relation to assembly accuracy and the like. .
  • the size of the exhaust static pressure pipe 14 depends on the type of the diesel engine 1 used, the longitudinal dimension is 3 to 20 m and the diameter is 1 to 2 m. Further, when the diesel engine 1 has a large number of cylinders and the cylinders are arranged in series, a plurality of exhaust static pressure pipes 14 may be arranged in the longitudinal direction and the exhaust static pressure pipes may be connected by a flexible connection pipe. .
  • the exhaust static pressure pipe 14 is supported from below with respect to the scavenging trunk 20 on the diesel engine 1 main body side. Specifically, an exhaust static pressure tube support structure having a support plate (second support portion) 30 and a flexible plate (first support portion) 32 is provided between the exhaust static pressure tube 14 and the scavenging trunk 20. ing.
  • the support plate 30 is erected upward from the scavenging trunk 20 and supports the weight of the exhaust static pressure pipe 14 by supporting the exhaust static pressure pipe 14 from below. Since the support plate 30 is provided at the center position in the longitudinal direction, which is the center of gravity of the exhaust static pressure tube 14, it mainly supports the weight of the exhaust static pressure tube 14.
  • the central position in the longitudinal direction of the exhaust static pressure pipe 14 does not mean a central position in a strict sense, but may be a position shifted from the central position within a predetermined range.
  • the support plate 30 is positioned at the center of gravity of the exhaust static pressure tube 14. However, the support plate 30 may be provided at a position away from the center of gravity of the exhaust static pressure tube 14.
  • the support plate 30 is disposed along the longitudinal direction of the exhaust static pressure tube 14 and has a trapezoidal shape with the upper side as the short side.
  • the support plate 30 is made of, for example, an iron-based metal and includes a pair of opposed plates (second plate-like bodies), and the plates are stacked with a predetermined gap therebetween. Has been placed.
  • the upper end of the support plate 30 is rigidly fixed by a plurality of bolts 35, nuts, and the like to the attachment portion 34 fixed to the lower end of the exhaust static pressure pipe 14 by welding or the like.
  • the lower end of the support plate 30 is rigidly fixed by a plurality of bolts, nuts, and the like to the attachment portion 36 fixed to the upper portion of the scavenging trunk 20 by bolts 37 and the like.
  • the support plate 30 is a plate-like body disposed along the longitudinal direction of the exhaust static pressure tube 14 and has high bending rigidity in the longitudinal direction, the vibration of the exhaust static pressure tube 14 in the longitudinal direction is suppressed. Be able to. As described above, the support plate 30 mainly supports the weight of the exhaust static pressure tube 14 and has a function of suppressing vibration in the longitudinal direction of the exhaust static pressure tube 14.
  • the flexible plate 32 is erected upward from the scavenging trunk 20, and a plurality (four in FIG. 3) is provided on the side of the support plate 30, and supports the exhaust static pressure tube 14 from below to exhaust static pressure tube. Supports 14 weights.
  • the number of flexible plates 32 is appropriately determined depending on the longitudinal dimension of the exhaust static pressure tube 14, but is preferably provided at least at both ends of the exhaust static pressure tube 14. This is to effectively suppress vibration around the vertical axis (so-called yaw vibration) at the longitudinal center position of the exhaust static pressure pipe 14.
  • the flexible plate 32 is disposed so as to be orthogonal to the longitudinal direction of the exhaust static pressure pipe 14 and is a plate-like body extending in a direction orthogonal to the longitudinal direction (hereinafter referred to as “exhaust pipe lateral direction”, see FIG. 4). Therefore, it has high bending rigidity in the exhaust pipe lateral direction. For this reason, the flexible plate 32 can suppress the vibration of the exhaust static pressure pipe 14 in the exhaust pipe lateral direction. Further, since the flexible plate 32 is arranged so as to extend in the exhaust pipe lateral direction, it can be bent and deformed in the longitudinal direction of the exhaust static pressure pipe 14 (see, for example, FIG. 7).
  • the flexible plate 32 can be deformed so as to allow expansion and contraction in the longitudinal direction due to heat of the exhaust static pressure tube 14.
  • the flexible plate 32 has a role of supporting the weight of the exhaust static pressure pipe 14 at each position while suppressing thermal deformation in the longitudinal direction of the exhaust static pressure pipe 14 and suppressing vibration in the exhaust pipe lateral direction. Yes.
  • FIG. 4 shows a view of the flexible plate 32 as seen from the front.
  • the upper end of the flexible plate 32 is attached to the exhaust static pressure pipe 14 and protrudes downward with respect to an upper mounting plate (upper mounting portion) 40, and a plurality of bolts 41a and nuts 41b ( (See FIG. 5).
  • the upper end of the flexible plate 32 is fixed in a state where a plurality of plates (first plate-like bodies) 32 a and 32 b constituting the flexible plate 32 are sandwiched from both sides of the upper mounting plate 40. Has been.
  • the lower end of the flexible plate 32 has a lower mounting plate (lower mounting portion) 43 fixed to the upper portion of the scavenging trunk 20 by a bolt 45 (see FIG. 6) or the like. It is fixed by a plurality of bolts 44a (see FIG. 5) and nuts 44b. Specifically, as shown in FIG. 5, the lower end of the flexible plate 32 is fixed in a state where a plurality of plates 32 a and 32 b constituting the flexible plate 32 are sandwiched from both sides of the lower mounting plate 43.
  • the flexible plate 32 is composed of a plurality of plates 32a and 32b made of iron-based metal. Specifically, the flexible plate 32 is overlapped with a pair of opposed plates 32a and 32a arranged so as to sandwich the upper and lower mounting portions 40 and 43, and on the outside of one (left side in FIG. 6) opposed plate 32a. It is comprised from the adjoining plate 32b arrange
  • the total number of plates constituting the flexible plate 32 is three. However, the number of plates may be four or more, and the adjacent plate 32b may be provided so as to overlap the other (right side in FIG. 6) opposing plate 32a.
  • the three plates 32a and 32b have substantially the same shape, and have the same thickness t, the same distance L1 between the upper and lower fixed parts, and the same width b (see FIG. 4).
  • the plate thickness t of the plates 32a and 32b is 5 mm or more, and is 10 mm or more, 14 mm or more, and further 20 mm or more depending on the model.
  • the distance L1 between the fixed parts is 600 mm or more, and is 1000 mm or more, and further 2000 mm or more depending on the model. Further, the distance L1 (L1 / b) between the fixed portions with respect to the width b of the plates 32a and 32b is larger than 1, and depending on the model, it is a vertically long shape that is 1.5 or more, further 2.0 or more. Yes.
  • each plate does not need to be exactly the same shape, and the shape of each plate may be appropriately changed as long as it has a function as a flexible plate composed of each plate.
  • the plate thickness t may be different for each plate.
  • the plate thickness t of each plate is preferably thinner than the plate thickness T of the upper and lower mounting plates 40, 43, and the total plate thickness obtained by integrating the plate thickness t of each plate is obtained by the flexible plate 32. Determined from design strength.
  • the flexible plate 32 of this embodiment is not composed of a pair of two plates, but is composed of three plates 32a and 32b. This advantage will be described below.
  • the bending moment M of the flexible plate 32 due to the thermal elongation of the exhaust static pressure pipe 14 is expressed by the following equation.
  • M 6 ⁇ E ⁇ n ⁇ I1 ⁇ ⁇ max / L1 ⁇ 2 [Kgf-mm] (1)
  • E Longitudinal elastic modulus (21000 kgf / mm 2 )
  • n Number of plates constituting the flexible plate
  • I1 Second moment of section of the center line in the transverse direction of the plate
  • b Plate width (mm)
  • t Plate thickness (mm)
  • L1 Length between fixed parts of plate (mm) ⁇ max: thermal elongation (mm)
  • the cross-sectional secondary moment I1 is expressed by the following equation.
  • I1 b ⁇ t ⁇ 3/12 [mm 4 ]
  • M E ⁇ n ⁇ b ⁇ t ⁇ 3 ⁇ ⁇ max / (2 ⁇ L1 ⁇ 2) [Kgf-mm] (2)
  • the thermal elongation amount ⁇ max, the plate fixing portion length L1 and the plate width b are determined by the design on the diesel engine 1 main body side, they are considered as constants. Therefore, if E, b, ⁇ max, and L1 are constants, the equation (2) can be transformed as the following equation. M ⁇ n ⁇ t ⁇ 3 (3) From the above equation, it can be seen that the bending moment M at the fixed portion of the flexible plate 32 caused by the thermal expansion of the exhaust static pressure tube 14 is proportional to the number n of plates and proportional to the cube of the plate thickness t.
  • the natural frequency f EC in the exhaust pipe lateral direction of the exhaust static pressure pipe 14 and the flexible plate 32 supporting the exhaust static pressure pipe 14 will be examined.
  • the natural frequency f EC is expressed by the following equation.
  • f EC (k1 / m) ⁇ 0.5 / (2 ⁇ ⁇ ) [Hz] (7)
  • each item in the above equation is as follows.
  • k1 Spring constant in the lateral direction of the exhaust pipe
  • I2 Cross-sectional secondary moment of the longitudinal center line of the plate
  • m Mass of the exhaust static pressure pipe 14
  • k1 3 ⁇ E ⁇ n ⁇ I2 / L1 ⁇ 3
  • I2 t ⁇ b ⁇ 3/12 [mm 4 ] If these are substituted into the above equation (7), the following equation is obtained.
  • the stress ⁇ generated in the mounting plates 40 and 43 changes accordingly.
  • the stress ⁇ (bending moment M) is at least constant before and after the change in the number n of plates and the thickness t.
  • the natural frequency f of the flexible plate 32 in the exhaust pipe lateral direction f. EC is represented by the following equation from equation (9).
  • f EC ⁇ n ⁇ (1/3) (11) As can be seen from the above equation, when the plate thickness t of each plate is determined so that the bending moment M does not change before and after the change in the number n of plates and the plate thickness t, the flexure plate 32 increases as the number n of plates increases.
  • the natural frequency f EC in the lateral direction increases in proportion to the 1/3 power of the number of plates.
  • the following operational effects are obtained.
  • exhaust gas is guided from the plurality of cylinders to the exhaust static pressure pipe 14 at various timings.
  • the pulsation of the exhaust gas is suppressed, and the energy of the exhaust gas is converted into a static pressure.
  • vibrations transmitted from the main body of the diesel engine 1, the influence of exhaust gas pressure, the self-weight of the exhaust static pressure pipe 14, and the like are applied to the exhaust static pressure pipe 14.
  • the main weight of the exhaust static pressure pipe 14 is supported by a support plate 30 provided at a substantially central position in the longitudinal direction. Vibration in the longitudinal direction of the exhaust static pressure pipe 14 is suppressed by the support plate 30 extending in the longitudinal direction.
  • the partial load at each longitudinal position of the exhaust static pressure pipe 14 is supported by the flexible plate 32.
  • the vibration in the lateral direction of the exhaust static pressure tube 14 is suppressed by the flexible plate 32 extending in the lateral direction of the exhaust static pressure tube 14.
  • the thermal elongation in the longitudinal direction of the exhaust static pressure tube 14 is allowed by the deformation of the flexible plate 32 in the longitudinal direction of the exhaust static pressure tube 14 as shown in FIG.
  • the flexible plate 32 is added to the pair of opposing plates 32a, and the adjacent plate 32b having the same thickness as the opposing plates 32a is provided adjacent to the opposing plate 32a.
  • the natural frequency in the lateral direction can be increased by using three plates in total.
  • the total plate thickness is increased by increasing the number of plates, thereby increasing the rigidity of the flexible plate 32. Even if the rigidity of the flexible plate 32 is increased in this way, a thin plate obtained by dividing the rigid plate 32 is combined instead of a single thick plate, so that the upper mounting portion 40 and the lower side of the flexible plate 32 are fixed to each other.
  • An increase in bending moment transmitted to the mounting portion 43 can be suppressed, and a fixing portion that is fixed to the exhaust static pressure pipe 14 or the scavenging trunk 20 by suppressing an increase in stress generated in the upper mounting portion 40 and the lower mounting portion 43. Damage can be avoided.
  • a large diesel engine used as a marine main engine is used.
  • the present invention is not limited to this, and can be applied to other internal combustion engines as long as they have an exhaust static pressure pipe.
  • the connection destination of the lower end of the flexible plate is described as the scavenging trunk.
  • the present invention is not limited to this, and the internal combustion engine main body side suitable for connecting the lower end of the flexible plate is used. If it is the structure of.
  • the configuration including the support plate 30 has been described.
  • the exhaust static pressure tube 14 may be supported only by the flexible plate 32 without using the support plate 30.

Abstract

The present invention provides an exhaust static tube support structure such that the natural frequency can be increased and such that a bending moment transmitted to an attachment part can be suppressed from increasing as much as possible. This exhaust static tube support structure is equipped with: a flexible plate (32) that is disposed between an exhaust static tube (14) and a scavenging trunk (20) and has plates (32a, 32b) for supporting the exhaust static tube (14) from below, said plates (32a, 32b) being arranged orthogonal to the longitudinal direction of the exhaust static tube (14); an upper mounting plate (40) that is fixed to the exhaust static tube (14) and is connected to the top end of the flexible plate (32); and a lower mounting plate (43) that is fixed to the scavenging trunk (20) and is connected to the bottom end of the flexible plate (32). The flexible plate (32) comprises: one pair of facing plates (32a) that are connected together with the upper mounting plate (40) and lower mounting plate (43) being sandwiched therebetween; and an adjoining plate (32b) that is disposed adjacent to one of the facing plates (32a).

Description

排気静圧管支持構造およびこれを備えた内燃機関Exhaust static pressure pipe support structure and internal combustion engine provided with the same
　本発明は、例えば静圧式とされた過給機に排ガスを導く排気静圧管を支持する排気静圧管支持構造およびこれを備えた内燃機関に関するものである。 The present invention relates to an exhaust static pressure pipe support structure that supports an exhaust static pressure pipe that guides exhaust gas to a turbocharger that is, for example, a static pressure type, and an internal combustion engine including the exhaust static pressure pipe support structure.
　舶用主機として用いられる大型２ストロークディーゼルエンジン（内燃機関）には、静圧式の過給機が用いられる。この静圧式の過給機には、過給機に導入する前の排ガスを一時的に貯留する排気静圧管が接続されている。排気静圧管は、ディーゼルエンジンの各シリンダから排出された排ガスの脈動を抑えるために所定容量の空間を有した容器となっている。なお、排気静圧管は、排ガスレシーバや排ガスマニホールドとも称される。
　このような排気静圧管は、それ自身の重量と各シリンダ側から発生するガス圧による荷重を受けるため、ディーゼルエンジン本体に対して支持板およびたわみ板によって支持されている（下記特許文献１参照）。 A static pressure supercharger is used for a large two-stroke diesel engine (internal combustion engine) used as a marine main engine. The static pressure supercharger is connected to an exhaust static pressure pipe that temporarily stores the exhaust gas before being introduced into the supercharger. The exhaust static pressure pipe is a container having a predetermined capacity in order to suppress pulsation of exhaust gas discharged from each cylinder of the diesel engine. The exhaust static pressure pipe is also referred to as an exhaust gas receiver or an exhaust gas manifold.
Since such an exhaust static pressure pipe receives a load due to its own weight and gas pressure generated from each cylinder side, the exhaust static pressure pipe is supported by a support plate and a flexible plate with respect to the diesel engine body (see Patent Document 1 below). .
特許第４９９５９９０号公報Japanese Patent No. 499990
　支持板は、排気静圧管を下方から支持することによって排気静圧管の重量を主として支えるものである。さらに、支持板は、排気静圧管の長手方向に沿って配置されており長手方向の剛性を有しているので、排気静圧管の長手方向の振動を抑えることができるようになっている。 The support plate mainly supports the weight of the exhaust static pressure tube by supporting the exhaust static pressure tube from below. Furthermore, since the support plate is disposed along the longitudinal direction of the exhaust static pressure pipe and has rigidity in the longitudinal direction, vibration in the longitudinal direction of the exhaust static pressure pipe can be suppressed.
　たわみ板は、支持板の両側方に、排気静圧管の長手方向に所定の間隔を有して複数設けられている。例えば参考例として模式的に図８に示すように、たわみ板５０は、排気静圧管１４と掃気トランク２０との間に設けられ、排気静圧管１４を下方から支持することによって排気静圧管１４の重量およびガス圧による荷重を支えている。さらに、たわみ板５０は、排気静圧管１４の長手方向に直交する横方向（図８の紙面垂直方向）に配置された１対のプレート５０ａによって構成されているので、排気静圧管１４の横方向の振動を抑えることができるようになっている。また、たわみ板５０は排気静圧管１４の横方向に配置されているため、図８にその変形状態が示されているように、排気静圧管１４の長手方向に撓んで変形することができるようになっている。これにより、たわみ板５０は、排気静圧管１４の熱による長手方向の伸縮を許容できるようになっている。 A plurality of flexible plates are provided on both sides of the support plate with a predetermined interval in the longitudinal direction of the exhaust static pressure tube. For example, as schematically shown in FIG. 8 as a reference example, the flexible plate 50 is provided between the exhaust static pressure tube 14 and the scavenging trunk 20 and supports the exhaust static pressure tube 14 from below to Supports load due to weight and gas pressure. Further, since the flexible plate 50 is constituted by a pair of plates 50a arranged in a lateral direction (perpendicular to the paper surface in FIG. 8) perpendicular to the longitudinal direction of the exhaust static pressure pipe 14, the lateral direction of the exhaust static pressure pipe 14 The vibration of the can be suppressed. Further, since the flexible plate 50 is disposed in the lateral direction of the exhaust static pressure tube 14, it can be deformed by being bent in the longitudinal direction of the exhaust static pressure tube 14 as shown in FIG. It has become. As a result, the flexible plate 50 can allow expansion and contraction in the longitudinal direction due to heat of the exhaust static pressure tube 14.
　近年のディーゼルエンジンのロングストローク化に伴い、ディーゼルエンジンのシリンダ部分の寸法が長くなることに伴い、排気静圧管と、排気静圧管を下方から支えるディーゼルエンジン本体（例えば掃気トランク）の固定位置との距離が長くなる傾向にある。このため、排気静圧管を下から支える支持板およびたわみ板の上下方向の長さが長くなる。これにより、排気静圧管を支える支持板およびたわみ板の剛性が低下し、排気静圧管の振動が大きくなり、この振動により、支持板を取り付けるために排気静圧管に固定された取付板や、たわみ板を取り付けるために排気静圧管に固定された取付板（図８の符号４０参照）、並びに、支持板を取り付けるためにディーゼルエンジン本体に固定された取付板や、たわみ板を取り付けるためにディーゼルエンジン本体に固定された取付板（図８の符号４３参照）、そしてこれらに付属する配管に損傷を及ぼすおそれがある。
　このような排気静圧管に生じる振動を小さくするため、支持板およびたわみ板の板厚を増大して剛性を上げ、固有振動数を上げることが一般的な対策として挙げられる。 Along with the long stroke of the diesel engine in recent years, as the size of the cylinder part of the diesel engine becomes longer, the exhaust static pressure pipe and the fixed position of the diesel engine main body (for example, the scavenging trunk) that supports the exhaust static pressure pipe from below are The distance tends to be longer. For this reason, the length of the up-down direction of the support plate and flexible plate which support an exhaust static pressure pipe from the bottom becomes long. As a result, the rigidity of the support plate and the flexible plate that supports the exhaust static pressure pipe decreases, and the vibration of the exhaust static pressure pipe increases, and this vibration causes the mounting plate fixed to the exhaust static pressure pipe to attach the support plate and the deflection. A mounting plate (see reference numeral 40 in FIG. 8) fixed to the exhaust static pressure pipe for mounting the plate, a mounting plate fixed to the diesel engine body for mounting the support plate, and a diesel engine for mounting the flexible plate There is a risk of damaging the mounting plates (see reference numeral 43 in FIG. 8) fixed to the main body and the pipes attached to them.
In order to reduce the vibration generated in the exhaust static pressure pipe, a general measure is to increase the thickness of the support plate and the flexible plate to increase the rigidity and increase the natural frequency.
　しかし、たわみ板の場合、固有振動数を上げるために板厚を増大すると、高温となった排気静圧管の長手方向の熱伸び変位により、大きな曲げモーメントが発生してしまう。この曲げモーメントは、たわみ板に接続された取付板にも伝達され、比較的強度の低い排気静圧管やディーゼルエンジン本体に対する取付板の固定部に大きな応力が発生し、損傷を及ぼすおそれがある。 However, in the case of a flexible plate, if the plate thickness is increased in order to increase the natural frequency, a large bending moment will be generated due to the thermal expansion displacement in the longitudinal direction of the exhaust static pressure tube that has become hot. This bending moment is transmitted also to the mounting plate connected to the flexible plate, and a large stress is generated in the fixing portion of the mounting plate with respect to the exhaust static pressure pipe having a relatively low strength or the diesel engine body, which may cause damage.
　本発明は、このような事情に鑑みてなされたものであって、固有振動数を上げることができかつ取付部に伝達される曲げモーメントの増大を可及的に抑えることができるたわみ板を備えた排気静圧管支持構造およびこれを備えた内燃機関を提供することを目的とする。 The present invention has been made in view of such circumstances, and includes a flexible plate that can increase the natural frequency and suppress the increase in bending moment transmitted to the mounting portion as much as possible. Another object of the present invention is to provide an exhaust static pressure pipe support structure and an internal combustion engine provided with the same.
　本発明の第１態様は、内燃機関本体から排出される排ガスを一時的に貯留するとともに、長手軸線が水平方向に延在する排気静圧管を、前記内燃機関本体に対して支持する排気静圧管支持構造であって、前記排気静圧管と前記内燃機関本体との間に設けられ、該排気静圧管を下方から支持する第１板状体を有し、該第１板状体が前記水平方向に直交するように配置された第１支持部と、前記排気静圧管に対して固定され、前記第１板状体の上端部に取り付けられる上側取付部と、前記内燃機関本体に対して固定され、前記第１板状体の下端部に取り付けられる下側取付部とを備え、前記第１板状体は、前記上側取付部および前記下側取付部を間に挟んで接続された１対の対向板状体と、少なくとも一方の該対向板状体に隣接して設けられた隣接板状体とから構成される排気静圧管支持構造である。 A first aspect of the present invention is an exhaust static pressure pipe that temporarily stores exhaust gas discharged from an internal combustion engine body and supports an exhaust static pressure pipe having a longitudinal axis extending in a horizontal direction with respect to the internal combustion engine body. A support structure, comprising a first plate-like body provided between the exhaust static pressure pipe and the internal combustion engine main body and supporting the exhaust static pressure pipe from below, wherein the first plate-like body is in the horizontal direction. Fixed to the exhaust static pressure pipe and attached to the upper end of the first plate-like body, and fixed to the internal combustion engine body. A lower attachment portion attached to a lower end portion of the first plate-like body, and the first plate-like body is connected with the upper attachment portion and the lower attachment portion interposed therebetween. Provided adjacent to at least one counter plate and at least one counter plate An exhaust static tube support structure composed of a contacting plate-like body.
　本態様によれば、第１支持部は、排気静圧管を下方から支持することによって排気静圧管の重量を支える。さらに、第１支持部は、水平方向に直交するように配置された第１板状体によって、水平方向に直交する方向すなわち横方向の振動を抑える。また、第１板状体は水平方向に直交するように配置されているため、排気静圧管の長手方向に撓んで変形することができるようになっている。これにより、第１支持部は、排気静圧管の熱による長手方向の伸縮を許容するように変形する。
　本態様によれば、第１板状体を一対の対向板状体に加えて、対向板状体に隣接する隣接板状体を設けることとした。このように板状体を合計で３枚以上とすることによって排気静圧管の横方向の固有振動数を上げることができる。また、１対の対向板状体の一方あるいは両方の板厚を増大するのではなく、１枚あたりの板厚を減じて板状体の枚数を増やすことによって全体の合計板厚を増大して第１支持部の剛性を上げることにした。これにより、第１板状体の端部から上側取付部および下側取付部に伝達される曲げモーメントの増加を抑えることができるので、上側取付部および下側取付部に生じる応力の増大を抑えることで、上側取付部および下側取付部を排気静圧管や内燃機関本体に固定する固定部の損傷を回避することができる。
　第１支持部の下端が取り付けられる内燃機関本体としては、典型的には、掃気トランクが挙げられる。
　排気静圧管の長手軸線は、水平方向に厳密に一致して延在している必要は無く、組立精度等の関係で所定の範囲で水平方向から傾いていても良い。 According to this aspect, the first support portion supports the weight of the exhaust static pressure tube by supporting the exhaust static pressure tube from below. Further, the first support portion suppresses vibration in the direction orthogonal to the horizontal direction, that is, in the horizontal direction, by the first plate-like body arranged to be orthogonal to the horizontal direction. Further, since the first plate-like body is arranged so as to be orthogonal to the horizontal direction, it can be bent and deformed in the longitudinal direction of the exhaust static pressure pipe. Accordingly, the first support portion is deformed so as to allow expansion and contraction in the longitudinal direction due to heat of the exhaust static pressure tube.
According to this aspect, the first plate-like body is added to the pair of opposed plate-like bodies, and the adjacent plate-like body adjacent to the opposed plate-like body is provided. Thus, the natural frequency in the lateral direction of the exhaust static pressure tube can be increased by using three or more plate-like bodies in total. Also, rather than increasing the thickness of one or both of the pair of opposing plates, the total thickness is increased by reducing the thickness per plate and increasing the number of plates. It was decided to increase the rigidity of the first support part. Thereby, since the increase in the bending moment transmitted from the edge part of the 1st plate-like body to an upper part attachment part and a lower part attachment part can be suppressed, the increase in the stress which arises in an upper part attachment part and a lower attachment part is suppressed. Thus, it is possible to avoid damage to the fixing portion that fixes the upper mounting portion and the lower mounting portion to the exhaust static pressure pipe or the internal combustion engine body.
A scavenging trunk is typically used as the internal combustion engine body to which the lower end of the first support portion is attached.
The longitudinal axis of the exhaust static pressure pipe does not need to extend exactly in the horizontal direction, and may be inclined from the horizontal direction within a predetermined range due to assembly accuracy and the like.
　上記排気静圧管支持構造では、前記対向板状体と前記隣接板状体とは、同じ板厚とされていてもよい。 In the exhaust static pressure pipe support structure, the opposing plate-like body and the adjacent plate-like body may have the same plate thickness.
　対向板状体と隣接板状体とを同じ板厚とすることにより、格別なコスト増大を招くことなく製造することができる。また、対向板状体および隣接板状体のそれぞれの板厚は、対向板状体に挟み込まれた上側取付部や下側取付部の板厚よりも小さいことが好ましい。 By making the opposing plate-like body and the adjacent plate-like body have the same plate thickness, it can be manufactured without causing a significant increase in cost. The plate thicknesses of the opposing plate-like body and the adjacent plate-like body are preferably smaller than the plate thicknesses of the upper mounting portion and the lower mounting portion sandwiched between the opposing plate-like bodies.
　上記排気静圧管支持構造では、前記排気静圧管と前記内燃機関本体との間に設けられ、該排気静圧管を下方から支持する第２板状体を有し、該第２板状体が前記水平方向に沿って配置された第２支持部を備えていてもよい。 In the exhaust static pressure pipe support structure, the exhaust static pressure pipe includes a second plate-like body that is provided between the exhaust static pressure pipe and the internal combustion engine main body and supports the exhaust static pressure pipe from below, and the second plate-like body is You may provide the 2nd support part arrange | positioned along a horizontal direction.
　第２支持部は、排気静圧管を下方から支持することによって排気静圧管の重量を支える。さらに、第２支持部は、水平方向に沿って配置された第２板状体によって、水平方向すなわち排気静圧管の長手軸線方向の振動を抑える。 The second support part supports the weight of the exhaust static pressure pipe by supporting the exhaust static pressure pipe from below. Further, the second support portion suppresses vibration in the horizontal direction, that is, the longitudinal axis direction of the exhaust static pressure pipe, by the second plate-like body disposed along the horizontal direction.
　本発明の第２態様は、上記の排気静圧管支持構造を備えている内燃機関である。 A second aspect of the present invention is an internal combustion engine provided with the exhaust static pressure pipe support structure described above.
　本態様によれば、上記発明に記載された排気静圧管支持構造を備えているので、内燃機関をロングストローク化して第２支持部が長くなっても、排気静圧管の横方向の振動を抑えつつ取付部の損傷を回避して排気静圧管を支持することができる。 According to this aspect, since the exhaust static pressure pipe support structure described in the above invention is provided, even if the internal combustion engine has a long stroke and the second support portion becomes long, the lateral vibration of the exhaust static pressure pipe is suppressed. However, the exhaust static pressure pipe can be supported while avoiding damage to the mounting portion.
　排気静圧管の長手方向に直交する横方向の固有振動数を上げることができるとともに、取付部に伝達される曲げモーメントの増大を可及的に抑えることができる。 The natural frequency in the transverse direction perpendicular to the longitudinal direction of the exhaust static pressure tube can be increased, and an increase in bending moment transmitted to the mounting portion can be suppressed as much as possible.
本発明の一実施形態にかかるディーゼルエンジンを示した概略構成図である。1 is a schematic configuration diagram illustrating a diesel engine according to an embodiment of the present invention. 図１のディーゼルエンジンを排気静圧管側から見た側面図である。It is the side view which looked at the diesel engine of Drawing 1 from the exhaust static pressure pipe side. 図２の排気静圧管周りを拡大して示した側面図である。FIG. 3 is an enlarged side view showing the periphery of an exhaust static pressure pipe in FIG. 2. 図３のたわみ板を拡大して示した正面図である。It is the front view which expanded and showed the flexible plate of FIG. 図３の左端のたわみ板を拡大して示した側面図である。It is the side view which expanded and showed the flexible board of the left end of FIG. 図５のたわみ板をさらに拡大して示した側面図である。It is the side view which expanded and showed the flexible board of FIG. 本発明の一実施形態にかかるたわみ板の変形状態を示した側面図である。It is the side view which showed the deformation | transformation state of the flexible board concerning one Embodiment of this invention. 参考例としてのたわみ板の変形状態を示した側面図である。It is the side view which showed the deformation | transformation state of the flexible board as a reference example.
　以下に、本発明の実施形態について、図面を参照して説明する。
　図１には、本発明の実施形態にかかるクロスヘッド型ディーゼルエンジン（内燃機関）１の概略が示されている。同図に示されたディーゼルエンジン１は、例えばＬＮＧ船やコンテナ船等の舶用主機として用いられ、低速２ストローク１サイクルのユニフロー掃気方式とされている。 Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 shows an outline of a crosshead type diesel engine (internal combustion engine) 1 according to an embodiment of the present invention. The diesel engine 1 shown in the figure is used as a marine main engine such as an LNG ship or a container ship, and is a low-flow 2-stroke 1-cycle uniflow scavenging system.
　ディーゼルエンジン１は、下方に位置する台板３と、台板３上に設けられた架構５と、架構５上に設けられたジャケット７とを備えている。これら台板３、架構５及びジャケット７は、上下方向に延在する複数のテンションボルト（図示せず）によって一体的に締め付けられて固定されている。 The diesel engine 1 includes a base plate 3 positioned below, a frame 5 provided on the base plate 3, and a jacket 7 provided on the frame 5. The base plate 3, the frame 5, and the jacket 7 are integrally tightened and fixed by a plurality of tension bolts (not shown) extending in the vertical direction.
　ジャケット７にはシリンダライナ９が設けられており、シリンダライナ９の下端側には複数の掃気ポート１０が形成されている。シリンダライナ９の上端には、シリンダカバー１１が設けられている。シリンダカバー１１には、排気弁１２が設けられている。このように、シリンダライナ９の下端側に設けた掃気ポート１０から空気が掃気として下方からシリンダ内に導入され、シリンダ内の上方に位置する排気弁１２から排ガスが排気されるユニフロー掃気方式が採用されている。 The jacket 7 is provided with a cylinder liner 9, and a plurality of scavenging ports 10 are formed on the lower end side of the cylinder liner 9. A cylinder cover 11 is provided at the upper end of the cylinder liner 9. The cylinder cover 11 is provided with an exhaust valve 12. In this way, a uniflow scavenging method is adopted in which air is introduced into the cylinder from below as scavenging gas from the scavenging port 10 provided on the lower end side of the cylinder liner 9 and exhaust gas is exhausted from the exhaust valve 12 located above the cylinder. Has been.
　各気筒の排気弁１２から排出された排ガスは、排気静圧管１４に集められた後に、過給機１６へと送られる。過給機１６では、導かれた排ガスによって図示しない排気タービンが回転させられ、これにより同軸にて接続された図示しないコンプレッサが回転させられる。コンプレッサは、外部から取り込んだ空気を圧縮し、圧縮された空気はエアクーラ１８にて冷却された後に掃気トランク２０へと導かれる。掃気トランク２０へと導かれた圧縮空気は、上述した掃気ポート１０へと導かれる。 The exhaust gas discharged from the exhaust valve 12 of each cylinder is collected in the exhaust static pressure pipe 14 and then sent to the supercharger 16. In the supercharger 16, an exhaust turbine (not shown) is rotated by the introduced exhaust gas, and thereby a compressor (not shown) connected coaxially is rotated. The compressor compresses air taken in from the outside, and the compressed air is cooled by the air cooler 18 and then guided to the scavenging trunk 20. The compressed air guided to the scavenging trunk 20 is guided to the scavenging port 10 described above.
　シリンダライナ９およびシリンダカバー１１によって形成された空間内には、ピストン１３が往復動可能に設けられている。ピストン１３の下端には、ピストン棒１５の上端が回動可能に取り付けられている。 In the space formed by the cylinder liner 9 and the cylinder cover 11, a piston 13 is provided so as to be able to reciprocate. The upper end of the piston rod 15 is rotatably attached to the lower end of the piston 13.
　台板３はクランクケースとされており、クランク軸１７が設けられている。クランク軸から取り出された回転出力が船舶の推進用プロペラへと伝達されるようになっている。クランク軸１７の上端には、連接棒１９の下端が回動可能に接続されている。 The base plate 3 is a crankcase and is provided with a crankshaft 17. The rotational output extracted from the crankshaft is transmitted to the propulsion propeller for the ship. The lower end of the connecting rod 19 is rotatably connected to the upper end of the crankshaft 17.
　架構５には、ピストン棒１５と連接棒１９とを回動可能に接続するクロスヘッド２１が設けられている。すなわち、ピストン棒１５の下端および連接棒１９の上端がクロスヘッド２１に接続されている。クロスヘッド２１は、上下方向に延在する一対の摺動板２３に沿って上下方向に往復動するようになっている。 The frame 5 is provided with a crosshead 21 that rotatably connects the piston rod 15 and the connecting rod 19. That is, the lower end of the piston rod 15 and the upper end of the connecting rod 19 are connected to the cross head 21. The cross head 21 reciprocates in the vertical direction along a pair of sliding plates 23 extending in the vertical direction.
　排気静圧管１４は、図１及び図２に示されているように、長手軸線を水平方向に延在させた円筒形状とされている。なお、排気静圧管１４の長手軸線は、水平方向に厳密に一致して延在している必要は無く、組立精度等の関係で所定の範囲で水平方向から傾いていても良い。
　排気静圧管１４の長手方向（図３参照）は、ディーゼルエンジン１の長手方向（機関長手方向）に一致している。なお、排気静圧管１４の長手方向は、ディーゼルエンジン１の長手方向に厳密に一致している必要は無く、組立精度等の関係で所定の範囲でディーゼルエンジン１の長手方向から傾いていても良い。
　排気静圧管１４の大きさは、使用されるディーゼルエンジン１の機種にもよるが、長手方向の寸法は３～２０ｍとなり、直径は１～２ｍとなる。また、ディーゼルエンジン１のシリンダ数が多くシリンダが直列に配列される場合は、排気静圧管１４を長手方向に複数並べて排気静圧管の間を、可撓性を有する接続管で接続する場合もある。 As shown in FIG. 1 and FIG. 2, the exhaust static pressure pipe 14 has a cylindrical shape with a longitudinal axis extending in the horizontal direction. Note that the longitudinal axis of the exhaust static pressure pipe 14 does not need to extend exactly in the horizontal direction, and may be inclined from the horizontal direction within a predetermined range in relation to assembly accuracy.
The longitudinal direction of the exhaust static pressure pipe 14 (see FIG. 3) coincides with the longitudinal direction of the diesel engine 1 (engine longitudinal direction). Note that the longitudinal direction of the exhaust static pressure pipe 14 does not need to be exactly the same as the longitudinal direction of the diesel engine 1 and may be inclined from the longitudinal direction of the diesel engine 1 within a predetermined range in relation to assembly accuracy and the like. .
Although the size of the exhaust static pressure pipe 14 depends on the type of the diesel engine 1 used, the longitudinal dimension is 3 to 20 m and the diameter is 1 to 2 m. Further, when the diesel engine 1 has a large number of cylinders and the cylinders are arranged in series, a plurality of exhaust static pressure pipes 14 may be arranged in the longitudinal direction and the exhaust static pressure pipes may be connected by a flexible connection pipe. .
　排気静圧管１４は、ディーゼルエンジン１本体側の掃気トランク２０に対して下方から支持されている。具体的には、排気静圧管１４と掃気トランク２０との間には、支持板（第２支持部）３０と、たわみ板（第１支持部）３２とを有する排気静圧管支持構造が設けられている。 The exhaust static pressure pipe 14 is supported from below with respect to the scavenging trunk 20 on the diesel engine 1 main body side. Specifically, an exhaust static pressure tube support structure having a support plate (second support portion) 30 and a flexible plate (first support portion) 32 is provided between the exhaust static pressure tube 14 and the scavenging trunk 20. ing.
　図３に示されているように、支持板３０は、掃気トランク２０から上方向に立設され、排気静圧管１４を下方から支持することによって排気静圧管１４の重量を支えるものである。支持板３０は、排気静圧管１４の重心位置である長手方向における中央位置に設けられているので、排気静圧管１４の重量を主として支える。ここで、排気静圧管１４の長手方向における中央位置とは、厳密な意味での中央位置を意味するものではなく、所定の範囲で中央位置からずれた位置でも良い。また、本実施形態では排気静圧管１４の重心位置に支持板３０が位置しているが、排気静圧管１４の重心から外れた位置に支持板３０を設けてもよい。 As shown in FIG. 3, the support plate 30 is erected upward from the scavenging trunk 20 and supports the weight of the exhaust static pressure pipe 14 by supporting the exhaust static pressure pipe 14 from below. Since the support plate 30 is provided at the center position in the longitudinal direction, which is the center of gravity of the exhaust static pressure tube 14, it mainly supports the weight of the exhaust static pressure tube 14. Here, the central position in the longitudinal direction of the exhaust static pressure pipe 14 does not mean a central position in a strict sense, but may be a position shifted from the central position within a predetermined range. In the present embodiment, the support plate 30 is positioned at the center of gravity of the exhaust static pressure tube 14. However, the support plate 30 may be provided at a position away from the center of gravity of the exhaust static pressure tube 14.
　支持板３０は、排気静圧管１４の長手方向に沿って配置され、上辺を短辺とした台形状とされている。支持板３０は、例えば鉄系の金属製とされ、対向する１対のプレート（第２板状体）から構成されており、各プレートは間に所定の隙間を有して重ねられた状態で配置されている。
　支持板３０の上端は、排気静圧管１４の下端に溶接等によって固定された取付部３４に対して、複数のボルト３５及びナット等によって剛に固定されている。支持板３０の下端は、掃気トランク２０の上部にボルト３７等によって固定された取付部３６に対して、複数のボルト及びナット等によって剛に固定されている。支持板３０は、排気静圧管１４の長手方向に沿って配置された板状体とされているため長手方向に高い曲げ剛性を有しているので、排気静圧管１４の長手方向の振動を抑えることができるようになっている。
　このように、支持板３０は、排気静圧管１４の重量を主として支えるとともに、排気静圧管１４の長手方向の振動を抑える役割を有している。 The support plate 30 is disposed along the longitudinal direction of the exhaust static pressure tube 14 and has a trapezoidal shape with the upper side as the short side. The support plate 30 is made of, for example, an iron-based metal and includes a pair of opposed plates (second plate-like bodies), and the plates are stacked with a predetermined gap therebetween. Has been placed.
The upper end of the support plate 30 is rigidly fixed by a plurality of bolts 35, nuts, and the like to the attachment portion 34 fixed to the lower end of the exhaust static pressure pipe 14 by welding or the like. The lower end of the support plate 30 is rigidly fixed by a plurality of bolts, nuts, and the like to the attachment portion 36 fixed to the upper portion of the scavenging trunk 20 by bolts 37 and the like. Since the support plate 30 is a plate-like body disposed along the longitudinal direction of the exhaust static pressure tube 14 and has high bending rigidity in the longitudinal direction, the vibration of the exhaust static pressure tube 14 in the longitudinal direction is suppressed. Be able to.
As described above, the support plate 30 mainly supports the weight of the exhaust static pressure tube 14 and has a function of suppressing vibration in the longitudinal direction of the exhaust static pressure tube 14.
　たわみ板３２は、掃気トランク２０から上方向に立設され、支持板３０の側方に複数（図３では４つ）設けられており、排気静圧管１４を下方から支持することによって排気静圧管１４の重量を支える。たわみ板３２の数は、排気静圧管１４の長手方向の寸法によって適宜決定されるが、少なくとも排気静圧管１４の両端に設けることが好ましい。これは、排気静圧管１４の長手方向の中央位置における鉛直軸線回りの振動（いわゆるヨー方向の振動）を有効に抑えるためである。 The flexible plate 32 is erected upward from the scavenging trunk 20, and a plurality (four in FIG. 3) is provided on the side of the support plate 30, and supports the exhaust static pressure tube 14 from below to exhaust static pressure tube. Supports 14 weights. The number of flexible plates 32 is appropriately determined depending on the longitudinal dimension of the exhaust static pressure tube 14, but is preferably provided at least at both ends of the exhaust static pressure tube 14. This is to effectively suppress vibration around the vertical axis (so-called yaw vibration) at the longitudinal center position of the exhaust static pressure pipe 14.
　たわみ板３２は、排気静圧管１４の長手方向に直交するように配置され、この長手方向に直交する方向（以下「排気管横方向」という。図４参照）に延在した板状体とされているため排気管横方向に高い曲げ剛性を有している。このため、たわみ板３２は、排気静圧管１４の排気管横方向の振動を抑えることができるようになっている。また、たわみ板３２は、排気管横方向に延在するように配置されているため、排気静圧管１４の長手方向に撓んで変形できるようになっている（例えば図７参照）。これにより、たわみ板３２は、排気静圧管１４の熱による長手方向の伸縮を許容するように変形することができる。
　このように、たわみ板３２は、排気静圧管１４の長手方向の熱変形を許容しつつ、排気静圧管１４の重量を各位置で支えるとともに、排気管横方向の振動を抑える役割を有している。 The flexible plate 32 is disposed so as to be orthogonal to the longitudinal direction of the exhaust static pressure pipe 14 and is a plate-like body extending in a direction orthogonal to the longitudinal direction (hereinafter referred to as “exhaust pipe lateral direction”, see FIG. 4). Therefore, it has high bending rigidity in the exhaust pipe lateral direction. For this reason, the flexible plate 32 can suppress the vibration of the exhaust static pressure pipe 14 in the exhaust pipe lateral direction. Further, since the flexible plate 32 is arranged so as to extend in the exhaust pipe lateral direction, it can be bent and deformed in the longitudinal direction of the exhaust static pressure pipe 14 (see, for example, FIG. 7). Thereby, the flexible plate 32 can be deformed so as to allow expansion and contraction in the longitudinal direction due to heat of the exhaust static pressure tube 14.
As described above, the flexible plate 32 has a role of supporting the weight of the exhaust static pressure pipe 14 at each position while suppressing thermal deformation in the longitudinal direction of the exhaust static pressure pipe 14 and suppressing vibration in the exhaust pipe lateral direction. Yes.
　図４には、たわみ板３２を正面から見た図が示されている。同図に示されているように、たわみ板３２の上端は、排気静圧管１４に取り付けられて下方に突出する上側取付板（上側取付部）４０に対して、複数のボルト４１ａ及びナット４１ｂ（図５参照）等によって剛に固定されている。具体的には、図５に示すように、たわみ板３２を構成する複数のプレート（第１板状体）３２ａ，３２ｂを上側取付板４０の両側から挟み込んだ状態でたわみ板３２の上端が固定されている。 FIG. 4 shows a view of the flexible plate 32 as seen from the front. As shown in the figure, the upper end of the flexible plate 32 is attached to the exhaust static pressure pipe 14 and protrudes downward with respect to an upper mounting plate (upper mounting portion) 40, and a plurality of bolts 41a and nuts 41b ( (See FIG. 5). Specifically, as shown in FIG. 5, the upper end of the flexible plate 32 is fixed in a state where a plurality of plates (first plate-like bodies) 32 a and 32 b constituting the flexible plate 32 are sandwiched from both sides of the upper mounting plate 40. Has been.
　たわみ板３２の下端は、図４に示されているように、掃気トランク２０の上部にボルト４５（図６参照）等によって固定された下側取付板（下側取付部）４３に対して、複数のボルト４４ａ（図５参照）及びナット４４ｂ等によって固定されている。具体的には、図５に示すように、たわみ板３２を構成する複数のプレート３２ａ，３２ｂを下側取付板４３の両側から挟み込んだ状態でたわみ板３２の下端が固定されている。 As shown in FIG. 4, the lower end of the flexible plate 32 has a lower mounting plate (lower mounting portion) 43 fixed to the upper portion of the scavenging trunk 20 by a bolt 45 (see FIG. 6) or the like. It is fixed by a plurality of bolts 44a (see FIG. 5) and nuts 44b. Specifically, as shown in FIG. 5, the lower end of the flexible plate 32 is fixed in a state where a plurality of plates 32 a and 32 b constituting the flexible plate 32 are sandwiched from both sides of the lower mounting plate 43.
　図６に示されているように、たわみ板３２は、鉄系の金属製とされた複数のプレート３２ａ，３２ｂによって構成されている。具体的には、たわみ板３２は、上下の取付部４０，４３を挟むように対向配置された１対の対向プレート３２ａ，３２ａと、一方（図６では左側）の対向プレート３２ａの外側に重ねられた状態で配置された隣接プレート３２ｂとから構成されている。本実施形態では、たわみ板３２を構成するプレートは合計で３枚とされている。ただし、プレートの数は４枚以上であっても良く、他方（図６では右側）の対向プレート３２ａに重ねるように隣接プレート３２ｂを設けてもよい。 As shown in FIG. 6, the flexible plate 32 is composed of a plurality of plates 32a and 32b made of iron-based metal. Specifically, the flexible plate 32 is overlapped with a pair of opposed plates 32a and 32a arranged so as to sandwich the upper and lower mounting portions 40 and 43, and on the outside of one (left side in FIG. 6) opposed plate 32a. It is comprised from the adjoining plate 32b arrange | positioned in the state made. In the present embodiment, the total number of plates constituting the flexible plate 32 is three. However, the number of plates may be four or more, and the adjacent plate 32b may be provided so as to overlap the other (right side in FIG. 6) opposing plate 32a.
　３枚の各プレート３２ａ，３２ｂの形状は、全て略同一形状とされ、同じ板厚ｔ、同じ上下の固定部間距離Ｌ１、同じ幅ｂ（図４参照）を有している。プレート３２ａ，３２ｂの板厚ｔは、５ｍｍ以上とされ、機種によっては１０ｍｍ以上または１４ｍｍ以上、さらには２０ｍｍ以上とされる。固定部間距離Ｌ１は、６００ｍｍ以上とされ、機種によっては１０００ｍｍ以上、さらには２０００ｍｍ以上とされる。
　また、プレート３２ａ，３２ｂの幅ｂに対する固定部間距離Ｌ１（Ｌ１／ｂ）は、１よりも大きく、機種によっては、１．５以上、さらには２．０以上とされた縦長形状となっている。
　なお、各プレートの形状は厳密に同一形状であることは必要とされず、各プレートから構成されるたわみ板としての機能を有する限りそれぞれのプレートの形状を適宜変更させても良い。また、板厚ｔを各プレートで異なることとしても良い。ただし、各プレートの板厚ｔは、上下の取付板４０，４３の板厚Ｔよりも薄いことが好ましく、また、各プレートの板厚ｔを積算した合計板厚は、たわみ板３２に求められる設計強度から決定される。 The three plates 32a and 32b have substantially the same shape, and have the same thickness t, the same distance L1 between the upper and lower fixed parts, and the same width b (see FIG. 4). The plate thickness t of the plates 32a and 32b is 5 mm or more, and is 10 mm or more, 14 mm or more, and further 20 mm or more depending on the model. The distance L1 between the fixed parts is 600 mm or more, and is 1000 mm or more, and further 2000 mm or more depending on the model.
Further, the distance L1 (L1 / b) between the fixed portions with respect to the width b of the plates 32a and 32b is larger than 1, and depending on the model, it is a vertically long shape that is 1.5 or more, further 2.0 or more. Yes.
In addition, the shape of each plate does not need to be exactly the same shape, and the shape of each plate may be appropriately changed as long as it has a function as a flexible plate composed of each plate. The plate thickness t may be different for each plate. However, the plate thickness t of each plate is preferably thinner than the plate thickness T of the upper and lower mounting plates 40, 43, and the total plate thickness obtained by integrating the plate thickness t of each plate is obtained by the flexible plate 32. Determined from design strength.
　本実施形態のたわみ板３２は、１対の２枚のプレートとするのではなく、３枚のプレート３２ａ，３２ｂから構成されているが、この有利点について以下に説明する。 The flexible plate 32 of this embodiment is not composed of a pair of two plates, but is composed of three plates 32a and 32b. This advantage will be described below.
　排気静圧管１４の熱伸びによるたわみ板３２の曲げモーメントＭは、下式で表される。
　　Ｍ＝６・Ｅ・ｎ・Ｉ１・δｍａｘ／Ｌ１＾２　［Ｋｇｆ－ｍｍ］　　・・・（１）
　ここで、上式における各諸元は以下の通りである。
　Ｅ：縦弾性係数（２１０００ｋｇｆ／ｍｍ2）
　ｎ：たわみ板を構成するプレートの枚数
　Ｉ１：プレートの横方向中心線の断面２次モーメント
　ｂ：プレートの幅（ｍｍ）
　ｔ：プレートの厚さ（ｍｍ）
　Ｌ１：プレートの固定部間長さ（ｍｍ）
　δｍａｘ：熱伸び量（ｍｍ） The bending moment M of the flexible plate 32 due to the thermal elongation of the exhaust static pressure pipe 14 is expressed by the following equation.
M = 6 · E · n · I1 · δmax / L1 ^ 2 [Kgf-mm] (1)
Here, each item in the above equation is as follows.
E: Longitudinal elastic modulus (21000 kgf / mm 2 )
n: Number of plates constituting the flexible plate I1: Second moment of section of the center line in the transverse direction of the plate b: Plate width (mm)
t: Plate thickness (mm)
L1: Length between fixed parts of plate (mm)
δmax: thermal elongation (mm)
　断面二次モーメントI1は、下式のように表される。
　　Ｉ１＝ｂ・ｔ＾３／１２　［ｍｍ４］
　この関係を用いて式（１）を変形すると、下式となる。
　　Ｍ＝Ｅ・ｎ・ｂ・ｔ＾３・δｍａｘ/（２・Ｌ１＾２）　［Ｋｇｆ－ｍｍ］・・・（２） The cross-sectional secondary moment I1 is expressed by the following equation.
I1 = b · t ^ 3/12 [mm 4 ]
When equation (1) is transformed using this relationship, the following equation is obtained.
M = E · n · b · t ^ 3 · δmax / (2 · L1 ^ 2) [Kgf-mm] (2)
　熱伸び量δｍａｘとプレート固定部間長さＬ１及びプレート幅ｂは、ディーゼルエンジン１本体側の設計で決定されるため、ここでは定数と考える。よって、Ｅ，ｂ，δｍａｘ，Ｌ１を定数とすれば、式（２）は下式のように変形できる。
　　Ｍ∝ｎ・ｔ＾３　　・・・（３）
　上式から、排気静圧管１４の熱伸びによって生じるたわみ板３２の固定部における曲げモーメントＭは、プレートの枚数ｎに比例し、プレートの板厚ｔの３乗に比例することが分かる。 Since the thermal elongation amount δmax, the plate fixing portion length L1 and the plate width b are determined by the design on the diesel engine 1 main body side, they are considered as constants. Therefore, if E, b, δmax, and L1 are constants, the equation (2) can be transformed as the following equation.
M∝n · t ^ 3 (3)
From the above equation, it can be seen that the bending moment M at the fixed portion of the flexible plate 32 caused by the thermal expansion of the exhaust static pressure tube 14 is proportional to the number n of plates and proportional to the cube of the plate thickness t.
　上式（３）に示した曲げモーメントＭは、たわみ板３２の各プレートの固定部を介して上側取付板４０及び下側取付板４３のそれぞれに伝達される。上側取付板４０及び下側取付板４３には、この曲げモーメントＭによって、下式に示す応力σが発生する。
　　σ＝Ｍ／Ｚ　［ｋｇｆ／ｍｍ２］　　・・・（４）
　ここで、上式における各諸元は以下の通りである。
　Ｚ：それぞれの取付板４０，４３の断面係数（Ｚ＝ｂ１・Ｔ＾２／１２）
　Ｔ：各取付板４０，４３の厚さ（ｍｍ）
　ｂ１：各取付板４０，４３の幅（ｍｍ） The bending moment M shown in the above expression (3) is transmitted to each of the upper mounting plate 40 and the lower mounting plate 43 through the fixing portion of each plate of the flexible plate 32. Due to this bending moment M, a stress σ shown in the following equation is generated in the upper mounting plate 40 and the lower mounting plate 43.
σ = M / Z [kgf / mm 2 ] (4)
Here, each item in the above equation is as follows.
Z: Section modulus of each mounting plate 40, 43 (Z = b1 · T ^ 2/12)
T: thickness of each mounting plate 40, 43 (mm)
b1: Width of each mounting plate 40, 43 (mm)
　取付板４０，４３の圧さＴ及び幅ｂ１は、排気静圧管１４及びディーゼルエンジン１本体側の設計で決定されるため、ここでは定数と考える。よって、Ｔ，ｂ１，Ｚを定数とすれば、上式（４）は下式のように変形できる。
　　σ∝Ｍ　　・・・（５） Since the pressure T and the width b1 of the mounting plates 40 and 43 are determined by the design of the exhaust static pressure pipe 14 and the diesel engine 1 main body side, they are considered as constants here. Therefore, if T, b1, and Z are constants, the above equation (4) can be transformed into the following equation.
σ∝M (5)
　ゆえに、式（３）及び式（５）から、下式（６）が導かれる。
　　σ∝Ｍ∝ｎ・ｔ＾３　　・・・（６）
　上式から、取付板４０，４３に生じる応力は、たわみ板３２から取付板４０，４３に伝達される曲げモーメントMに比例するとともに、プレートの枚数ｎに比例し、プレートの板厚ｔの３乗に比例することが分かる。 Therefore, the following equation (6) is derived from the equations (3) and (5).
σ∝M∝n · t ^ 3 (6)
From the above equation, the stress generated in the mounting plates 40 and 43 is proportional to the bending moment M transmitted from the flexible plate 32 to the mounting plates 40 and 43, and is proportional to the number n of plates, and the plate thickness t is 3 It can be seen that it is proportional to the power.
　次に、排気静圧管１４と排気静圧管１４を支えるたわみ板３２の排気管横方向の固有振動数ｆＥＣについて検討する。固有振動数ｆＥＣは、下式で表される。
　　ｆＥＣ=（ｋ１／ｍ）＾０．５／（２・π）　［Ｈｚ］　　・・・（７）
　ここで、上式における各諸元は以下の通りである。
　ｋ１：排気管横方向のばね定数
　Ｉ２：プレートの長手方向中心線の断面２次モーメント
　ｍ：排気静圧管１４の質量 Next, the natural frequency f EC in the exhaust pipe lateral direction of the exhaust static pressure pipe 14 and the flexible plate 32 supporting the exhaust static pressure pipe 14 will be examined. The natural frequency f EC is expressed by the following equation.
f EC = (k1 / m) ^ 0.5 / (2 · π) [Hz] (7)
Here, each item in the above equation is as follows.
k1: Spring constant in the lateral direction of the exhaust pipe I2: Cross-sectional secondary moment of the longitudinal center line of the plate m: Mass of the exhaust static pressure pipe 14
　なお、ばね定数k1及び断面二次モーメントＩ２は下式で表される。
　　ｋ１＝３・Ｅ・ｎ・Ｉ２／Ｌ１＾３
　　Ｉ２＝ｔ・ｂ＾３／１２　［ｍｍ４］
　これらを上式（７）に代入すると、下式となる。
　　fＥＣ＝（3・E・n・ｔ・ｂ＾3/（12・ｍ・L1＾3））＾0.5/（2・π）
　　　　＝11.5・（（ｎ・ｔ・ｂ＾3）/（m・L1＾3））＾0.5　［Hz］　・・・（８） The spring constant k1 and the cross-sectional secondary moment I2 are expressed by the following equations.
k1 = 3 · E · n · I2 / L1 ^ 3
I2 = t · b ^ 3/12 [mm 4 ]
If these are substituted into the above equation (7), the following equation is obtained.
f EC = (3 · E · n · t · b ^ 3 / (12 · m · L1 ^ 3)) ^ 0.5 / (2 · π)
= 11.5 ・ ((n ・ t ・ b ^ 3) / (m ・ L1 ^ 3)) ^ 0.5 [Hz] (8)
　排気静圧管１４の質量ｍは、排気静圧管の容積及び強度より決定されるため、ここでは定数と考える。よって、Ｅ，ｂ，ｍ，Ｌ１を定数とすれば、下式のように変形できる。
　　ｆＥＣ∝（ｎ・ｔ）＾０．５　　・・・（９）
　上式から、たわみ板の排気管横方向の固有振動数ｆＥＣは、プレートの枚数の０．５乗に比例し、プレートの板厚の０．５乗に比例する。 Since the mass m of the exhaust static pressure pipe 14 is determined by the volume and strength of the exhaust static pressure pipe, it is considered as a constant here. Therefore, if E, b, m, and L1 are constants, the following equation can be obtained.
f EC ∝ (n · t) ^ 0.5 (9)
From the above formula, the natural frequency f EC of the flexible plate in the exhaust pipe lateral direction is proportional to the 0.5th power of the number of plates and is proportional to the 0.5th power of the plate thickness.
　プレートの枚数ｎや板厚ｔの変更によってたわみ板３２から取付板４０，４３に伝達される曲げモーメントMが変化し、これに伴い取付板４０，４３に生じる応力σが変化した場合に、応力σが増大して上下の取付板４０，４３が損傷を受けないようにするためには、プレートの枚数ｎや板厚ｔの変更の前後で応力σ（曲げモーメントＭ）が少なくとも一定とされる必要がある。そのためには、上式（６）から下式が導かれる。
　　ｔ∝（１／ｎ）＾（１／３）　　・・・（１０）
　上式（１０）から、１枚のプレートで受ける応力σと同じ応力σとなるように２枚のプレートに変更する場合、（１／２）＾（１／３）＝約０．８倍の板厚とされたプレートを２枚重ねれば良いことが分かる。すなわち、約０．８倍未満の板厚のプレートであれば、１枚のプレートの場合よりもプレートに生じる応力が小さくなる。 When the bending moment M transmitted from the flexible plate 32 to the mounting plates 40 and 43 is changed by changing the number n of plates and the plate thickness t, the stress σ generated in the mounting plates 40 and 43 changes accordingly. In order to prevent the upper and lower mounting plates 40 and 43 from being damaged by increasing σ, the stress σ (bending moment M) is at least constant before and after the change in the number n of plates and the thickness t. There is a need. For that purpose, the following equation is derived from the above equation (6).
t∝ (1 / n) ^ (1/3) (10)
From the above equation (10), when changing to two plates so that the stress σ is the same as the stress σ received by one plate, (1/2) ^ (1/3) = about 0.8 times It can be seen that it is sufficient to stack two plates having a thickness. That is, if the plate has a thickness of less than about 0.8 times, the stress generated in the plate is smaller than in the case of a single plate.
　プレートの枚数ｎや板厚ｔの変更の前後で一定とした曲げモーメントMとなるように上式（１０）に従って板厚ｔを決定した場合、たわみ板３２の排気管横方向の固有振動数ｆＥＣは式（９）から下式のようになる。
　　ｆＥＣ∝ｎ＾（１／３）　　・・・（１１）
　上式から分かるように、プレートの枚数ｎや板厚ｔの変更の前後で曲げモーメントＭが変化しないように各プレートの板厚ｔを決定した場合、プレートの枚数ｎを増やすほどたわみ板３２の横方向の固有振動数ｆＥＣはプレート枚数の１／３乗に比例して大きくなる。 When the plate thickness t is determined in accordance with the above equation (10) so that the bending moment M is constant before and after the change of the number n of plates and the plate thickness t, the natural frequency f of the flexible plate 32 in the exhaust pipe lateral direction f. EC is represented by the following equation from equation (9).
f EC ∝n ^ (1/3) (11)
As can be seen from the above equation, when the plate thickness t of each plate is determined so that the bending moment M does not change before and after the change in the number n of plates and the plate thickness t, the flexure plate 32 increases as the number n of plates increases. The natural frequency f EC in the lateral direction increases in proportion to the 1/3 power of the number of plates.
　また、式（６）及び式（９）から、次のように考えることもできる。すなわち、たわみ板の固有振動数を変えることなく、板厚ｔとされた１枚のプレートを用いる場合よりも、同じ板厚ｔでも半分の板厚である０．５ｔとされた２枚のプレートを用いた方が、取付板４０，４３に生じる応力σを小さくすることができる。
　したがって、本実施形態のように、１対の２枚のプレートとした場合に、一方または両方のプレートの板厚を増大させて固有振動数の増大を図るのではなく、１対のプレート３２ａに同じ板厚の隣接プレート３２ｂを加えた３枚のプレート３２ａ，３２ｂとすることによって、固有振動数の増大を図るとともに、取付板４０，４３に伝達されるモーメントＭの増大を回避することができる。 Moreover, it can also consider as follows from Formula (6) and Formula (9). That is, two plates with 0.5t, which is half the plate thickness even with the same plate thickness t, than when using one plate with the plate thickness t without changing the natural frequency of the flexible plate It is possible to reduce the stress σ generated in the mounting plates 40 and 43 by using.
Therefore, when a pair of two plates is used as in the present embodiment, the natural frequency is not increased by increasing the plate thickness of one or both plates, but the pair of plates 32a. By using three plates 32a and 32b including the adjacent plate 32b having the same thickness, it is possible to increase the natural frequency and to avoid an increase in the moment M transmitted to the mounting plates 40 and 43. .
　以上の通り、本実施形態によれば、以下の作用効果を奏する。
　ディーゼルエンジン１の運転中には、複数のシリンダから種々のタイミングで排ガスが排気静圧管１４へと導かれる。排気静圧管１４内では、排ガスの脈動が抑えられ、排ガスのエネルギーが静圧に変換される。このとき、排気静圧管１４には、ディーゼルエンジン１本体から伝達される振動、排ガス圧力の影響や排気静圧管１４の自重等が加わるため、排気静圧管１４を支持板３０及びたわみ板３２によって下方から支持する。
　排気静圧管１４の主たる重量は、長手方向の略中央位置に設けられた支持板３０によって支持される。排気静圧管１４の長手方向の振動は、長手方向に延在する支持板３０によって抑えられる。 As described above, according to the present embodiment, the following operational effects are obtained.
During operation of the diesel engine 1, exhaust gas is guided from the plurality of cylinders to the exhaust static pressure pipe 14 at various timings. In the exhaust static pressure pipe 14, the pulsation of the exhaust gas is suppressed, and the energy of the exhaust gas is converted into a static pressure. At this time, vibrations transmitted from the main body of the diesel engine 1, the influence of exhaust gas pressure, the self-weight of the exhaust static pressure pipe 14, and the like are applied to the exhaust static pressure pipe 14. Support from.
The main weight of the exhaust static pressure pipe 14 is supported by a support plate 30 provided at a substantially central position in the longitudinal direction. Vibration in the longitudinal direction of the exhaust static pressure pipe 14 is suppressed by the support plate 30 extending in the longitudinal direction.
　一方、排気静圧管１４の各長手方向位置における部分的な荷重は、たわみ板３２によって支持される。排気静圧管１４の横方向の振動は、排気静圧管１４の横方向に延在するたわみ板３２によって抑えられる。また、排気静圧管１４の長手方向における熱伸びは、図７に示すように、たわみ板３２が排気静圧管１４の長手方向に撓んで変形することによって許容する。 On the other hand, the partial load at each longitudinal position of the exhaust static pressure pipe 14 is supported by the flexible plate 32. The vibration in the lateral direction of the exhaust static pressure tube 14 is suppressed by the flexible plate 32 extending in the lateral direction of the exhaust static pressure tube 14. Further, the thermal elongation in the longitudinal direction of the exhaust static pressure tube 14 is allowed by the deformation of the flexible plate 32 in the longitudinal direction of the exhaust static pressure tube 14 as shown in FIG.
　本実施形態では、たわみ板３２を一対の対向プレート３２ａに加えて、これら対向プレート３２ａと同じ板厚とされた隣接プレート３２ｂを対向プレート３２ａに隣接して設けることとした。このようにプレートを合計で３枚とすることによって横方向の固有振動数を上げることができる。
　また、プレートの板厚を増大するのではなく、プレートの枚数を増やすことによって全体の合計板厚を増大してたわみ板３２の剛性を上げることにした。このようにたわみ板３２の剛性を上げても、厚い１枚のプレートとするのではなくこれを分割した薄いプレートを組み合わせることとしたので、たわみ板３２の固定部から上側取付部４０および下側取付部４３に伝達される曲げモーメントの増加を抑えることができ、上側取付部４０および下側取付部４３に生じる応力の増大を抑えることで、排気静圧管１４や掃気トランク２０に固定する固定部の損傷を回避することができる。 In the present embodiment, the flexible plate 32 is added to the pair of opposing plates 32a, and the adjacent plate 32b having the same thickness as the opposing plates 32a is provided adjacent to the opposing plate 32a. Thus, the natural frequency in the lateral direction can be increased by using three plates in total.
Further, instead of increasing the plate thickness, the total plate thickness is increased by increasing the number of plates, thereby increasing the rigidity of the flexible plate 32. Even if the rigidity of the flexible plate 32 is increased in this way, a thin plate obtained by dividing the rigid plate 32 is combined instead of a single thick plate, so that the upper mounting portion 40 and the lower side of the flexible plate 32 are fixed to each other. An increase in bending moment transmitted to the mounting portion 43 can be suppressed, and a fixing portion that is fixed to the exhaust static pressure pipe 14 or the scavenging trunk 20 by suppressing an increase in stress generated in the upper mounting portion 40 and the lower mounting portion 43. Damage can be avoided.
　なお、上述した実施形態では、舶用主機として用いられる大型ディーゼルエンジンとしたが、本発明はこれに限定されるものではなく、排気静圧管を備えるものであれば他の内燃機関にも適用できる。
　また、上述した実施形態では、たわみ板の下端の接続先を掃気トランクとして説明したが、本発明はこれに限定されるものではなく、たわみ板の下端を接続するために適切な内燃機関本体側の構造であれば良い。
　また、上述した実施形態では、支持板３０を備えた構成として説明したが、支持板３０を使用せずにたわみ板３２のみで排気静圧管１４を支える構成としても良い。 In the embodiment described above, a large diesel engine used as a marine main engine is used. However, the present invention is not limited to this, and can be applied to other internal combustion engines as long as they have an exhaust static pressure pipe.
In the above-described embodiment, the connection destination of the lower end of the flexible plate is described as the scavenging trunk. However, the present invention is not limited to this, and the internal combustion engine main body side suitable for connecting the lower end of the flexible plate is used. If it is the structure of.
In the above-described embodiment, the configuration including the support plate 30 has been described. However, the exhaust static pressure tube 14 may be supported only by the flexible plate 32 without using the support plate 30.
１　ディーゼルエンジン（内燃機関）
９　シリンダライナ
１４　排気静圧管
１６　過給機
２０　掃気トランク
３０　支持板（第２支持部）
３２　たわみ板（第１支持部）
３２ａ　対向プレート（対向板状体）
３２ｂ　隣接プレート（隣接板状体）
４０　上側取付板（上側取付部）
４３　下側取付板（下側取付部） 1 Diesel engine (internal combustion engine)
9 Cylinder liner 14 Exhaust static pressure pipe 16 Supercharger 20 Scavenging trunk 30 Support plate (second support part)
32 Flexible plate (first support)
32a Opposing plate (opposing plate)
32b Adjacent plate (adjacent plate)
40 Upper mounting plate (upper mounting part)
43 Lower mounting plate (lower mounting part)

Claims (4)

  1. 　内燃機関本体から排出される排ガスを一時的に貯留するとともに、長手軸線が水平方向に延在する排気静圧管を、前記内燃機関本体に対して支持する排気静圧管支持構造であって、
    　前記排気静圧管と前記内燃機関本体との間に設けられ、該排気静圧管を下方から支持する第１板状体を有し、該第１板状体が前記水平方向に直交するように配置された第１支持部と、
    　前記排気静圧管に対して固定され、前記第１板状体の上端部に取り付けられる上側取付部と、
    　前記内燃機関本体に対して固定され、前記第１板状体の下端部に取り付けられる下側取付部と、
    を備え、
    　前記第１板状体は、前記上側取付部および前記下側取付部を間に挟んで接続された１対の対向板状体と、少なくとも一方の該対向板状体に隣接して設けられた隣接板状体とから構成されることを特徴とする排気静圧管支持構造。     An exhaust static pressure pipe support structure for temporarily storing exhaust gas discharged from an internal combustion engine body and supporting an exhaust static pressure pipe whose longitudinal axis extends in a horizontal direction with respect to the internal combustion engine body,
    A first plate-like body is provided between the exhaust static pressure pipe and the internal combustion engine main body and supports the exhaust static pressure pipe from below, and is arranged so that the first plate-like body is orthogonal to the horizontal direction. A first support portion,
    An upper attachment portion fixed to the exhaust static pressure pipe and attached to an upper end portion of the first plate-like body;
    A lower attachment portion fixed to the internal combustion engine body and attached to a lower end portion of the first plate-like body;
    With
    The first plate-like body is provided adjacent to at least one of the pair of opposed plate-like bodies and a pair of opposed plate-like bodies connected with the upper attachment portion and the lower attachment portion interposed therebetween. An exhaust static pressure pipe support structure comprising an adjacent plate-like body.
  2. 　前記対向板状体と前記隣接板状体とは、同じ板厚とされていることを特徴とする請求項１に記載の排気静圧管支持構造。 The exhaust static pressure pipe support structure according to claim 1, wherein the opposing plate-like body and the adjacent plate-like body have the same plate thickness.
  3. 　前記排気静圧管と前記内燃機関本体との間に設けられ、該排気静圧管を下方から支持する第２板状体を有し、該第２板状体が前記水平方向に沿って配置された第２支持部を備えていることを特徴とする請求項１又は２に記載の排気静圧管支持構造。 A second plate-like body is provided between the exhaust static pressure pipe and the internal combustion engine main body and supports the exhaust static pressure pipe from below, and the second plate-like body is disposed along the horizontal direction. The exhaust static pressure pipe support structure according to claim 1, further comprising a second support portion.
  4. 　請求項１から３のいずれかに記載された排気静圧管支持構造を備えていることを特徴とする内燃機関。　 An internal combustion engine comprising the exhaust static pressure pipe support structure according to any one of claims 1 to 3. *
PCT/JP2015/064140 2014-05-28 2015-05-18 Exhaust static tube support structure and internal combustion engine equipped with same WO2015182414A1 (en)

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Citations (2)

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Publication number Priority date Publication date Assignee Title
JP2008002341A (en) * 2006-06-22 2008-01-10 Man Diesel As Exhaust gas receiver for large 2-cycle diesel engine
JP4995990B1 (en) * 2011-01-25 2012-08-08 マン・ディーゼル・アンド・ターボ，フィリアル・アフ・マン・ディーゼル・アンド・ターボ・エスイー，ティスクランド Large two-stroke diesel engine, and support plate structure for connecting engine main structure and exhaust gas receiver

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DE3635478C1 (en) * 1986-10-18 1988-02-11 Mtu Friedrichshafen Gmbh Exhaust pipe for a charged, multi-cylinder internal combustion engine
JP3306845B2 (en) * 1996-06-10 2002-07-24 ヤンマーディーゼル株式会社 Exhaust system structure of internal combustion engine

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Publication number Priority date Publication date Assignee Title
JP2008002341A (en) * 2006-06-22 2008-01-10 Man Diesel As Exhaust gas receiver for large 2-cycle diesel engine
JP4995990B1 (en) * 2011-01-25 2012-08-08 マン・ディーゼル・アンド・ターボ，フィリアル・アフ・マン・ディーゼル・アンド・ターボ・エスイー，ティスクランド Large two-stroke diesel engine, and support plate structure for connecting engine main structure and exhaust gas receiver

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