CN103917764A - Torsional vibration stress reduction control device, marine vessel comprising same, and torsional vibration stress reduction method - Google Patents
Torsional vibration stress reduction control device, marine vessel comprising same, and torsional vibration stress reduction method Download PDFInfo
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- CN103917764A CN103917764A CN201280055865.7A CN201280055865A CN103917764A CN 103917764 A CN103917764 A CN 103917764A CN 201280055865 A CN201280055865 A CN 201280055865A CN 103917764 A CN103917764 A CN 103917764A
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- Prior art keywords
- torsional vibration
- vibration stress
- main frame
- control gear
- scavenging
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/30—Mounting of propulsion plant or unit, e.g. for anti-vibration purposes
- B63H21/302—Mounting of propulsion plant or unit, e.g. for anti-vibration purposes with active vibration damping
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/22—Safety or indicating devices for abnormal conditions
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/30—Mounting of propulsion plant or unit, e.g. for anti-vibration purposes
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- 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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
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- 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
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
- F02D29/02—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving vehicles; peculiar to engines driving variable pitch propellers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
-
- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
- F02B2039/162—Control of pump parameters to improve safety thereof
- F02B2039/166—Control of pump parameters to improve safety thereof the fluid pressure in the pump or exhaust drive being limited
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- 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
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
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- 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
- F02B37/12—Control of the pumps
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/28—Control for reducing torsional vibrations, e.g. at acceleration
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- 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
Abstract
A torsional vibration stress reduction control device (50) according to the present invention is used to reduce torsional vibration stress occurring in a propulsion shafting (10) in a marine vessel (100) comprising a propulsion shafting (10) which rotates integrally with a propulsion propeller (11), a main engine (20) for driving the propulsion shafting (10), and a supercharger (30) which has a turbine (31) driven by exhaust (27) expelled from the main engine (20) and which uses the rotational force of the turbine (31) as motive power to compress new air and supply scavenged air (24) to the main engine (20), wherein the pressure of the scavenged air (24) is reduced when the torsional vibration stress is a predetermined value or greater.
Description
Technical field
The torsional vibration stress that the present invention relates to the torsional vibration stress of the Propulsion Systems place generation that is reduced in boats and ships reduces control gear and possesses this torsional vibration stress the boats and ships that reduce control gear.Relate to the torsional vibration stress reduction method that reduces torsional vibration stress again.
Background technique
The main frame that is loaded into boats and ships is by bent axle, the to-and-fro motion of piston to be transformed to the structure rotatablely moving, due to the to-and-fro motion in different phase places of multiple pistons, therefore the power on bent axle is because of the rotary angle position difference of bent axle, and the warping stress producing at the Propulsion Systems place that comprises bent axle is also because the rotary angle position of bent axle is different.The warping stress rotary synchronous main and main frame consequently producing at Propulsion Systems place changes.On the other hand, Propulsion Systems has eigentone in each vibrational mode.And, exist above-mentioned warping stress to increase in a flash, and can damage in some cases the danger of Propulsion Systems when consistent in the rotation of main frame and the eigentone of Propulsion Systems.About the torsional vibration stress when this resonance, inquiring at present countermeasure always.
As one in the countermeasure of torsional vibration stress, there is the balance that forms size and the weight etc. of the member of Propulsion Systems by change to change the method for the eigentone of Propulsion Systems.According to the method, can make the peak value of torsional vibration stress move to the lower slow-speed of revolution of frequency of utilization in the utilization of boats and ships, or reduce the value of torsional vibration stress.But the such change of the diameter of axle that reduces the member of formation of Propulsion Systems exists intensity such problem that declines, exist manufacture cost to rise and weight increases such problem and increase the such change of the diameter of axle.Again, also have by being the material that intensity is higher by the material change of the member of formation of Propulsion Systems, thereby expand the method for the admissible value of torsional vibration stress, but the method also can make manufacture cost rise, and have and produce other the possibility of problem that is accompanied by material change.So, the such countermeasure of member of formation of change Propulsion Systems easily has problems at the aspect such as manufacture cost and intensity.
With respect to this, also inquire into the member of formation that does not change Propulsion Systems, and from the countermeasure of control aspect Avoids or reduces torsional vibration stress.For example, patent documentation 1 discloses the dangerous rotary speed area eluding game device of removing the dangerous rotary speed area that speed regulator scavenging pressure limiter (governor scavenging pressure limiter) passed through when Offhost is in speedup in advance by temporary transient.
Again, to disclose and be formed as engine speed be the anti-locking apparatus of torsion that regulation rotating speed improves the bent axle of the structure of boost pressure when above to patent documentation 2.According to this device, the power that acts on upward bent axle diminishes, thereby the torsion of bent axle is diminished.
Again, patent documentation 3 discloses the crankshaft torsion equipment for inhibiting of vibration of adjusting the diesel engine of fuel injection timing or the structure between fuel injection period when the rotating speed that is formed as diesel engine is positioned at the scope of resonance speed.According to this device, starting of oscillation torque composition diminishes, thereby can reduce resonant stress.
Prior art document:
Patent documentation:
Patent documentation 1: Japanese Patent Publication 06-39072 communique;
Patent documentation 2: TOHKEMY 2005-273571 communique;
Patent documentation 3: Japanese kokai publication hei 03-275958 communique.
Summary of the invention
The problem that invention will solve:
But the invention of recording in patent documentation 1 is because the size self of torsional vibration stress is unchanged, so can not say the solution countermeasure of essence.Again, the invention of recording in patent documentation 2 be engine speed compared with high and engine load is lower and the region of taking as the leading factor with respect to torsional vibration inertial force in countermeasure, its to as if conditional.Especially be difficult to be applied to such the operating as in main motor with low speed high load of boats and ships main frame.Again, the object of control of the invention of recording in patent documentation 3 is that fuel sprays, thus be that the control that is directly connected to the performance of main frame is complicated control, and exist and must possess the problem of adjusting fuel injection timing and the mechanism between injection period.
Therefore, the object of the present invention is to provide a kind of torsional vibration stress reduction control gear that reduces torsional vibration stress by easy control.
The means of dealing with problems:
According to torsional vibration stress according to the present invention reduce control gear be for reducing possess with the Propulsion Systems that advances the propeller cavitation of use to rotate integratedly, drive the main frame of this Propulsion Systems and there is the turbine of the exhaust gas drive of being discharged from this main frame and using the rotating force of this turbine as the new gas of powered compressor and the torsional vibration stress that scavenging is supplied to the torsional vibration stress that the described Propulsion Systems in the boats and ships of pressurized machine of described main frame produces reduce control gear, and to be formed as described torsional vibration stress be specified value when above, reduce the structure of the pressure of described scavenging.
According to this structure, torsional vibration stress is that specified value reduces the pressure of scavenging when above, although therefore there is the risk of the Efficiency Decreasing of main frame, can reduce effectively torsional vibration stress.
Again, can be to be also formed as reducing in control gear at above-mentioned torsional vibration stress, the reduction of the pressure of described scavenging drives the pressure of the described exhaust of the turbine of described pressurized machine to carry out structure by reduction.
Again, also can be to be formed as reducing in control gear at above-mentioned torsional vibration stress, described pressurized machine has the exhaust that will discharge from described main frame and guide to the exhaust passageway of described turbine and be arranged at the bypass valve this exhaust passageway, and the reduction of the pressure of the described exhaust structure of being undertaken by open described bypass valve.
Again, can be to be also formed as reducing in control gear at above-mentioned torsional vibration stress, described pressurized machine has variable-nozzle at the leading portion of described turbine, and the reduction of the pressure of the described exhaust structure of being undertaken by changing the aperture of described variable-nozzle.
Again, also can be to be formed as reducing in control gear at above-mentioned torsional vibration stress, also possess the scavenging bypass valve that the scavenging of supplying with to described main frame from described pressurized machine is detoured, and the reduction of the pressure of described scavenging is by the structure that regulates described scavenging bypass valve to carry out.
Again, can be to be also formed as reducing in control gear at above-mentioned torsional vibration stress, judge by the rotating speed of described main frame whether described torsional vibration stress is structure more than specified value.
Again, can be to be also formed as reducing in control gear at above-mentioned torsional vibration stress, judge by measuring torsional vibration stress whether described torsional vibration stress is structure more than specified value.
In addition, boats and ships according to the present invention possess above-mentioned any one torsional vibration stress reduction control gear.
In addition, torsional vibration stress reduction method according to the present invention is for reducing possessing and the Propulsion Systems that advances the propeller cavitation of use to rotate integratedly, drive the main frame of this Propulsion Systems, with there is the turbine of the exhaust gas drive of being discharged from this main frame and using the rotating force of this turbine as powered compressor scavenging and be supplied to the torsional vibration stress reduction method of the torsional vibration stress that the described Propulsion Systems in the boats and ships of pressurized machine of described main frame produces, judge whether described torsional vibration stress is more than specified value, when judging that described torsional vibration stress is the function that specified value reduces described pressurized machine when above.
Invention effect:
Reduce control gear according to torsional vibration stress of the present invention, can reduce torsional vibration stress by easy control.
Brief description of the drawings
Fig. 1 is according to the skeleton diagram of the boats and ships of an example of the present invention;
Fig. 2 is the chart that the rotating speed of main frame and the relation of torsional vibration stress are shown;
Fig. 3 is the chart illustrating by the control curve of the variable-nozzle of scavenging pressure control gear control;
Fig. 4 illustrates that torsional vibration stress reduces the flow chart of the action of control gear;
Fig. 5 illustrates the load of main frame when reducing the control of control gear and be performed from torsional vibration stress and the chart of the relation of scavenging pressure;
Fig. 6 illustrates the rotating speed of main frame when reducing the control of control gear and be performed from torsional vibration stress and the chart of the relation of torsional vibration stress.
Embodiment
Below, example of the present invention is described.In addition, in the drawings attached of institute below, be marked with identical reference marks and omit repeat specification for identical or suitable key element.
Fig. 1 is according to the skeleton diagram of the boats and ships 100 of an example of the present invention.As shown in Figure 1, boats and ships 100 possess Propulsion Systems 10, main frame 20, pressurized machine 30, scavenging pressure control gear 40 and torsional vibration stress reduction control gear 50.Below, these structures are described successively.
Propulsion Systems 10 is that a series of axle rotating integratedly with the propeller cavitation 11 that advances use is.Propulsion Systems 10 starts from the paper left side of Fig. 1 successively by advancing the propeller cavitation 11 of use, the screw shaft 12 being connected with propeller cavitation 11, with the coaxial jack shaft being connected 13 of screw shaft, is installed near the escapement (flywheel, flywheel) 14 of the main frame 20 of jack shaft 13, as the bent axle 15 connecting with jack shaft 13 of the constituting component of main frame 20 and be installed on regulating wheel (tuning wheel) 16 formations of the end of a contrary side with jack shaft 13 of bent axle 15.In addition, regulating wheel 16 can be installed according to demand.This Propulsion Systems 10 receives the rotating power from main frame 20 by bent axle 15, and entirety is rotated with being integrated.
Main frame 20 is the devices that drive Propulsion Systems 10.The diesel engine of uniflow type according to the main frame 20 of this example.Main frame 20 drives as follows.First, (new gas) 24 from scavenging air pipe 21 to the interior supply scavenging of cylinder 23 by transfer port 22.The scavenging 24 being supplied to is compressed because piston 25 rises, the ignited fuel blast of meanwhile spraying from fuel injection nozzle 26.By this blast, after piston 25 is pushed back downwards, exhaust (mixed gas after burning) 27 is in due course from relief opening 28 to outside drain.The lower end of piston 25 is connected with bent axle 15, and piston 25 repeats as described above moving up and down, with this crankshaft rotating.
The solid line of Fig. 2 illustrates an example of the relation (torsional vibration stress curve 101) of rotating speed and the torsional vibration stress of main frame 20.The transverse axis of Fig. 2 is the rotating speed of main frame 20, and the longitudinal axis is torsional vibration stress.Although be only an example, the in the situation that of Fig. 2,65% rotating speed of main frame 20 is resonance speed, and in the time of this rotating speed, torsional vibration stress rises in a flash.
Here in Fig. 2, be shown in dotted line the first dangerous curve 102 and the second dangerous curve 103.Wherein the first dangerous curve 102 is to be illustrated under the state that produces the torsional vibration stress that exceedes this curve to carry out continuous operation, exists Propulsion Systems may produce the dangerous curve of fatigue ruption.Again, the second dangerous curve 103 is to illustrate to produce the curve that the Propulsion Systems of torsional vibration stress that exceedes this curve cannot be used for boats and ships.In the utilization of actual boats and ships, be set with the rotary speed area that is called forbidding scope (Barred Range).So-called forbidding scope refers to the rotary speed area of forbidding the continuous use of main frame in actual utilization.In this example, the region between the intersection point that the first dangerous curve 102 and torsional vibration stress curve 101 are intersected is set as forbidding region.
Pressurized machine 30 is the devices that suck new gas and the scavenging 24 after compression is supplied to main frame 20 by scavenging air pipe 21.Pressurized machine 30 is mainly made up of turbine 31, variable-nozzle 32, compressor 33, exhaust passageway 34 and bypass valve 35.The exhaust 27 of discharging from main frame 20 is directed into variable-nozzle 32 by exhaust passageway 34.Variable-nozzle 32 is positioned at the leading portion of turbine 31, is made up of multiple nozzle vanes (not shown).This nozzle vane is formed as the structure of variable-angle, can regulate by changing the angle of nozzle vane the aperture of variable-nozzle 32.The pressure (dynamic pressure) of the exhaust 27 that the aperture of variable-nozzle 32 is supplied to while becoming large diminishes, and it is large that the pressure of the exhaust 27 that the aperture of variable-nozzle 32 is supplied to while diminishing becomes.
The exhaust 27 of having passed through variable-nozzle 32 is rotated turbine 31.Turbine 31 is connected by rotor shaft 36 with compressor 33, along with the rotary compressor 33 of turbine 31 also rotates.Compressor 33 compresses the new gas sucking from outside, scavenging 24 is supplied to main frame 20 by scavenging air pipe 21, if but the rotational speed of compressor 33 becomes large, the pressure of the scavenging 24 in the outlet port of compressor 33 also becomes large, become large by means of the pressure in this scavenging air pipe 21 (following, to be called " scavenging pressure ").On above-mentioned exhaust passageway 34, be provided with bypass valve 35 again.When open bypass valve 35, a part of drawing the exhaust 27 of guided turbine 31 detours to outside, thus the pressure decreased of the exhaust being supplied to 27.In addition, bypass valve 35 can be the valve that (ON-OFF switching) type is switched in the changeable switching for the arbitrary state in opening and closing, and can be also the valve that can regulate arbitrarily the regulation type of aperture.
Scavenging pressure control gear 40 is to control the device of scavenging pressure, makes the pressure of the exhaust 27 that turbine 31 rotates control scavenging pressure by control.More specifically, in scavenging pressure control gear 40, by regulating the aperture of bypass valve 35 and variable-nozzle 32 to control the pressure of exhaust 27, control scavenging pressure by means of this.In addition, to be efficiency to improve main frame 20 by the scavenging pressure at sub load place that increases main frame design as object scavenging pressure control gear 40.Scavenging pressure control gear 40 is formed as generating based on control curve 104 described later the control signal of controlling bypass valve 35 and variable-nozzle 32, and as shown in Figure 1, this control signal is sent to the structure of torsional vibration stress reduction control gear 50.Again, scavenging pressure control gear 40 is formed as obtaining the signal relevant to the rotating speed of main frame 20 from tachometer 41, can obtain the signal relevant to fuel tooth bar amount (fuel oil filling amount) from being installed on the fuel index conveyer 61 of petrolift 60, can obtain from scavenging pressure table 42 structure of the signal relevant to scavenging pressure.
Be conceived to control the situation explanation of variable-nozzle 32 from the control (the generation method of control signal) of scavenging pressure control gear 40 here.The solid line of Fig. 3 illustrates an example of the control curve 104 of variable-nozzle 32.The transverse axis of Fig. 3 is the load of main frame 20, and the longitudinal axis is scavenging pressure.Again, in two dotted lines shown in Fig. 3, the straight line of scavenging pressure upper side is that the aperture of variable-nozzle 32 is that common hour scavenging pressure line is (following, be called " the first scavenging pressure line ") 105, scavenging pressure line (following, to be called " the second scavenging pressure line ") the 106 when aperture that scavenging pressure is variable-nozzle compared with the straight line of downside is conventionally maximum.First, scavenging pressure control gear 40 obtains the rotating speed of main frame 20 from tachometer 41, obtains fuel tooth bar amount from fuel index conveyer 61, is inferred the load of main frame 20 by the rotating speed of the main frame 20 obtaining and fuel tooth bar amount.In addition, also can be by obtaining the signal relevant to in-cylinder pressure and rotating relevant signal etc. with pressurized machine and infer main unit load.Further, read the scavenging pressure corresponding with the load of the main frame 20 of inferring from Fig. 3.Then, so that the scavenging pressure reading from Fig. 3 mode control variable-nozzle 32(identical with scavenging pressure by the actual measurement of scavenging pressure table 42 generates control signal).In addition, the actual aperture of variable-nozzle because of atmospheric conditions etc. slightly different.
Like this, scavenging pressure control gear 40 generates control signal based on Fig. 3, if while therefore only carrying out control by scavenging pressure control gear 40, scavenging pressure is passed along control curve 104 as shown in Figure 3.That is, with the example of Fig. 3, the load of main frame 20 during lower than 75% load the aperture of variable-nozzle 32 be minimum, scavenging pressure is passed along the first scavenging pressure line 105.Again, the load of main frame 20 during higher than 75% load the aperture of variable-nozzle 32 become gradually greatly, decline by means of the ratio of the rising of this scavenging pressure.When the load of main frame 20 finally reaches 100% load, the aperture of variable-nozzle 32 becomes maximum, and scavenging pressure is crossing with the second scavenging pressure line 106.In addition, the situation of only controlling variable-nozzle 32 is more than described, but also can have similarly controlled bypass valve 35.Especially in the time that bypass valve 35 is the valve of regulation type, can fine adjustments aperture this point identical with variable-nozzle 32, therefore can control with the such control curve identical with Fig. 3.Again, bypass valve 35 is while opening and closing the valve of switch type, for example carries out, in the time that the load of main frame 20 arrives a certain value (, 75% load), and bypass valve 35 is switched to the such control of standard-sized sheet from complete shut-down.
It is the control gear for reducing torsional vibration stress that torsional vibration stress reduces control gear 50.As shown in Figure 1, torsional vibration stress reduces control gear 50 and is formed as receiving the control signal for controlling variable-nozzle 32 and bypass valve 35 from scavenging pressure control gear 40, receive the signal relevant to the rotating speed of main frame 20 from tachometer 41, and the structure that can transmit control signal to variable-nozzle 32 and bypass valve 35.Torsional vibration stress reduces control gear 50 and works as described below.
Fig. 4 illustrates that torsional vibration stress reduces the flow chart of the action of control gear 50.First, as shown in Figure 4, torsional vibration stress reduces control gear 50 and judges whether torsional vibration stress is specified value above (step S1).In this example, obtain the rotating speed of main frame 20 from tachometer 41, whether be positioned at dangerous rotary speed area by the rotating speed of main frame 20 and judge whether torsional vibration stress is more than specified value.Here, dangerous rotary speed area refers to that torsional vibration stress is the region of the rotating speed of specified value when above, and torsional vibration stress curve based on as shown in Figure 2 presets (with reference to Fig. 6).In this example, dangerous rotary speed area is set as slightly wider than above-mentioned forbidding scope.In addition, in this example, judge by the rotating speed of main frame 20 whether torsional vibration stress is more than specified value, but the testing apparatus of warping stress also can be set on Propulsion Systems 10, directly measure the value of torsional vibration stress and judge.Again, whether be in judgement more than specified value at torsional vibration stress, can using with the irrelevant certain value of the rotating speed of main frame 20 as specified value, also can be using the value of the rotating speed variation along with main frame 20 as specified value.
Then, when judging that torsional vibration stress does not reach specified value when above (being "No" in step S1), torsional vibration stress reduces control gear 50 control signal receiving from scavenging pressure control gear 40 is kept intact and passed on (step S3) to variable-nozzle 32 and bypass valve 35., now variable-nozzle 32 and bypass valve 35 are controlled by scavenging pressure control gear 40.On the other hand, when judging that torsional vibration stress is that specified value is when above (being "Yes" in step S1), it is maximum control signal that torsional vibration stress reduction control gear 50 makes aperture to variable-nozzle 32 transmissions, it is maximum control signal that bypass valve 35 transmissions of aperture adjustment type are made to aperture, and the bypass valve 35 that opens and closes switch type is sent to the control signal (step S2) that makes valve open.That is, when judging that torsional vibration stress is specified value when above, reduce to greatest extent the pressure of the exhaust that is supplied to turbine 31, in other words, control in the mode of the function that reduces pressurized machine 30.Be more than the control that reduces control gear 50 from torsional vibration stress.
Torsional vibration stress reduces control gear 50 and carries out control as above, passes as illustrated in fig. 5 by means of this scavenging pressure.The solid line of Fig. 5 shows the load of main frame 20 and the relation of scavenging pressure (scavenging pressure curve 107) carried out while reducing the control of control gear 50 from torsional vibration stress.The transverse axis of Fig. 5 is the load of main frame 20, and the longitudinal axis is scavenging pressure.In addition, the situation of Fig. 5 and Fig. 3 is same is all the figure while only having controlled variable-nozzle 32.Dotted line shown in Fig. 5 is the first scavenging pressure line 105 shown in Fig. 3 and the second scavenging pressure line 106.As shown in Figure 5, in the time that the load of main frame 20 is less than the corresponding load of dangerous rotary speed area, the control signal of scavenging pressure control gear 40 is kept intact and is transferred to variable-nozzle 32, therefore with the passing of the control curve 104 shown in Fig. 3 in the same manner scavenging pressure pass along the first scavenging pressure line 105.Then, in the time that the load of main frame 20 is the corresponding load of dangerous rotary speed area, making aperture to variable-nozzle 32 transmissions is maximum control signal, and therefore scavenging pressure reduces in a flash and passes along the second scavenging pressure line 106.And then, in the time that the load of main frame 20 is greater than the corresponding load of dangerous rotary speed area, the control signal of scavenging pressure control gear 40 is kept intact and is transferred to variable-nozzle 32, therefore with the passing of the control curve 104 shown in Fig. 3 in the same manner scavenging pressure pass until after the load of main frame 20 reaches 75%, pass to the second scavenging pressure line 106 along the first scavenging pressure line 105.As above, reduce the control of control gear 50 according to torsional vibration stress, torsional vibration stress is specified value when above (when main frame 20 is positioned at dangerous rotating speed), reduction scavenging pressure.
Reduce the control of control gear 50 by torsional vibration stress, the result that scavenging pressure is passed is as illustrated in fig. 5 that torsional vibration stress is passed as illustrated in fig. 6.The solid line of Fig. 6 shows the rotating speed of main frame 20 and the relation of torsional vibration stress (torsional vibration stress curve 108) carried out while reducing the control of control gear 50 from torsional vibration stress.The transverse axis of Fig. 6 is the rotating speed of main frame 20, and the longitudinal axis is torsional vibration stress.Here, in two curves that represent with single-point dotted line of Fig. 6, the curve of torsional vibration stress larger side is the curve identical with the torsional vibration stress curve 101 of Fig. 2, and the aperture that is variable-nozzle 32 is (while also can be described as common operation) torsional vibration stress curve (hereinafter referred to as " the first torsional vibration stress curve ") 109 hour.Again, the curve of torsional vibration stress smaller side is the aperture of variable-nozzle 32 when scavenging pressure is reduced () torsional vibration stress curve (hereinafter referred to as " the second torsional vibration stress curve ") 110 while being maximum.In addition, with the situation of Fig. 2 in the same manner, in Fig. 6, also drawn the first dangerous curve 102 and the second dangerous curve 103.
Based on above-mentioned, the passing of carrying out the torsional vibration stress while reducing the control of control gear 50 from torsional vibration stress is described with reference to Fig. 6.When the rotating speed of main frame 20 is less than dangerous rotary speed area, carry out control so that the aperture of variable-nozzle 32 becomes minimum mode, therefore torsional vibration stress is passed along the first torsional vibration stress curve 109.Then, when the rotating speed of main frame 20 enters dangerous rotary speed area, carry out control so that the aperture of variable-nozzle 32 becomes maximum mode, therefore scavenging pressure reduces in a flash, thereby torsional vibration stress also reduces in a flash.Then,, during the rotating speed of main frame 20 is positioned at dangerous rotary speed area, torsional vibration stress is passed along the second torsional vibration stress curve 110.And then, when the rotating speed of main frame 20 is greater than dangerous rotary speed area, so that becoming minimum mode, the aperture of variable-nozzle 32 carries out control, and therefore torsional vibration stress recovery initial value, passes along the first torsional vibration stress curve 109.Like this, according to the control that reduces control gear 50 from torsional vibration stress, can in dangerous rotary speed area, (in the region that torsional vibration stress originally can uprise) reduce torsional vibration stress.
In addition, illustrate that with reference to Fig. 5 and Fig. 6 torsional vibration stress reduces control gear 50 and controls the situation of variable-nozzle 32 above, but only controlled the situation of bypass valve 35 and control variable-nozzle 32 and both situations of bypass valve 35 also can obtain same result simultaneously.Again, even if the valve that bypass valve 35 is regulation type also because become standard-sized sheet, so there is not the situation different because of the kind result of valve in the time that the rotating speed of main frame 20 enters dangerous rotary speed area.Like this, the control that reduces control gear 50 from the torsional vibration stress of this example, only by regulating the aperture of variable-nozzle 32, bypass valve 35 etc. just can make torsional vibration stress reduce, therefore can be described as very easily and controls.In addition, in order to realize stable control in variable-nozzle, regulation type valve etc., also can periodically or gently and continuously change the nozzle/valve regulation under dangerous rotating speed.
As above, reduce control gear 50 according to the torsional vibration stress of this example, can in the higher region of original torsional vibration stress, reduce torsional vibration stress, even therefore for example torsional vibration stress exceedes the such Propulsion Systems 10 of the second dangerous curve 103, also can not change Propulsion Systems 10 construction element be applied in boats and ships 100.Again, comparison diagram 6 and Fig. 2 are known, can dwindle the scope of forbidding scope according to the control of torsional vibration stress reduction control gear 50, make to use more efficiently to become possibility.Again, reducing control gear 50 according to the torsional vibration stress of this example is to reduce Torsional Vibration Control stress from control plane, therefore does not need to change the construction element of Propulsion Systems 10.
Above, the boats and ships 100 according to example of the present invention have been described, but concrete structure is not limited to these examples, the change of design without departing from the spirit and scope of the invention etc. is also contained in the present invention.For example, in above-mentioned example, reduce the pressure of exhaust 27 in order to reduce scavenging pressure, but the angle that also can be arranged at the guide blades of the entrance of compressor 33 by adjusting reduces scavenging pressure.Again, the scavenging bypass valve that the scavenging of supplying with from pressurized machine to main frame is detoured also can be set at compressor outlet place, and by regulating this scavenging bypass valve to reduce scavenging pressure.
Again, in above-mentioned example, illustrated that arranged in series torsional vibration stress reduces the situation of control gear 50 and scavenging pressure control gear 40, but also can be formed as they configurations in parallel, and from stream oriented device directly to the structure of the transmitted signals such as variable-nozzle 32, bypass valve 35.
Industrial applicability:
Send torsional vibration stress to reduce control gear can to reduce torsional vibration stress by easy control according to according to the present invention, therefore in the technical field of boats and ships etc., benefit.
Symbol description:
10 Propulsion Systems;
11 propeller cavitations;
20 main frames;
24 scavengings;
27 exhausts;
30 pressurized machines;
31 turbines;
32 variable-nozzles;
33 compressors;
34 exhaust passageways;
35 bypass valve;
50 torsional vibration stress reduce control gear;
100 boats and ships.
Claims (9)
1. a torsional vibration stress reduces control gear, be for reducing possess with the Propulsion Systems that advances the propeller cavitation of use to rotate integratedly, drive the main frame of this Propulsion Systems and there is the turbine of the exhaust gas drive of being discharged from this main frame and using the rotating force of this turbine as the new gas of powered compressor and the torsional vibration stress that scavenging is supplied to the torsional vibration stress that the described Propulsion Systems in the boats and ships of pressurized machine of described main frame produces reduce control gear
Be formed as described torsional vibration stress and be specified value when above, reduce the structure of the pressure of described scavenging.
2. torsional vibration stress according to claim 1 reduces control gear, it is characterized in that, the reduction of the pressure of described scavenging drives the pressure of the described exhaust of the turbine of described pressurized machine to carry out by reduction.
3. torsional vibration stress according to claim 2 reduces control gear, it is characterized in that, described pressurized machine has and will guide to the exhaust passageway of described turbine and be arranged at the bypass valve this exhaust passageway from the exhaust of described main frame discharge;
The reduction of the pressure of described exhaust is undertaken by open described bypass valve.
4. torsional vibration stress according to claim 2 reduces control gear, it is characterized in that, described pressurized machine has variable-nozzle at the leading portion of described turbine;
The reduction of the pressure of described exhaust is undertaken by the aperture that changes described variable-nozzle.
5. torsional vibration stress according to claim 1 reduces control gear, it is characterized in that, also possesses the scavenging bypass valve that the scavenging of supplying with to described main frame from described pressurized machine is detoured;
The reduction of the pressure of described scavenging is by regulating described scavenging bypass valve to carry out.
6. reduce control gear according to the torsional vibration stress described in any one in claim 1 to 4, it is characterized in that, judge by the rotating speed of described main frame whether described torsional vibration stress is more than specified value.
7. reduce control gear according to the torsional vibration stress described in any one in claim 1 to 4, it is characterized in that, judge by measuring torsional vibration stress whether described torsional vibration stress is more than specified value.
8. boats and ships, possess according to the torsional vibration stress described in any one in claim 1 to 7 and reduce control gear.
9. a torsional vibration stress reduction method, for reducing possessing with the Propulsion Systems that advances the propeller cavitation of use to rotate integratedly, drive the main frame of this Propulsion Systems and there is the turbine of the exhaust gas drive of being discharged from this main frame and using the rotating force of this turbine as the new gas of powered compressor and scavenging is supplied to the torsional vibration stress reduction method of the torsional vibration stress that the described Propulsion Systems in the boats and ships of pressurized machine of described main frame produces
Judge whether described torsional vibration stress is more than specified value, when judging that described torsional vibration stress is the function that specified value reduces described pressurized machine when above.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-275629 | 2011-12-16 | ||
| JP2011275629A JP5795731B2 (en) | 2011-12-16 | 2011-12-16 | Torsional vibration stress reduction control device, ship equipped with the same, and torsional vibration stress reduction method |
| PCT/JP2012/007328 WO2013088643A1 (en) | 2011-12-16 | 2012-11-15 | Torsional vibration stress reduction control device, marine vessel comprising same, and torsional vibration stress reduction method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103917764A true CN103917764A (en) | 2014-07-09 |
Family
ID=48612123
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280055865.7A Pending CN103917764A (en) | 2011-12-16 | 2012-11-15 | Torsional vibration stress reduction control device, marine vessel comprising same, and torsional vibration stress reduction method |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5795731B2 (en) |
| KR (1) | KR20140075811A (en) |
| CN (1) | CN103917764A (en) |
| WO (1) | WO2013088643A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105468046A (en) * | 2016-01-08 | 2016-04-06 | 中国船舶重工集团公司第七0四研究所 | Multi-power branch local vibration control method for ship main propulsion system |
| CN109983210A (en) * | 2016-11-30 | 2019-07-05 | 三菱重工业株式会社 | Marine diesel engine |
| CN110312856A (en) * | 2017-02-24 | 2019-10-08 | 三菱重工业株式会社 | Marine diesel engine, engine control system and method |
| CN111836955A (en) * | 2018-03-16 | 2020-10-27 | 株式会社 Ihi | Engine for ship |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03273998A (en) * | 1990-03-23 | 1991-12-05 | Sanshin Ind Co Ltd | Ship propulsion machine |
| WO1994029585A1 (en) * | 1993-06-04 | 1994-12-22 | Man B & W Diesel A/S | A method of diminishing extra stresses from torsional vibrations in a main shaft for a large two-stroke diesel engine |
| JP3004307B2 (en) * | 1990-03-23 | 2000-01-31 | 三菱重工業株式会社 | Diesel engine crankshaft torsional vibration suppressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0639072Y2 (en) * | 1985-02-25 | 1994-10-12 | 三菱重工業株式会社 | Device for avoiding dangerous speed range |
-
2011
- 2011-12-16 JP JP2011275629A patent/JP5795731B2/en not_active Expired - Fee Related
-
2012
- 2012-11-15 KR KR1020147014635A patent/KR20140075811A/en active Search and Examination
- 2012-11-15 CN CN201280055865.7A patent/CN103917764A/en active Pending
- 2012-11-15 WO PCT/JP2012/007328 patent/WO2013088643A1/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03273998A (en) * | 1990-03-23 | 1991-12-05 | Sanshin Ind Co Ltd | Ship propulsion machine |
| JP3004307B2 (en) * | 1990-03-23 | 2000-01-31 | 三菱重工業株式会社 | Diesel engine crankshaft torsional vibration suppressor |
| WO1994029585A1 (en) * | 1993-06-04 | 1994-12-22 | Man B & W Diesel A/S | A method of diminishing extra stresses from torsional vibrations in a main shaft for a large two-stroke diesel engine |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105468046A (en) * | 2016-01-08 | 2016-04-06 | 中国船舶重工集团公司第七0四研究所 | Multi-power branch local vibration control method for ship main propulsion system |
| CN109983210A (en) * | 2016-11-30 | 2019-07-05 | 三菱重工业株式会社 | Marine diesel engine |
| CN110312856A (en) * | 2017-02-24 | 2019-10-08 | 三菱重工业株式会社 | Marine diesel engine, engine control system and method |
| CN110312856B (en) * | 2017-02-24 | 2021-12-07 | 三菱重工业株式会社 | Marine diesel engine, engine control device, and method |
| CN111836955A (en) * | 2018-03-16 | 2020-10-27 | 株式会社 Ihi | Engine for ship |
| CN111836955B (en) * | 2018-03-16 | 2022-12-06 | 株式会社 Ihi | Engine for ship |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013124652A (en) | 2013-06-24 |
| WO2013088643A1 (en) | 2013-06-20 |
| JP5795731B2 (en) | 2015-10-14 |
| KR20140075811A (en) | 2014-06-19 |
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Application publication date: 20140709 |