CN105275649A - Method for operating an internal combustion engine and engine control unit - Google Patents
Method for operating an internal combustion engine and engine control unit Download PDFInfo
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- CN105275649A CN105275649A CN201510303023.4A CN201510303023A CN105275649A CN 105275649 A CN105275649 A CN 105275649A CN 201510303023 A CN201510303023 A CN 201510303023A CN 105275649 A CN105275649 A CN 105275649A
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- sparger
- independent
- pressure
- injection rate
- hydraulic pressure
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Classifications
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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
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
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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
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
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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
- F02D41/221—Safety or indicating devices for abnormal conditions relating to the failure of actuators or electrically driven elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/005—Fuel-injectors combined or associated with other devices the devices being sensors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
- F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L23/00—Devices or apparatus for measuring or indicating or recording rapid changes, such as oscillations, in the pressure of steam, gas, or liquid; Indicators for determining work or energy of steam, internal-combustion, or other fluid-pressure engines from the condition of the working fluid
- G01L23/22—Devices or apparatus for measuring or indicating or recording rapid changes, such as oscillations, in the pressure of steam, gas, or liquid; Indicators for determining work or energy of steam, internal-combustion, or other fluid-pressure engines from the condition of the working fluid for detecting or indicating knocks in internal-combustion engines; Units comprising pressure-sensitive members combined with ignitors for firing internal-combustion engines
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L23/00—Devices or apparatus for measuring or indicating or recording rapid changes, such as oscillations, in the pressure of steam, gas, or liquid; Indicators for determining work or energy of steam, internal-combustion, or other fluid-pressure engines from the condition of the working fluid
- G01L23/26—Details or accessories
- G01L23/32—Apparatus specially adapted for recording pressure changes measured by indicators
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M15/00—Testing of engines
- G01M15/04—Testing internal-combustion engines
- G01M15/08—Testing internal-combustion engines by monitoring pressure in cylinders
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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
- F02D2041/224—Diagnosis of the fuel system
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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
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D2041/3881—Common rail control systems with multiple common rails, e.g. one rail per cylinder bank, or a high pressure rail and a low pressure rail
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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
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0602—Fuel pressure
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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
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0614—Actual fuel mass or fuel injection amount
- F02D2200/0616—Actual fuel mass or fuel injection amount determined by estimation
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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
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0618—Actual fuel injection timing or delay, e.g. determined from fuel pressure drop
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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
- F02D41/008—Controlling each cylinder individually
- F02D41/0085—Balancing of cylinder outputs, e.g. speed, torque or air-fuel ratio
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/24—Fuel-injection apparatus with sensors
- F02M2200/247—Pressure sensors
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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
- Y02T10/40—Engine management systems
Abstract
The present invention relates to a method for operating an internal combustion engine and an engine control unit, and particularly, a method for operating a marine diesel oil engine, and particularly operating the marine diesel oil engine employing heavy fuel oil. The fuel is injected to an air cylinder of a marine diesel oil engine by utilizing a fuel supply system, and particularly an injector (1) of a co-orbiting fuel supply system. The pressure signal is separately detected on the injector (1) directly through the measuring for each injector (1) with the help of a pressure sensor (15) allocated to the injector (1). At least one characteristic and/or injecting rate and/or injecting amount of hydraulic pressure needle stroke timing is separately determined according to the single pressure signal of each injector (1).
Description
Technical field
The present invention relates to a kind of method of the marine diesel engine for operating preamble according to claim 1 and the control unit of engine for implementing described method.
Background technique
Figure 1A and Figure 1B shows the essential structure of the common rail road fuel supply system according to the known marine diesel engine of prior art.This structure is known according to DE10157135B4.Therefore, the common rail road fuel supply system of Figure 1A and Figure 1B includes at least one sparger (Figure 1A: pressure controlled injection valve, Figure 1B are the reservoir sparger that stroke controls) 1 for each cylinder.Via sparger 1, fuel can be ejected in each cylinder.In addition, common rail road fuel supply system comprises at least one low pressure pump 5, at least one high-pressure service pump 2 and has the pumping installations 3 of high-pressure service pump reservoir 8, so that fuel is sent to its high-pressure area 6 from the area of low pressure 4 of common rail road fuel supply system, wherein, in high-pressure area 6 between pumping installations 3 and sparger 1, provide the pressure reservoir 7 be for good and all under high pressure.The pressure reservoir 7(be for good and all under high pressure is called common rail road) comprise multiple storage unit 9.Storage unit 9 is connected to pumping installations 3 and connects via the high pressure line 10 be for good and all under high pressure between it.
Figure 1A: in addition, pressure reservoir 7, that is, storage unit 9, via based on spraying cycle, the high pressure line 11 be sometimes under high pressure is connected to sparger.Sometimes the high pressure line 11 being connected to storage unit 9 under being in high pressure based on spraying cycle, by sparger 1 has been assigned with the switching valve 12 supplying fuel to sparger 1 based on spraying cycle.One in the storage unit 9 of pressure reservoir 7 has been assigned with pressure-limit valve 13 and purge valve 14.
Figure 1B: pressure reservoir 7, that is, storage unit 9 and sparger 1, also connect via the high pressure line 11 be for good and all under high pressure.In the sparger 1 be for good and all under high pressure, switching valve 12 is integrated, thus is reduced pressure Jet control room 21 according to spraying cycle, to trigger injection.One in the storage unit 9 of pressure reservoir 7 has been assigned with pressure-limit valve 13 and purge valve 14.
In order to accurately control or regulate the operation of this marine diesel engine, importantly always accurately determine the so-called injection rate of sparger in the operation period of explosive motor or spray quantity.In this respect, up to the present only it is known that distribute injector needle stroke sensor, under it helps, can monitor and assess the mechanical strokes of the pin of sparger, thus determine the injection rate of sparger by this way and/or spray quantity.But using on the injector and install pin stroke sensor and relate to great efforts and high cost, therefore, is not practicable well for serial application.In addition, the life-span of pin stroke sensor depends on the operating conditions of explosive motor.In particular, when the marine diesel engine operated when utilizing heavy fuel oil, the life-span of pin stroke sensor is extremely restricted.
Summary of the invention
Therefore, need for operating the method for marine diesel engine and the control unit of engine for implementing described method, its help under, can like a dream, at low cost and easily and reliably determine in particular marine diesel engine sparger injection rate and/or spray quantity.From then on starting, the present invention is based on the object of the novel method created for operating marine diesel engine.This object is solved by method according to claim 1.According to the present invention, detected pressures signal is carried out by directly measuring sparger to each sparger individually under the help of pressure transducer distributing to sparger, wherein, according to the pressure signal that each sparger for each sparger is independent, determine at least one feature and/or the injection rate of hydraulic pressure pin stroke timing individually and/or spray quantity.
The pressure signal that the object of the invention is to measure sparger independent by the sparger of the fuel supply system to marine diesel engine detects.According to the pressure signal that sparger is independent, at least one independent feature of each sparger determination hydraulic pressure pin stroke timing and/or the independent injection rate of sparger and/or the independent injection quantity of sparger.Fully can omit the use of pin stroke sensor.Determine under the help of pressure transducer pressure signal for the marine diesel engine utilizing heavy fuel oil to operate also be easily, cost-saving ground and reliably feasible.According to the pressure signal that sparger is independent, easily and reliably can determine the parameter of described or each expectation, i.e. described or each feature of injection rate and/or injection quantity and/or the timing of hydraulic pressure stroke.
Preferably, each sparger has independent sparger reservoir volume, wherein, under the help of the pressure transducer for each sparger, as independent pressure signal, the reservoir pressure signal of corresponding sparger reservoir volume detects by measuring, wherein, according to the reservoir pressure signal that each sparger for each sparger is independent, determine described or each feature of injection rate and/or injection quantity and/or hydraulic pressure pin/timing individually.
In particular when the reservoir pressure signal of the sparger reservoir volume of respective injectors is confirmed as the pressure signal of respective injectors, can especially advantageously determine injection rate according to pressure signal and/or spray described in quantity and/or the timing of hydraulic pressure pin stroke or each feature.The independent reservoir pressure signal of sparger is not by the impact that the miscellaneous part of fuel supply system affects, thus especially accurately and reliably can determine at least one in above parameter subsequently, that is, described or each feature of injection rate and/or injection quantity and/or the timing of hydraulic pressure stroke.
According to other favourable improvement, by measuring the independent pressure signal of the sparger that detects according to time differentiate or differential, wherein, according to the pressure signal that the sparger of differential is independent, determine the injection rate of respective injectors and/or spray described or each feature of quantity and/or the timing of hydraulic pressure pin stroke.For determine injection rate and/or spray described in quantity and/or the timing of hydraulic pressure pin stroke or this assessment of the pressure signal of each feature due to reliable, easy and accurate but especially preferred.
Preferably, determine the injection rate of respective injectors from the pressure signal that the sparger of differential is independent according to equation below:
dm/dt=V*(dp/dt)/c(p)
2
Wherein, dm/dt is injection rate, and wherein, V is independent sparger reservoir volume, and wherein, dp/dt carries out the independent pressure signal of the sparger of differential according to time t, and wherein, c (p) is the velocity of sound depending on the pressure p that sparger is independent.This of the injection rate of respective injectors is determined to be easy to, reliably and accurate.
Preferably, the beginning of injection and/or hydraulic pressure maximum stroke reach and/or the end left and/or spray of hydraulic pressure maximum stroke is determined individually according to the pressure signal independent for the sparger of each sparger of the feature of the hydraulic pressure pin stroke timing as the spraying cycle for respective injectors.
Noted here, the timing of hydraulic pressure pin stroke is different from the timing of mechanical needle stroke.
Therefore, the throttle effect of needle stand that hydraulic pressure maximum stroke corresponds to sparger is equal to or less than the pin stroke during throttle effect of the nozzle bore of respective injectors or spray-hole.From now, the through-flow maintenance of hydraulic pressure nozzle of the nozzle of sparger is constant, and mechanical maximum stroke can continue to rise.
Other differences between the timing of mechanical needle stroke and the timing of hydraulic pressure pin stroke comprise: when leaving hydraulic pressure maximum stroke, and the through-flow reduction of nozzle of sparger, that is, the throttle effect of the needle stand of respective injectors is greater than the throttle effect of nozzle bore.By contrast, the machinery of mechanical maximum stroke leaves and usually occurs in advance.
Accompanying drawing explanation
Of the present invention preferably progress further obtains from dependent claims and following description.Exemplary embodiment of the present invention is explained in more detail under accompanying drawing helps, but is not limited to this.Illustrate:
Figure 1A: schematically showing of common rail road fuel supply system, it has the pressure controlled injection valve (sparger 1) together with control unit of engine of explosive motor;
Figure 1B: schematically showing of common rail road fuel supply system, the reservoir sparger (sparger 1) that its stroke together with control unit of engine with explosive motor controls;
Fig. 2: for illustrating the first figure according to the method for operating marine diesel engine of the present invention;
Fig. 3: for illustrating the second figure of other examples according to the method for operating marine diesel engine of the present invention; And
Fig. 4: for illustrating the 3rd figure of other examples according to the method for operating marine diesel engine of the present invention.
Embodiment
The present invention relates to the method for operating the marine diesel engine that marine diesel engine especially utilizes heavy fuel oil to operate, wherein, such marine diesel engine comprises the fuel supply system being preferably designed to be common rail road fuel supply system.The essential structure of such common rail road fuel supply system of marine diesel engine has been described with reference to Figure 1A and Figure 1B.Therefore, with reference to the above explanation about Figure 1A and Figure 1B.Here, for the sake of completeness, only explain again: the such fuel supply system for each cylinder comprises at least one sparger 1, and wherein, via sparger 1, fuel can be injected in the cylinder of marine diesel engine.
According to Figure 1A and Figure 1B, each sparger 1 has been assigned with pressure transducer 15.Under the help of pressure transducer 15, by directly carrying out detecting separately for the pressure signal of each sparger 1 according to measurement of the present invention to sparger 1.
Preferably, each sparger 1 comprises independent sparger reservoir volume (not shown), wherein, be independent pressure signal for each sparger 1 by the reservoir pressure input of the respective injectors reservoir volume of respective injectors 1 by measuring under the help of pressure transducer 15 subsequently.
According to the present invention, at least one feature of the hydraulic pressure pin stroke timing of the injection rate of respective injectors 1 and/or the injection quantity of respective injectors 1 and/or respective injectors 1 is also determined individually according to the pressure signal that each sparger being used for each sparger 1 is independent, wherein, as the feature of hydraulic pressure pin stroke timing, the beginning of injection and/or hydraulic pressure maximum stroke reach and/or the end left and/or spray of hydraulic pressure maximum stroke is determined.
Noted here, the timing of hydraulic pressure pin stroke is different from the timing of mechanical needle stroke.Therefore, hydraulic pressure maximum stroke is that the pin stroke when the throttle effect of the needle stand of respective injectors 1 is equal to or less than the throttle effect of the nozzle bore of respective injectors 1 or spray-hole is issued to, and wherein, when this pin stroke, hydraulic pressure nozzle is through-flow is constant.By contrast, mechanical maximum stroke can rise relative to hydraulic pressure maximum stroke further.In particular when the throttle effect of the needle stand of respective injectors is greater than the throttle effect of the nozzle bore of respective injectors, leave hydraulic pressure maximum stroke, wherein, mechanical maximum stroke was left usually before hydraulic pressure maximum stroke.
Preferably, by measuring the independent pressure signal reservoir pressure signal that preferably sparger is independent of the sparger that detects according to time t differentiate or differential, wherein, according to the pressure signal that the sparger of differential is independent, determine the injection rate of respective injectors and/or spray described or each feature of quantity and/or the timing of hydraulic pressure pin stroke.According to the pressure signal (it is preferably the reservoir pressure signal of differential) that the sparger of differential is independent, preferably determine the injection rate of respective injectors according to equation below:
dm/dt=V*(dp/dt)/c(p)
2
Wherein, dm/dt is injection rate, and wherein, V is independent sparger reservoir volume, and wherein, dp/dt carries out the independent pressure signal of the sparger of differential according to time t, and wherein, c (p) is the velocity of sound depending on the pressure p that sparger is independent.
Depend on that preferably feature based or characteristic pattern are determined according to the pressure that measured sparger is independent in this case for the velocity of sound of pressure.
According to the injection rate determined above, the injection rate of respective injectors 1 can be determined by its integration in time.
Fig. 2 shows two bars curves 20,21 in time, and wherein, signal curve 20 is pressure signals independent to the sparger measured by sparger 1 under the help of pressure transducer 15, the reservoir pressure signal that namely sparger is independent.Signal curve 21 is time-derivative or the time diffusion of the pressure signal of this measurement.
As explained above, the injection rate separately for respective injectors 1 preferably utilizes above-mentioned formula to calculate according to the pressure signal 21 that the sparger of differential is independent, and wherein, in the diagram, the injection rate calculated is represented by signal curve 22.By comparing with the signal curve 23 corresponding to measured injection rate, being apparent that, under the help of method according to the present invention, reliably and accurately can determining the injection rate of sparger 1.In the diagram, signal curve 24 shows the injection rate of the respective injectors calculated from signal curve 22 by integration in time.
In addition, as obvious from Fig. 2, can according to the independent pressure signal of the sparger of differential easily and reliably determine at least one feature of the hydraulic pressure pin stroke timing of respective injectors.Therefore, time t1 corresponds to the beginning of spraying, and time t4 corresponds to the end of the injection of spraying cycle.At time t2, reach hydraulic pressure maximum stroke, and at time t3, leave hydraulic pressure maximum stroke.
According to these features, can calculate the pin stroke signal of the pin of respective injectors 1 according to the signal curve 25 of Fig. 3, wherein, the time t1 to t4 of Fig. 3 corresponds to the time t1 to t4 of Fig. 2.Therefore, time t1 corresponds to the beginning of spraying, and at time t2, reaches hydraulic pressure maximum stroke, at time t3, leaves hydraulic pressure maximum stroke, wherein, at time t4, reach the end of injection.
In figure 3, the pin stroke signal 25 calculated compares by measuring the pin stroke signal 26 detected with under the help of pin stroke sensor, wherein, obvious from signal curve 25 and 26, the pin stroke signal calculated demonstrates and good agreement by measuring the pin stroke signal detected.
Under help of the present invention, can the operation period of marine diesel engine easily and reliably determine at least one feature of the hydraulic pressure pin stroke timing of the injection rate of sparger and/or the injection quantity of sparger and/or sparger.
Based at least one in the determined above parameter of the pressure signal independent from sparger, the functional diagnosis for respective injectors 1 and/or wear-out diagnosis can be implemented.Therefore, the wearing and tearing of sparger 1 can be inferred according to the injection rate of time dependent sparger 1, to start component maintenance or parts replacement subsequently in time.Utilize according to method of the present invention, this can occur during the normal operation of marine diesel engine, thus the functional check can correspondingly omitted independent measurement test bench or abrasion inspection.
Under the help of method according to the present invention, such as, for each cylinder, accurately can determine injection rate individually or spray quantity.By means of this, the control that the cylinder of the operation of explosive motor is independent is possible subsequently.In particular, the method is suitable for the marine diesel engine for utilizing heavy fuel oil to operate.
In addition, the present invention relates to the control unit of engine 16 for implementing described method.Figure 1A and Figure 1B shows the control unit of engine 16 comprising means (instrument) 17,18,19 for implementing described method.Means 17 are at least one data-interfaces, thus exchange data with pressure transducer 15 in particular, namely read the pressure measurement signal can made by pressure transducer 15.Means 18 are hardware means, and means 19 are the software approach for implementing according to method of the present invention.In particular, hardware means 18 is the data memory unit for storing data and the data processing system for the treatment of data.Software approach 19 is the program modules for implementing according to method of the present invention.
Under method according to the present invention and the help according to control unit of engine 16 of the present invention, can during the normal operation of the marine diesel engine especially utilizing heavy fuel oil to operate easily and reliably and automatically determine the injection rate of respective injectors 1 and/or spray at least one feature of quantity and/or the timing of hydraulic pressure pin stroke.For this reason, only to need in above-described mode directly to assess it the independent reservoir volume detected pressures measurement signal of sparger in particular respective injectors 1.
The list of reference character
1 sparger
2 high-pressure service pumps
3 pumping installations
4 areas of low pressure
5 low pressure pumps
6 high-pressure areas
7 pressure reservoir
8 high-pressure service pump reservoirs
9 storage units
10 high pressure lines
11 high pressure lines
12 switching valves
13 pressure-limit valves
14 purge valves
15 pressure transducers
16 control unit of engine
17 interfaces
18 hardware means
19 software approach
20 signal curves
21 signal curves
22 signal curves
23 signal curves
24 signal curves
25 signal curves
26 signal curves.
Claims (9)
1. one kind for operating the method for the marine diesel engine that marine diesel engine utilizes heavy fuel oil to operate in particular, wherein, utilize the sparger (1) of fuel supply system common rail road fuel supply system in particular, fuel is injected in the cylinder of marine diesel engine, it is characterized in that, under the help of pressure transducer (15) distributing to described sparger (1), come directly at the upper detected pressures signal of described sparger (1) by carrying out measurement individually to each sparger (1), and according to the pressure signal that each sparger for each sparger (1) is independent, determine at least one feature and/or the injection rate of hydraulic pressure pin stroke timing individually and/or spray quantity.
2. method according to claim 1, it is characterized in that, each sparger (1) has independent sparger reservoir volume, wherein, under the help of the pressure transducer (15) for each sparger (1), as independent pressure signal, the reservoir pressure signal of corresponding sparger reservoir volume detects by measuring, and according to the reservoir pressure signal that each sparger for each sparger (1) is independent, determine described or each feature of described hydraulic pressure pin stroke timing and/or described injection rate and/or described injection quantity individually.
3. method according to claim 1 and 2, it is characterized in that, by measuring the independent pressure signal of the described sparger that detects according to time differentiate or differential, and according to the pressure signal that the sparger of differential is independent, determine described or each feature of the described hydraulic pressure pin stroke timing of respective injectors and/or described injection rate and/or described injection quantity.
4. method according to claim 3, is characterized in that, according to the pressure signal that the sparger of differential is independent, determines the described injection rate of described respective injectors according to equation below:
dm/dt=V*(dp/dt)/c(p)
2
Wherein, dm/dt is injection rate, wherein, V is independent sparger reservoir volume, and wherein, dp/dt carries out the independent pressure signal of the described sparger of differential according to time t, wherein, c (p) is the velocity of sound depending on the pressure p that described sparger is independent.
5. method according to claim 4, is characterized in that, the described velocity of sound is determined according to the feature or characteristic pattern that depend on the pressure that measured sparger is independent.
6. the method according to claim 4 or 5, is characterized in that, the described injection rate of described respective injectors is determined by described injection rate integration in time.
7. the method according to any one in claim 1 to 6, it is characterized in that, according to the pressure signal that the described sparger for each sparger (1) is independent, by the beginning of injection and/or described hydraulic pressure maximum stroke reach and/or the end left and/or spray of described hydraulic pressure maximum stroke is defined as the feature of the described hydraulic pressure pin stroke timing of the spraying cycle for described respective injectors (1) individually.
8. the method according to any one in claim 1 to 7, it is characterized in that, based on described in the timing of described hydraulic pressure pin stroke or each feature and/or described injection rate and/or described injection quantity, implement the functional diagnosis inspection and/or the wear-out diagnosis that are used for each respective injectors (1).
9. the control unit of engine (16) of the marine diesel engine marine diesel engine that utilizes heavy fuel oil to operate in particular, wherein, explosive motor comprises fuel supply system, be common rail road fuel supply system in particular, it is characterized in that, described control unit of engine (16) comprises the instrument (17,18,19) for implementing the method according to any one in claim 1 to 8.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014007963.5 | 2014-06-04 | ||
| DE102014007963.5A DE102014007963A1 (en) | 2014-06-04 | 2014-06-04 | Method for operating an internal combustion engine and engine control unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105275649A true CN105275649A (en) | 2016-01-27 |
| CN105275649B CN105275649B (en) | 2021-01-15 |
Family
ID=54705935
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510303023.4A Active CN105275649B (en) | 2014-06-04 | 2015-06-04 | Method for operating an internal combustion engine and engine control unit |
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| JP (1) | JP6522423B2 (en) |
| KR (1) | KR102184034B1 (en) |
| CN (1) | CN105275649B (en) |
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| FI (1) | FI129818B (en) |
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| CN109072804A (en) * | 2016-05-12 | 2018-12-21 | 罗伯特·博世有限公司 | Method for the error diagnostics in internal combustion engine |
| CN111065808A (en) * | 2017-08-29 | 2020-04-24 | 维特思科科技有限责任公司 | Method and device for determining the injection quantity or injection rate of a fluid injected into a reaction space by means of an injector |
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| DE102018104848B3 (en) | 2018-03-02 | 2019-07-04 | Mtu Friedrichshafen Gmbh | Distribution device of a common rail system |
| CN108757254B (en) * | 2018-06-28 | 2024-03-15 | 武汉理工大学 | Marine heavy oil fuel injection system test bed |
| DE102020101102A1 (en) * | 2020-01-17 | 2021-07-22 | Bayerische Motoren Werke Aktiengesellschaft | Procedure for checking the functionality of an injector |
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Also Published As
| Publication number | Publication date |
|---|---|
| KR102184034B1 (en) | 2020-11-27 |
| CN105275649B (en) | 2021-01-15 |
| DE102014007963A1 (en) | 2015-12-17 |
| FI129818B (en) | 2022-09-15 |
| JP2015230004A (en) | 2015-12-21 |
| KR20150139771A (en) | 2015-12-14 |
| JP6522423B2 (en) | 2019-05-29 |
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