WO2019167708A1 - 舶用流体ポンプおよびその制御方法 - Google Patents

舶用流体ポンプおよびその制御方法 Download PDF

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Publication number
WO2019167708A1
WO2019167708A1 PCT/JP2019/005958 JP2019005958W WO2019167708A1 WO 2019167708 A1 WO2019167708 A1 WO 2019167708A1 JP 2019005958 W JP2019005958 W JP 2019005958W WO 2019167708 A1 WO2019167708 A1 WO 2019167708A1
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WO
WIPO (PCT)
Prior art keywords
time
valve
piston
fluid
movement amount
Prior art date
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PCT/JP2019/005958
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English (en)
French (fr)
Japanese (ja)
Inventor
泰 柿元
基輝 和泉
Original Assignee
株式会社ジャパンエンジンコーポレーション
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Application filed by 株式会社ジャパンエンジンコーポレーション filed Critical 株式会社ジャパンエンジンコーポレーション
Priority to KR1020207024036A priority Critical patent/KR102316904B1/ko
Priority to CN201980016089.1A priority patent/CN111788381B/zh
Publication of WO2019167708A1 publication Critical patent/WO2019167708A1/ja

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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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/025—Hydraulically actuated valves draining the chamber to release the closing pressure
    • 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
    • B63H21/12—Use of propulsion power plant or units on vessels the vessels being motor-driven
    • B63H21/14—Use of propulsion power plant or units on vessels the vessels being motor-driven relating to internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/12—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with non-fuel substances or with anti-knock agents, e.g. with anti-knock fuel
    • 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
    • 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
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber

Definitions

  • the present invention relates to a marine fluid pump and a control method thereof.
  • a marine fluid pump for discharging a fluid such as fuel or water is applied to a marine diesel engine mounted on a marine vessel.
  • a fuel injection pump that pumps fuel to be injected into a cylinder to a fuel injection valve, and water is injected into a fuel flow passage from a discharge port of the fuel injection pump to a fuel injection valve injection port through a pipe.
  • Examples include water injection pumps.
  • Patent Document 1 describes a fuel injection pump that is driven and controlled by hydraulic fluid supplied via an electromagnetic valve.
  • a marine fluid pump in general, includes a piston in a state where the piston can reciprocate in the longitudinal direction, and pressurizes the fluid by moving the piston using the pressure of hydraulic oil supplied through a control valve. To discharge.
  • the amount of fluid discharged by such a marine fluid pump changes in accordance with the amount of movement of the piston when the fluid is pressurized and discharged. For this reason, in a marine fluid pump, the movement amount of the piston is accurately controlled from the viewpoint of ensuring the accuracy required for the fluid discharge amount (for example, the fuel injection amount or water injection amount in a marine diesel engine). Is desired.
  • an opening adjustment type electromagnetic valve such as a servo valve or a proportional valve that can control the amount of hydraulic oil supplied with high accuracy by adjusting the opening.
  • a control valve for a marine fluid pump Is used as a control valve for a marine fluid pump.
  • an opening adjustment type electromagnetic valve is used as a control valve, generally, an actual measurement value of the piston movement amount is frequently measured during the fluid discharge period, and each time an actual measurement value of the piston movement amount is obtained. Since it is necessary to reflect the deviation from the target value in the adjustment of the opening degree of the control valve, the device configuration for accurately controlling the movement amount of the piston may be complicated, and the cost of the device may be expensive.
  • the opening adjustment type solenoid valve is often vulnerable to foreign matter, and foreign matter is likely to be mixed in the environment where marine diesel engines operate. Solenoid valves may not be suitable.
  • the present invention has been made in view of the above circumstances, and is a marine fluid pump capable of accurately controlling the movement amount of a piston when pressurizing and discharging a fluid while suppressing an increase in cost.
  • An object is to provide a control method thereof.
  • a marine fluid pump includes a pump body that pressurizes and discharges fluid by moving a piston using the pressure of hydraulic oil, A detection unit that detects the maximum movement amount of the piston in one discharge of the fluid, and an on state in which the hydraulic oil is supplied to the pump body and an off state in which the supply of the hydraulic oil is stopped are alternatively switched.
  • the target movement amount of the piston is derived according to the control valve and the discharge amount of the fluid required for one discharge of the fluid, and the target movement amount derived at the time of the current discharge of the fluid and the previous time Based on the difference from the maximum amount of movement detected at the time of discharge, a time correction value of a valve on time, which is a time for turning on the control valve, is calculated, and the calculated time correction value is calculated.
  • the valve on-time is corrected at the time of output, characterized in that it comprises a control unit for controlling the control valve so as to continue said valve on-time after correction becomes the ON state.
  • the control unit derives a valve on basic time that is a valve on time of the control valve set according to the target movement amount of the piston.
  • the valve on time during the current discharge of the fluid is corrected so as to be the sum of the valve on basic time and the time correction value.
  • the marine fluid pump according to the present invention is the marine fluid pump according to the above invention, wherein the control unit has a data table indicating a correlation between the target movement amount of the piston and the valve on basic time of the control valve, The basic valve-on time correlated with the target movement amount derived at the time of fluid discharge is derived based on the data table.
  • the marine fluid pump control method includes the pump body via a control valve that selectively switches between an on state in which hydraulic oil is supplied to the pump body and an off state in which the supply of the hydraulic oil is stopped.
  • a target movement amount deriving step for deriving a target movement amount of the piston in accordance with a discharge amount of the fluid required by the discharge of the piston, and the target movement amount of the piston by the target movement amount deriving step and the previous time of the fluid
  • a time correction value calculation step for calculating a time correction value of a valve on time that is a time for which the control valve is in the on state.
  • a correction step for correcting the valve on time at the time of the current discharge of the fluid taking into account the time correction value by the time correction value calculation step, and the valve on time after correction is continued.
  • a control step of controlling the control valve so as to be in an on state.
  • the marine fluid pump control method is the above-described invention, wherein the correction step is a valve on basic time which is a valve on time of the control valve set according to the target movement amount of the piston. And the valve on time at the time of the current discharge of the fluid is corrected so as to be the sum of the valve on basic time and the time correction value.
  • the correction step is based on a data table indicating a correlation between the target movement amount of the piston and the valve-on basic time of the control valve. Then, the valve-on basic time correlated with the target movement amount in the target movement amount derivation step is derived.
  • FIG. 1 is a schematic diagram showing a configuration example of a marine fluid pump according to an embodiment of the present invention.
  • FIG. 2 is a diagram illustrating an on state and an off state of the control valve in the embodiment of the present invention.
  • FIG. 3 is a flowchart showing an example of a control method for the marine fluid pump according to the embodiment of the present invention.
  • FIG. 4 is a diagram for specifically explaining a marine fluid pump control method according to an embodiment of the present invention.
  • FIG. 1 is a schematic diagram showing a configuration example of a marine fluid pump according to an embodiment of the present invention.
  • this marine fluid pump 10 is a water injection pump which inject
  • the fuel flow passage of the marine diesel engine is a fuel flow passage from the discharge port of the fuel injection pump to the injection port of the fuel injection valve through the pipe, although not particularly shown.
  • a fuel injection pump is a device that injects fuel through piping or the like to a fuel injection valve for injecting fuel into a cylinder of a marine diesel engine.
  • a marine fluid pump 10 includes a pump body 1 that discharges water as an example of a fluid, a detection unit 6 that detects a maximum lift amount L m (n) of a piston 2 of the pump body 1, A control valve 7 for supplying and discharging hydraulic oil to and from the pump body 1 and a control unit 11 for controlling the control valve 7 are provided.
  • solid arrows indicate the flow of fluid such as hydraulic oil, and alternate long and short dash arrows indicate electrical signal lines.
  • the pump body 1 is a hydraulically driven pump device that discharges a fluid (water in the present embodiment) using the pressure of hydraulic oil. As shown in FIG. 1, the pump main body 1 includes a piston 2, a discharge chamber 3, a hydraulic oil chamber 4, and a water inlet 5.
  • the piston 2 is provided in the internal space of the pump body 1 so that it can reciprocate along its longitudinal direction.
  • the piston 2 includes a front portion 2a which is a piston portion on the water discharge side, a rear portion 2b which is a piston portion on the hydraulic oil receiving side, and a tapered portion 2c which is a portion between the front portion 2a and the rear portion 2b.
  • the piston 2 is formed in a rod shape so that the piston diameter of the front part 2a is smaller than the piston diameter of the rear part 2b.
  • the tapered portion 2c is formed such that the piston diameter increases or decreases (decreases in FIG. 1) from the front portion 2a side toward the rear portion 2b side.
  • the taper part 2c is used for detection of the maximum lift amount L m (n) of the piston 2 by the detection part 6 described later.
  • the discharge chamber 3 is a space for temporarily storing water discharged from the pump body 1.
  • the discharge chamber 3 is configured to be a space that faces the end surface of the front portion 2 a of the piston 2 in the internal space of the pump body 1.
  • the hydraulic oil chamber 4 is a space that receives hydraulic oil for operating the pump body 1.
  • the hydraulic oil chamber 4 is configured to be a space facing the end surface of the rear portion 2 b of the piston 2 in the internal space of the pump body 1.
  • the water injection port 5 is for filling the discharge chamber 3 with water, and is provided in the pump body 1 so as to communicate with the discharge chamber 3. Water to be injected is supplied from the water injection port 5 to the discharge chamber 3 through piping of a water tank (not shown). Water is supplied (supplied) to the discharge chamber 3 through the water inlet 5 every time water is discharged by the pump body 1.
  • a water injection pipe 18 leading to the discharge chamber 3 is connected to the discharge port side of the pump body 1.
  • the water injection pipe 18 is a pipe that guides the water discharged from the discharge chamber 3 of the pump body 1 to the fuel flow passage described above.
  • a hydraulic oil flow passage 17 communicating with the hydraulic oil chamber 4 is connected to the hydraulic oil receiving side of the pump body 1.
  • the pump main body 1 having such a configuration pressurizes and discharges water to be discharged by moving the piston 2 using the pressure of the hydraulic oil supplied via the control valve 7. At this time, the pump main body 1 receives the hydraulic oil from the hydraulic oil flow passage 17 to the hydraulic oil chamber 4 via the control valve 7 when the control valve 7 is in an ON state in which the hydraulic oil is supplied to the pump main body 1.
  • the pump body 1 moves (advances) the piston 2 so as to compress the discharge chamber 3 using the pressure of the received hydraulic oil. Thereby, the pump body 1 pressurizes the water in the discharge chamber 3 while blocking the communication between the discharge chamber 3 and the water injection port 5 with the piston 2.
  • the pressurized water is discharged from the discharge chamber 3 into the water injection pipe 18.
  • the pump main body 1 is the hydraulic oil after being used for the above-described water discharge (movement of the piston 2) (hereinafter, (Referred to as drain appropriately) is discharged from the hydraulic oil chamber 4 to the control valve 7 through the hydraulic oil flow passage 17.
  • the piston 2 allows the drain in the hydraulic oil chamber 4 to flow through the hydraulic oil flow passage 17 and the control valve 7 by the repulsive force of an urging portion (not shown) such as a spring provided in the internal space of the pump body 1. Push to the side. As a result, the piston 2 is returned to the position before water discharge.
  • the pump body 1 releases the compression (water pressurization) of the discharge chamber 3 by the piston 2.
  • the detection unit 6 detects the maximum lift amount L m (n) of the piston 2 in one discharge of water by the pump body 1. As shown in FIG. 1, the detection unit 6 includes a detection processing unit 6a and an arithmetic processing unit 6b.
  • the maximum lift amount L m (n) is an example of the maximum movement amount of the piston 2 that moves in the direction in which the fluid is pressurized (upward in the present embodiment) in one discharge of the fluid by the pump body 1.
  • the detection processing unit 6a performs a detection process for detecting the maximum lift amount L m (n). Specifically, as shown in FIG. 1, the detection processing unit 6 a is provided in the pump main body 1 so as to face the tapered portion 2 c of the piston 2. In the present embodiment, the pair of detection processing parts 6a are arranged so as to face each other with the taper part 2c interposed therebetween. The detection processing unit 6a detects (measures) the distance from the tapered portion 2c that changes due to the movement (lift) of the piston 2. The detection processing unit 6a performs such distance detection processing continuously or intermittently in time series, and each time, a signal indicating the obtained distance (hereinafter referred to as a distance detection signal as appropriate) is arithmetically processed. To the unit 6b.
  • the arithmetic processing unit 6b performs arithmetic processing for detecting the maximum lift amount L m (n). Specifically, the arithmetic processing unit 6b sequentially receives the distance detection signals from the detection processing unit 6a in chronological order. The arithmetic processing unit 6b selects the distance detection signal that maximizes the distance and the distance detection signal that minimizes the distance from the plurality of distance detection signals received from the detection processing unit 6a. For example, the arithmetic processing unit 6b generates a distance detection signal at which the voltage reaches a peak when the distance between the detection processing unit 6a and the taper portion 2c becomes maximum and minimum during one discharge period of water by the pump body 1. Each distance detection signal is selected.
  • the arithmetic processing unit 6b uses the distances between the selected distance detection signals (the distance between the detection processing unit 6a and the taper portion 2c) and the inclination angle of the taper portion 2c to generate water from the pump body 1.
  • the maximum lift amount L m (n) of the piston 2 in one discharge is calculated.
  • the arithmetic processing unit 6 b transmits a signal indicating the obtained maximum lift amount L m (n) (hereinafter, appropriately referred to as a lift amount detection signal) to the control unit 11.
  • the control valve 7 is a valve that switches between an ON state in which hydraulic oil for operating the pump body 1 is supplied to the pump body 1 and an OFF state in which the supply of hydraulic oil to the pump body 1 is stopped.
  • the control valve 7 is configured by an open / close electromagnetic valve that switches between opening and closing of the hydraulic oil flow passage.
  • the control valve 7 includes a supply flow path unit 7a, a discharge flow path unit 7b, and a drive unit 7c.
  • control valve 7 includes a hydraulic oil pipe 15 leading to a pressure accumulating facility (not shown) for accumulating the hydraulic oil pressure, a drain pipe 16 leading to a tank (not shown) for collecting the hydraulic oil (drain), A hydraulic oil flow passage 17 communicating with the hydraulic oil chamber 4 of the pump body 1 is connected.
  • FIG. 1 illustrates a state in which the hydraulic oil pipe 15, the drain pipe 16, and the hydraulic oil flow passage 17 are connected to the supply flow path unit 7 a of the control valve 7.
  • the supply flow path unit 7 a has a supply flow path 8 a for supplying hydraulic oil to the pump body 1 and a closed path 8 b for closing the drain pipe 16.
  • the discharge flow path unit 7 b includes a discharge flow path 9 a for discharging drain from the pump body 1 and a closed path 9 b for closing the hydraulic oil pipe 15.
  • the supply flow path unit 7a and the discharge flow path unit 7b are arranged so as to be adjacent to each other in a predetermined direction (lateral direction in FIG. 1), for example, as shown in FIG.
  • the drive unit 7c is configured using an electromagnetic coil (solenoid coil) or the like.
  • the drive unit 7c moves the supply flow path unit 7a and the discharge flow path unit 7b in the adjacent direction based on the valve control signal from the control unit 11, and thereby the supply flow path unit 7a and the discharge flow path unit 7b. Either of them is connected to the hydraulic oil pipe 15, the drain pipe 16, and the hydraulic oil flow passage 17.
  • the control valve 7 selectively switches between the on state and the off state by the action of the drive unit 7c.
  • FIG. 2 is a diagram illustrating an on state and an off state of the control valve in the embodiment of the present invention.
  • the control valve 7 is switched from the OFF state to the ON state by connecting the supply flow path unit 7 a to the hydraulic oil pipe 15, the drain pipe 16, and the hydraulic oil flow passage 17.
  • the supply flow path unit 7 a connects the supply flow path 8 a to the hydraulic oil pipe 15 and the hydraulic oil flow path 17 and connects the closed path 8 b and the drain pipe 16.
  • the hydraulic oil pipe 15 and the hydraulic oil flow passage 17 are in communication with each other via the supply flow path 8a.
  • the drain pipe 16 is closed by the closed path 8b.
  • the hydraulic oil is supplied to the hydraulic oil chamber 4 of the pump body 1 through the hydraulic oil pipe 15, the supply flow path 8 a, and the hydraulic oil flow passage 17 that are in communication with each other.
  • the hydraulic oil supplied to the hydraulic oil chamber 4 presses the piston 2 of the pump body 1 from the rear portion 2b side.
  • the pump body 1 uses the pressure of the hydraulic oil to move the piston 2 to pressurize the water in the discharge chamber 3 at the front portion 2 a of the piston 2 and discharge the water into the water injection pipe 18.
  • the supply of the hydraulic oil is continuously performed while the control valve 7 is on.
  • the control valve 7 is switched from the on state to the off state by connecting the discharge flow path unit 7b, the hydraulic oil pipe 15, the drain pipe 16, and the hydraulic oil flow passage 17.
  • the discharge flow path unit 7b connects the discharge flow path 9a with the drain pipe 16 and the hydraulic oil flow path 17, and connects the closed path 9b with the hydraulic oil pipe 15.
  • the drain pipe 16 and the hydraulic oil flow passage 17 are in communication with each other via the discharge flow path 9a.
  • the hydraulic oil pipe 15 is closed by the closed path 9b. As a result, the supply of hydraulic oil in the on state is stopped.
  • the piston 2 is used for operating the hydraulic oil in the hydraulic oil chamber 4 (that is, for operating the pump main body 1) by a repulsive force of an urging portion (not shown) such as a spring provided in the internal space of the pump main body 1.
  • the subsequent hydraulic oil is pressed toward the control valve 7 side.
  • the pressed hydraulic oil is discharged as drainage from the hydraulic oil chamber 4 through the hydraulic oil flow passage 17, the discharge flow passage 9a, and the drain pipe 16 that are in communication with each other as described above, and a predetermined tank (not shown). It is collected in As a result, the piston 2 is returned to the position before water discharge.
  • the pump body 1 releases the compression (water pressurization) of the discharge chamber 3 by the front portion 2 a of the piston 2 and stops the discharge of water into the water injection pipe 18.
  • the control unit 11 shown in FIG. 1 controls switching of the control valve 7 between an on state and an off state.
  • the control unit 11 includes a CPU for executing various programs, a memory, a solenoid driving unit, and the like.
  • the control unit 11 determines the target lift amount L t (n) of the piston 2 of the pump body 1 according to the water discharge amount (water injection amount into the fuel flow passage) required for one discharge of water by the pump body 1. ) Is derived.
  • the target lift amount L t (n) is an example of the movement amount (target movement amount) of the piston 2 that is a target for the pump main body 1 to discharge the required discharge amount of fluid by one discharge.
  • the target lift amount L t (n) is required for one discharge of the fluid by the pump body 1 because the equipment specifications such as the discharge capacity of the pump body 1 that discharges the fluid are known. It can be derived based on the discharge amount of the fluid.
  • the control unit 11 uses the target lift amount L t (n) derived during the current discharge of water by the pump body 1 and the maximum lift amount L m (n ⁇ 1) detected by the detection unit 6 during the previous discharge. Based on the difference, a time correction value of the valve ON time of the control valve 7 is calculated.
  • the valve on time is a time for which the control valve 7 is turned on as described above.
  • the time correction value is a value (correction time) for correcting the valve ON time.
  • the control unit 11 corrects the valve on time during the current discharge of water by the pump main body 1 so that the corrected valve on time continues and remains on.
  • the control valve 7 is controlled.
  • the control unit 11 has a data table 11a as shown in FIG.
  • the data table 11 a shows the correlation between the target lift amount L t (n) of the piston 2 and the basic valve-on time of the control valve 7.
  • the valve on basic time is the valve on time (theoretical valve on time in terms of equipment specifications) of the control valve 7 set according to the target lift amount L t (n) of the piston 2.
  • the data table 11 a includes a plurality of combinations of the target lift amount L t (n) of the piston 2 and the valve on basic time of the control valve 7 that are correlated with each other.
  • the control unit 11 derives the valve on basic time correlated with the target lift amount L t (n) derived during the current discharge of water by the pump body 1 based on the data table 11a.
  • the control unit 11 corrects the valve-on time during the current discharge of water by the pump body 1 so as to approach the sum of the derived valve-on basic time and the above-described time correction value.
  • FIG. 3 is a flowchart showing an example of a control method for the marine fluid pump according to the embodiment of the present invention.
  • FIG. 4 is a diagram for specifically explaining a marine fluid pump control method according to an embodiment of the present invention.
  • the control method of the marine fluid pump 10 see FIG. 1
  • each process of steps S101 to S104 shown in FIG. 3 is performed.
  • switching of the control valve 7 between the on state and the off state is controlled based on the valve control signal S1 from the control unit 11, and the pump body 1 discharges water through this control.
  • the lift amount of the piston 2 at that time is controlled.
  • nth cycle water discharge the current water discharge by the pump body 1
  • n ⁇ 1 cycle water discharge the previous water discharge by the pump body 1
  • n + 1 cycle water discharge The next water discharge is referred to as “n + 1 cycle water discharge”.
  • the control method of the marine fluid pump 10 will be described by exemplifying each process of steps S101 to S104 when the nth cycle of water discharge is performed.
  • the control valve 7 switches from the OFF state to the ON state at the time T1 based on the valve control signal S1, and then the timing at the time T2. Switch from on to off.
  • the time from time T1 to time T2 is the valve ON time ⁇ T3 of the control valve 7 in the water discharge of the (n-1) th cycle.
  • the valve on time ⁇ T3 is the basic valve on time of the control valve 7 set according to the target lift amount L t (n ⁇ 1) of the piston 2 in the water discharge of the (n ⁇ 1) th cycle. This corresponds to the sum of ⁇ T1 and the time correction value ⁇ T2 calculated by the control unit 11 when the water is discharged in the (n-1) th cycle.
  • the pump body 1 moves the piston 2 using the pressure of the supplied hydraulic oil, thereby pressurizing and discharging water.
  • the lift amount of the piston 2 increases with the passage of time from the time T1 when the control valve 7 is turned on, and the time from the time T2 when the control valve 7 is turned off. Decreases with progress.
  • the maximum lift amount L m (n ⁇ 1) of the piston 2 in the water discharge of the (n ⁇ 1) th cycle is the lift amount of the piston 2 at the timing of time T2, as shown in FIG.
  • Detector 6 transmits a lift detection signal indicating the maximum lift L m (n-1) detecting a maximum resultant lift L m (n-1) to the control unit 11.
  • the control unit 11 receives the lift amount detection signal from the detection unit 6 and holds the maximum lift amount L m (n ⁇ 1) indicated by the received lift amount detection signal as a parameter at the time of the subsequent n-th water discharge. To do.
  • control unit 11 sets the target of the piston 2 according to the discharge amount of the fluid required for one discharge of the fluid by the pump body 1.
  • a movement amount is derived (step S101).
  • step S101 the control unit 11 derives the target lift amount L t (n) of the piston 2 according to the water discharge amount required for the n-th water discharge.
  • control unit 11 determines the control valve 7 based on the difference between the target movement amount of the piston 2 in step S101 (target movement amount derivation step) and the maximum movement amount of the piston 2 at the previous discharge of fluid.
  • a time correction value for the valve ON time is calculated (step S102).
  • step S102 the control unit 11 acquires and holds the target lift amount L t (n) of the piston 2 derived in step S101 described above and the water discharge at the (n-1) th cycle.
  • the controller 11 calculates a time correction value ⁇ T12 in the nth cycle of water discharge.
  • the control unit 11 lifts the lift based on the equipment specifications of the pump body 1, for example, the lift amount per unit time of the piston 2 that moves using the pressure of the hydraulic oil (amount of change over time of the lift amount).
  • the quantity deviation ⁇ L (n) is converted into time (that is, converted into a time correction value ⁇ T12).
  • the control unit 11 updates the time correction value ⁇ T2 in the water discharge of the (n ⁇ 1) th cycle to the time correction value ⁇ T12 calculated in this way.
  • control unit 11 corrects the valve-on time of the control valve 7 during the current discharge of the fluid by the pump body 1 in consideration of the time correction value ⁇ T12 in step S102 (time correction value calculation step) (step S102). S103).
  • the control unit 11 derives the valve on basic time ⁇ T11 of the control valve 7 set according to the target lift amount Lt (n) of the piston 2. For example, the control unit 11 derives the valve-on basic time ⁇ T11 that correlates with the target lift amount Lt (n) in step S101 described above based on the data table 11a.
  • control unit 11 controls the control valve 7 so as to be continuously turned on during the valve on-time ⁇ T13 after the correction in step S103 (correction step) (step S104). After executing step S104 (correction step), the control unit 11 returns to step S101 described above and repeats the processing steps after step S101.
  • step S104 the control unit 11 transmits to the control valve 7 a valve control signal S1 (see FIG. 4) that instructs the valve ON time ⁇ T13 corrected as described above to continue to be in the ON state.
  • the control part 11 controls switching of the ON state of the control valve 7 in the water discharge of the nth cycle, and an OFF state.
  • the control valve 7 switches from the off state to the on state at the timing of time T3 based on the valve control signal S1, and then switches from the on state to the off state at the timing of time T4.
  • the time from time T3 to time T4 is the valve-on time ⁇ T13 of the control valve 7 in the water discharge of the nth cycle.
  • the pump body 1 moves the piston 2 using the pressure of the supplied hydraulic oil, thereby pressurizing and discharging water.
  • the lift amount of the piston 2 increases with the passage of time from the timing at time T3 when the control valve 7 is turned on, and the time from the timing at time T4 when the control valve 7 is turned off. Decreases with progress.
  • the maximum lift amount L m (n) of the piston 2 in the water discharge at the nth cycle is the lift amount of the piston 2 at time T4 as shown in FIG.
  • Detector 6 transmits a lift detection signal indicating the maximum detected the lift amount L m (n), the amount of the maximum resultant lift L m (n) to the controller 11.
  • the control unit 11 receives the lift amount detection signal from the detection unit 6 and holds the maximum lift amount L m (n) indicated by the received lift amount detection signal as a parameter at the time of the subsequent n + 1 cycle water discharge.
  • the control valve 7 switches from the off state to the on state at the time T5 based on the valve control signal S1, and then the timing at the time T6. Switch from on to off.
  • the time from time T5 to time T6 is the valve ON time ⁇ T23 of the control valve 7 in the water discharge of the (n + 1) th cycle.
  • the valve on time ⁇ T23 is equal to the basic valve on time ⁇ T21 of the control valve 7 set according to the target lift amount L t (n + 1) of the piston 2 in the water discharge of the (n + 1) th cycle, and n + 1 This corresponds to the sum of the time correction value ⁇ T22 calculated by the control unit 11 when the water is discharged in the cycle.
  • the hydraulic oil is continuously supplied to the hydraulic oil chamber 4 of the pump body 1 through the control valve 7 in the on state.
  • the pump body 1 moves the piston 2 using the pressure of the supplied hydraulic oil, thereby pressurizing and discharging water.
  • the lift amount of the piston 2 increases with the passage of time from the timing at time T5 when the control valve 7 is turned on, and the time from the timing at time T6 when the control valve 7 is turned off. Decreases with progress.
  • the maximum lift amount of the piston 2 in the water discharge of the (n + 1) th cycle is the lift amount of the piston 2 at the timing of time T6 as shown in FIG.
  • the detection unit 6 detects the maximum lift amount and transmits a lift amount detection signal indicating the obtained maximum lift amount to the control unit 11.
  • the control unit 11 holds this maximum lift amount as a parameter at the time of water discharge in the subsequent cycle, as in the case of each of the water discharges in the (n-1) th cycle and the nth cycle described above.
  • the error between the target lift amount L t (n) of the piston 2 and the maximum lift amount L m (n) in the water discharge of the nth cycle is the n ⁇ 1th cycle. It is reduced compared to the water discharge.
  • the error between the target lift amount L t (n + 1) of the piston 2 and the maximum lift amount in the water discharge of the (n + 1) th cycle is reduced compared to the water discharge of the nth cycle.
  • the control valve 7 for supplying the hydraulic oil for operating the pump body 1 is turned on to supply the hydraulic oil.
  • an open / close control valve that selectively switches off the supply of hydraulic oil, and the piston of the pump body 1 according to the fluid discharge amount required for one discharge of the fluid by the pump body 1 2 is derived, and the control valve 7 is turned on based on the difference between the target movement amount of the piston 2 during the current fluid discharge and the maximum movement amount of the piston 2 during the previous fluid discharge.
  • the time correction value of the valve on time is calculated, and the valve on time of the control valve 7 at the time of the current fluid discharge is corrected in consideration of the calculated time correction value, and the valve on time after correction is continued.
  • Control to turn on 7, and the piston 2 is moved using the pressure of the hydraulic oil supplied to the pump body 1 through the control valve 7, so that the piston 2 pressurizes the fluid and discharges it from the pump body 1.
  • control valve 7 is an opening / closing type electromagnetic valve that is relatively resistant to foreign matter mixing, rather than an opening adjustment type electromagnetic valve that is relatively weak against foreign matter mixing, the marine diesel engine operates.
  • the control valve 7 suitable for the marine fluid pump 10 installed in an environment, that is, an environment in which foreign matter is likely to be mixed, can be configured. As a result, it is possible to suppress failure and maintenance frequency due to foreign matter mixing into the control valve 7 of the marine fluid pump 10 in the marine vessel.
  • the water injection pump is exemplified as the marine fluid pump 10, but the present invention is not limited to this.
  • the marine fluid pump 10 may be a fuel injection pump that discharges (pressure feeds) fuel to the fuel injection valve, or may be a pump that discharges fluid other than fuel. That is, in the present invention, the type of fluid to be discharged is not particularly limited.
  • control unit 11 in which the data table 11a indicating the correlation between the target movement amount of the piston 2 and the basic valve-on time of the control valve 7 is illustrated as an example. It is not limited.
  • the control unit 11 may be preliminarily set with an arithmetic expression, a calculation program, or the like that calculates the valve-on basic time of the control valve 7 based on the target movement amount of the piston 2.
  • the lift amount (the upward movement amount of the piston 2) is exemplified as the movement amount of the piston 2, but the present invention is not limited to this.
  • the movement amount of the piston 2 may be any movement amount in the direction in which the fluid to be discharged is pressurized, and this direction is not particularly limited.
  • the present invention is not limited by the above-described embodiment, and the present invention includes a configuration in which the above-described constituent elements are appropriately combined.
  • other embodiments, examples, operation techniques, and the like made by those skilled in the art based on the above-described embodiments are all included in the scope of the present invention.
  • the marine fluid pump and the control method thereof according to the present invention are useful for discharging fluids such as fuel and water in marine diesel engines, and in particular, the amount of movement of the piston when the fluid is pressurized and discharged. Is suitable for a marine fluid pump that can be controlled with high accuracy while suppressing an increase in cost, and a control method thereof.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Ocean & Marine Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Details Of Reciprocating Pumps (AREA)
PCT/JP2019/005958 2018-03-02 2019-02-19 舶用流体ポンプおよびその制御方法 WO2019167708A1 (ja)

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CN201980016089.1A CN111788381B (zh) 2018-03-02 2019-02-19 船用流体泵及其控制方法

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KR102666988B1 (ko) 2022-04-05 2024-05-20 (주)태성정밀 선박용 레이디얼 피스톤 펌프
JP2024030317A (ja) * 2022-08-24 2024-03-07 株式会社ジャパンエンジンコーポレーション 燃料噴射システム

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JP2000356156A (ja) * 1999-06-15 2000-12-26 Isuzu Motors Ltd コモンレール式燃料噴射装置
JP2009085074A (ja) * 2007-09-28 2009-04-23 Denso Corp 蓄圧式燃料噴射システムの制御装置
JP2010103315A (ja) * 2008-10-23 2010-05-06 Denso Corp 圧電アクチュエータおよびそれを用いた燃料噴射弁
JP2012002179A (ja) * 2010-06-18 2012-01-05 Denso Corp 高圧ポンプの制御装置
JP2013142299A (ja) * 2012-01-10 2013-07-22 Honda Motor Co Ltd 内燃機関の燃料供給装置

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JPH04176742A (ja) 1990-11-08 1992-06-24 Hayashi Gijutsu Kenkyusho:Kk 自動車用フロアカーペットの製造方法
JP3287297B2 (ja) * 1998-02-10 2002-06-04 トヨタ自動車株式会社 燃料ポンプの制御装置
JP2002364396A (ja) 2001-06-05 2002-12-18 Tokico Ltd 燃料混合充填システム
JP5061347B2 (ja) * 2004-11-04 2012-10-31 国立大学法人東京海洋大学 舶用ディーゼル機関の燃料噴射制御方法及びその装置
JP4176742B2 (ja) * 2005-06-14 2008-11-05 三菱重工業株式会社 内燃機関の液圧供給装置
NL2002384C2 (nl) * 2008-03-03 2011-04-04 Vialle Alternative Fuel Systems Bv Inrichting en werkwijze voor een verbrandingsmotor met directe inspuiting met twee brandstoffen.
EP2295774A1 (en) * 2009-08-18 2011-03-16 Delphi Technologies Holding S.à.r.l. Control method for a common rail fuel pump and apparatus for performing the same

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JP2000356156A (ja) * 1999-06-15 2000-12-26 Isuzu Motors Ltd コモンレール式燃料噴射装置
JP2009085074A (ja) * 2007-09-28 2009-04-23 Denso Corp 蓄圧式燃料噴射システムの制御装置
JP2010103315A (ja) * 2008-10-23 2010-05-06 Denso Corp 圧電アクチュエータおよびそれを用いた燃料噴射弁
JP2012002179A (ja) * 2010-06-18 2012-01-05 Denso Corp 高圧ポンプの制御装置
JP2013142299A (ja) * 2012-01-10 2013-07-22 Honda Motor Co Ltd 内燃機関の燃料供給装置

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CN111788381B (zh) 2022-05-03
KR20200105951A (ko) 2020-09-09
JP2019152148A (ja) 2019-09-12
CN111788381A (zh) 2020-10-16
JP6546307B1 (ja) 2019-07-17
KR102316904B1 (ko) 2021-10-22

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