WO2018054553A1 - Verfahren zum betreiben einer hochdruckpumpe eines hochdruck- einspritzsystems eines kraftfahrzeugs sowie steuervorrichtung und kraftfahrzeug - Google Patents
Verfahren zum betreiben einer hochdruckpumpe eines hochdruck- einspritzsystems eines kraftfahrzeugs sowie steuervorrichtung und kraftfahrzeug Download PDFInfo
- Publication number
- WO2018054553A1 WO2018054553A1 PCT/EP2017/054941 EP2017054941W WO2018054553A1 WO 2018054553 A1 WO2018054553 A1 WO 2018054553A1 EP 2017054941 W EP2017054941 W EP 2017054941W WO 2018054553 A1 WO2018054553 A1 WO 2018054553A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- dead center
- piston
- top dead
- coil current
- motor vehicle
- Prior art date
Links
- 238000002347 injection Methods 0.000 title claims abstract description 21
- 239000007924 injection Substances 0.000 title claims abstract description 21
- 238000000034 method Methods 0.000 title claims abstract description 20
- 239000012530 fluid Substances 0.000 claims abstract description 38
- 230000006835 compression Effects 0.000 claims abstract description 34
- 238000007906 compression Methods 0.000 claims abstract description 34
- 230000008859 change Effects 0.000 claims abstract description 12
- 238000005259 measurement Methods 0.000 claims description 6
- 230000004044 response Effects 0.000 claims description 5
- 230000001419 dependent effect Effects 0.000 abstract description 3
- 239000000446 fuel Substances 0.000 description 11
- 238000002485 combustion reaction Methods 0.000 description 7
- 230000008901 benefit Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000006698 induction Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 238000005056 compaction Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 239000003502 gasoline Substances 0.000 description 2
- 238000010992 reflux Methods 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 230000002123 temporal effect Effects 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 210000003608 fece Anatomy 0.000 description 1
- 230000012447 hatching Effects 0.000 description 1
- 230000001939 inductive effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- 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
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
-
- 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
- F02D41/3836—Controlling the fuel pressure
- F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
-
- 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
- F02D41/009—Electrical control of supply of combustible mixture or its constituents using means for generating position or synchronisation signals
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/025—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by a single piston
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- 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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
-
- 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
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
- F02D2041/2055—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit with means for determining actual opening or closing time
-
- 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
-
- 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
- F02D2200/0606—Fuel temperature
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/02—Piston parameters
- F04B2201/0201—Position of the piston
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/06—Valve parameters
- F04B2201/0601—Opening times
- F04B2201/06011—Opening times of the inlet valve only
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1208—Angular position of the shaft
Definitions
- the invention relates to a method for operating a high-pressure pump of a high-pressure injection system of a motor vehicle ⁇ .
- fuel can be conveyed into an internal combustion engine of the motor vehicle.
- the invention also includes a control device for a high-pressure injection system and a
- the fuel pressure as generated by a high-pressure pump of the high-pressure injection system is regulated to a target pressure.
- An actuator of this pressure control is an electromagnet of the intake valve. It is a Digital Inlet Valve (DIV) whose closing time during a high pressure pump discharge phase decides how much of the pumped fluid is expelled or pushed or pumped through the fuel pump's outlet valve into the high pressure area (rail). In other words, the delivery rate of the high-pressure pump is dependent on the activation time of the solenoid of the intake valve. Since a spring presses the intake valve permanently toward an open position, no fuel is supplied through the exhaust valve without energizing the solenoid.
- DIV Digital Inlet Valve
- the inlet valve By activating a drive profile for the coil current of the electromagnet (the so-called peak-and-hold current profile), the inlet valve is closed by means of the electromagnet.
- the fuel within the compression chamber or pump chamber can be compressed by the piston of the high-pressure pump and conveyed through the outlet valve into the high-pressure region.
- the adjustment of the flow rate and thus of the target pressure is only possible in a precise manner if the control during the grain Pression phase or ejection phase (delivery phase) of the high ⁇ pressure pump takes place, even while the piston is moved from bottom dead center to the top dead center of its cyclic piston movement. Therefore, it is necessary to know the timing of the top dead center of the high-pressure pump piston so as to be able to adjust the fuel pressure to the target pressure at all.
- a time is not necessarily meant to indicate a time.
- the piston is usually driven by an engine shaft, for example the crankshaft of the internal combustion engine, which by means of the high-pressure injection system with
- the top dead center can be described accordingly by the corresponding rotational position of the motor shaft be ⁇ .
- the rotational position of the motor shaft at top dead center of the piston is referred to here as dead center rotational position.
- the invention has for its object to determine the dead center rotational position in a driven by a motor shaft high-pressure pump of a high-pressure injection system.
- the invention provides a method for operating a high-pressure pump of a high-pressure injection system of a motor vehicle.
- a piston is the High pressure pump driven by a motor shaft of the motor vehicle in a conventional manner.
- the piston thereby moves in a pump room or displacement or compression space of the high-pressure pump cyclically between a bottom dead center (lowest compression) and a top dead center (largest
- the coil current is switched on again alternatively, that is, the solenoid is again charged with a coil current.
- the coil current in time been considered by a ⁇ estimated or a default value (default value) for the dead-center rotational position can be.
- Inlet valve meets a predetermined change criterion. For example, a current intensity of the coil current is determined and its time course is checked to see if the change criterion is met. Thus, it is the movement that performs the intake valve from the closed position into the ⁇ Of fengnagna, detected on the basis of the temporal course of the coil current.
- the beginning of movement is important, ie the starting time at which the inlet valve moves out of the closed position.
- the dead center rotational position of the motor shaft is determined, in which therefore the piston is in top dead center.
- Said start time, which is detected may itself be indicated as a value of the rotational position of the motor shaft. Thus, no time measurement is necessary, but all the values determined can be specified as the rotational position value of the motor shaft.
- the invention there is the advantage that for the determination of the top dead center no complex position measurement of the piston by means of a separate sensor is necessary.
- the Tot ⁇ point rotational position is determined indirectly from the time course of the coil current. For this purpose, the coil current after the Close the intake valve continues to be maintained or turned on again.
- the invention also includes advantageous developments, the characteristics of which provide additional advantages.
- the change criterion is checked in the manner described.
- This change criterion provides in particular that the effective coil current increases.
- the opening movement of the inlet valve is detected by inducing an induction voltage in the electrical coil of the electromagnet and this leads to an additional induction current which is superimposed on the set coil current and thus causes a larger effective coil current.
- an average value of the coil current is preferably determined at certain measuring times, that is to say cyclically, for example at intervals in a range from 1 ms to 100 ms.
- the measured values of the coil current in a range of the last millisecond up to the last 200 ms can be combined to the respective mean value.
- Start time is that measurement time at which the average value is greater than the average value at the immediately vo ⁇ reaching measuring time. In other words, if the sequence of measurement times increases or increases with the current mean value, this is determined as the start time.
- the intake valve By energizing the intake valve, as provided for determining the dead center rotational position, the intake valve may not be kept closed, as this would otherwise prevent the opening movement starts at all. To ensure this, it is preferably provided that a current intensity of the coil current during and / or after exceeding the top dead center is set to be smaller than is necessary to close the inlet valve. It is therefore not a coil current to close the inlet valve, but a measuring current.
- a closing force caused by the coil current is smaller than a spring force of the valve spring, which presses the inlet valve toward the open position. This ensures that is relaxed, at least for the case where the fluid is completely relaxed, so the A ⁇ let pressure in the inlet or low pressure area of the high-pressure pump, the inlet valve opens secure or reliable.
- the relaxation or expansion of the fluid also has an influence on the starting time at which the inlet valve opens, that is to say the opening movement begins or begins, being offset in time from the top dead center. Because the intake valve does not open already when the piston exceeds the top dead center, but at a later time when the piston has moved away from top dead center and the fluid is so relaxed that the spring force of the valve spring and the pressure force of the inlet pressure together are greater than the pressure of the fluid in the compression chamber.
- the dead center rotational position is preferably accurately estimated by starting from a rotational position of the motor shaft to the start ⁇ time when, therefore, the intake valve starts or begins to open, is calculated back by a piston stroke is determined, which is necessary to the fluid starting from the top dead center to relax or expand so far that the movement start of the opening movement of the intake valve results.
- the expansion of the fluid is taken into account.
- the fluid is still elastically compressed in such a way that it keeps the inlet valve closed even when the piston continues to move.
- This required piston stroke up to the beginning of the movement need not be recalculated for every piston movement or every movement cycle.
- Predefined calculation values can be used for this purpose.
- the described back calculation can be done for example by means of a table or a map.
- the recalculation is carried out as a function of a temperature and / or a pressure of the fluid.
- the current elastic modulus (modulus of elasticity) of the fluid can be taken into account, which changes with the temperature and / or the pressure of the fluid. This makes the determination of the dead-center rotational position more precise.
- a control device for a high-pressure injection system of a motor vehicle is provided according to the invention.
- the STEU ⁇ ervoriques has a processor device is set to, depending on a rotational signal of a motor shaft which can drive the piston of a high pressure pump of the high ⁇ pressure injection system, to set an intake valve of the high pressure pump to switch a current of Elekt ⁇ romagneten or adjust.
- the solenoid is activated on the one hand to close the inlet valve and thereby to conduct the ejected fluid through the outlet valve in the manner described.
- the inlet valve is then re-opened depending on the spring force of the valve spring and the pressure conditions in the inlet valve.
- the control device can also adjust the said measuring current.
- the processor device is set up to act on the electromagnet in the ejection phase of the high-pressure pump during and / or after exceeding the top dead center of the piston of the high-pressure pump with a coil current which represents the measuring current.
- the control device is configured to detect a start time at which the coil current satisfies the change criterion due to a start of movement of an opening movement of the intake valve.
- the processor input Direction determines the dead center rotational position of the motor shaft, in which the piston is at top dead center.
- the invention also includes a motor vehicle with the control device according to the invention.
- the motor vehicle is set up to carry out an embodiment of the method according to the invention.
- a piston of a high-pressure pump of a high-pressure injection system of the motor vehicle is driven so that it is cyclically moved back and forth between the bottom dead center and top dead center in the compression chamber.
- Fig. 1 is a schematic representation of an embodiment of the motor vehicle according to the invention
- Fig. 2 is a diagram illustrating a sequence of
- Fig. 3 is a diagram illustrating a sequence of a
- Fig. 4 is a schematic representation of the high-pressure pump of
- FIG. 5 diagrams for illustrating a method for
- Fig. 1 shows a motor vehicle 10, which may be, for example, a motor vehicle, such as a passenger car or truck.
- the motor vehicle 10 may include an internal combustion engine 11 which may be coupled to a fuel tank 12 via a high pressure injection system 13 by which a fluid 14 contained in the fuel tank 12, eg, a fuel such as diesel or gasoline, is delivered to the engine 11 can be.
- the high-pressure injection system 13 may have a high-pressure pump 15 with an inlet valve 16 and a control device 17 for controlling an electromagnet 18 of the inlet valve 16.
- the control device 17 may adjust a coil current 19 flowing through an electric coil 18 'of the electromagnet 18.
- the controller 17 may adjust the coil current 19 in response to a rotational position signal 20 that a rotational position of a motor shaft 21 of the motor vehicle 10 describes or signaled ⁇ Siert.
- the motor shaft 21 may, for example, be coupled to a crankshaft of the internal combustion engine 11.
- the motor shaft 21 may also be the crankshaft itself.
- a pin 27 of the inlet valve 16 is thereby moved by means of the coil current 19 by energizing the coil 18 'of the electromagnet 18.
- a valve spring 28 counteracts the magnetic force of the electromagnet 18 and pushes the pin 27 thereby to an open position, as shown in Fig. 1.
- the spring force of the Ven ⁇ spring spring 28 is overcome and a valve 29 with the attached pin 27 is moved against the spring force of the valve spring 28 and thereby the inlet valve 16 is closed.
- FIG. 2 illustrates how this leads to the conveyance of the fluid 14.
- the intake valve is opened and the piston 22 is moved from a top dead center 31 (see FIG. 1) to the bottom dead center 32.
- the inlet valve 16 Through the inlet valve 16, the fluid 14 flows into the compression space 33.
- the piston 22 is moved between a top dead center 31 and a bottom dead center 32 in a compression chamber 33 back and forth.
- a subsequent ejection phase 34 the piston 22 is moved by the piston movement 23, starting from the bottom dead center 32 toward the top dead center 31 (see FIG. 1).
- the inlet valve 16 is still open, and the piston 22 thereby expels fluid 14 from the compression space 33 back through the inlet valve 16 (return flow 35).
- the control device 17 energizes the electromagnet 18 if the rotational position signal 20 of the motor shaft 21 has a corresponding value. As a result, the electromagnet 18 is energized or turned on and the on ⁇ let valve 16 is closed.
- FIG. 3 again illustrates this process as a function of the rotational position of the motor shaft 21 signaled by the rotational position signal 20, it being assumed here that the sequence of the inlet phase 30 and the ejection phase 34 with the reflux 35 is twice the same for each complete revolution of the motor shaft 21 and the pumping process 36 takes place.
- Fig. 4 illustrates how in the closed position shown in Fig. 4, the pin 27 is held even when no coil current 19 flows.
- the piston 22 must first a predetermined intermediate position 39 reach between the top dead center 31 and the bottom dead center 32, so that the fluid 14 in the compression chamber 33 is sufficiently relaxed, so that the pressure in the compression space 33, a compressive force 37 ⁇ results, which is small enough to the pin 27 from the in 4 to the open position shown in Fig. 1 by means of the spring force 38 and the low pressure 37 to move.
- Fig. 5 shows how, on the one hand, the start of movement of this opening movement of the inlet valve 16, i. whose pin 27 can be detected by the control device 17 and how, on the other hand, starting from this value of the rotational position signal 20 of the motor shaft 21 can be calculated back, which results when the piston 22 is at top dead center 31.
- Fig. 5 illustrates this with respect to time t on the one hand the flow of fluid F
- the rotational position signal 20 can be generated by a Drehla ⁇ gegeber 47, for example, as a pulse train, and a temporal course of the coil current 19.
- the inlet valve by adjusting a current profile 40 is closed for the coil current 19.
- the coil current 19 may be switched off in a switching pause 41.
- the coil current 19 can be switched on again with a measuring profile 42 by the control device 17, wherein a current intensity I results from the measuring profile 42 which is smaller than the current intensity I of the current profile 40 Closing the Inlet Valve 16.
- a mean value 43 of the current I of the coil current 19 remains constant or within a predetermined tolerance until a start of movement of the opening movement of the pin 27 of the inlet valve 16 becomes a start time 44 occurs.
- start time 44 a balance of forces is compensated as described in FIG. 4.
- the inlet valve 16 opens at the start time 44. This occurs when the pressure in the compression space 33, ie in its free dead volume, has degraded by the piston movement 23 toward the bottom dead center 32 (intermediate position 39).
- the movement of the pin 27 and the armature 29 induces in the electrical coil 18 ⁇ an additional induction current, which leads to an increase 45 of the RMS value or mean 43.
- the beginning of this increase 45 represents a change criterion.
- the start time 44 can be detected by the control device 17. Taking into account the current modulus of elasticity of the fluid 14, the dead center rotational position 46 of the motor shaft 21 can be determined, at which the piston 22 was at top dead center 31 or also in the next pumping cycle. The following is a calculation example for the recalculation of
- a current increase in the reduced measuring profile 42 is the natural opening point of the inlet valve (NOP). NOP occurs to BEWE ⁇ supply the beginning of the valve. Before that, the inlet valve remains closed because there is a pressure inside the compression chamber 33 which prevents opening of the inlet valve. The valve will only move when the spring force and the resulting force from the pressure on the low-pressure side become greater than the hydraulic force prevailing in the compression chamber. This can only happen if the pressure in the compression chamber is reduced by the piston movement in the direction of the bottom dead center:
- valve can only move when the compaction ⁇ processing chamber pressure is below 0.88Mpa.
- the piston In order to achieve the smallest compression chamber pressure, the piston must complete a certain lifting height in the direction of bottom dead center, so are 39 to the intermediate position.
- volume (actual high-pressure side high pressure - minimum compression chamber pressure) / modulus * dead volume
- volume (actual high-pressure side high pressure - minimum compression chamber pressure) / modulus * dead volume
- the Detection of top dead center 31 of the high-pressure pump in particular solved by software. This is not only a cost effective solution, but also more accurate than previously available solutions with a position sensor for the piston 22.
- the example shows how an upper dead center can be detected by the invention in a high-pressure pump of a high-pressure injection system.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/336,541 US11346331B2 (en) | 2016-09-26 | 2017-03-02 | High-pressure pump in a high-pressure injection system of a vehicle |
JP2019516248A JP6793821B2 (ja) | 2016-09-26 | 2017-03-02 | 自動車の高圧噴射システムの高圧ポンプを動作させる方法ならびに制御装置および自動車 |
KR1020197011449A KR102169756B1 (ko) | 2016-09-26 | 2017-03-02 | 자동차의 고압 분사 시스템의 고압 펌프를 동작시키는 방법, 그리고 제어 장치 및 자동차 |
CN201780059477.9A CN109863292B (zh) | 2016-09-26 | 2017-03-02 | 用于操作机动车辆的高压喷射系统的高压泵的方法、控制装置和机动车辆 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016218426.1A DE102016218426B3 (de) | 2016-09-26 | 2016-09-26 | Verfahren zum Betreiben einer Hochdruckpumpe eines Hochdruckeinspritzsystems eines Kraftfahrzeugs sowie Steuervorrichtung und Kraftfahrzeug |
DE102016218426.1 | 2016-09-26 |
Publications (1)
Publication Number | Publication Date |
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WO2018054553A1 true WO2018054553A1 (de) | 2018-03-29 |
Family
ID=58266570
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/EP2017/054941 WO2018054553A1 (de) | 2016-09-26 | 2017-03-02 | Verfahren zum betreiben einer hochdruckpumpe eines hochdruck- einspritzsystems eines kraftfahrzeugs sowie steuervorrichtung und kraftfahrzeug |
Country Status (6)
Country | Link |
---|---|
US (1) | US11346331B2 (de) |
JP (1) | JP6793821B2 (de) |
KR (1) | KR102169756B1 (de) |
CN (1) | CN109863292B (de) |
DE (1) | DE102016218426B3 (de) |
WO (1) | WO2018054553A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112867863A (zh) * | 2018-07-13 | 2021-05-28 | 纬湃科技有限责任公司 | 用于诊断高压燃料喷射泵的数字流量调节阀的方法 |
US11346331B2 (en) | 2016-09-26 | 2022-05-31 | Vitesco Technologies GmbH | High-pressure pump in a high-pressure injection system of a vehicle |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102010030447A1 (de) * | 2010-06-23 | 2011-12-29 | Bayerische Motoren Werke Aktiengesellschaft | Verfahren zur Bestimmung der Lage eines oberen Totpunkts bei einer Kolben-Hochdruckpumpe in einer Kraftstoffversorgung eines Verbrennungsmotors |
DE102012223645B3 (de) * | 2012-12-18 | 2014-02-27 | Continental Automotive Gmbh | Verfahren zum Betreiben eines Kraftstoffeinspritzsystems und Kraftstoffeinspritzsystem |
Family Cites Families (15)
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- 2017-03-02 US US16/336,541 patent/US11346331B2/en active Active
- 2017-03-02 KR KR1020197011449A patent/KR102169756B1/ko active IP Right Grant
- 2017-03-02 JP JP2019516248A patent/JP6793821B2/ja active Active
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Also Published As
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DE102016218426B3 (de) | 2018-02-01 |
KR102169756B1 (ko) | 2020-10-26 |
JP2019529783A (ja) | 2019-10-17 |
US20210285410A1 (en) | 2021-09-16 |
CN109863292A (zh) | 2019-06-07 |
US11346331B2 (en) | 2022-05-31 |
KR20190047731A (ko) | 2019-05-08 |
CN109863292B (zh) | 2022-02-11 |
JP6793821B2 (ja) | 2020-12-02 |
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