CN101542106B - A piston of a fuel injection pump and a fuel injection pump - Google Patents

A piston of a fuel injection pump and a fuel injection pump Download PDF

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Publication number
CN101542106B
CN101542106B CN2007800439093A CN200780043909A CN101542106B CN 101542106 B CN101542106 B CN 101542106B CN 2007800439093 A CN2007800439093 A CN 2007800439093A CN 200780043909 A CN200780043909 A CN 200780043909A CN 101542106 B CN101542106 B CN 101542106B
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China
Prior art keywords
piston
fuel
load
control limit
pressure chamber
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CN2007800439093A
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CN101542106A (en
Inventor
M·科伊武南
T·哈格伦
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Wartsila Finland Oy
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Wartsila Finland Oy
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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
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • 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
    • F02M59/10—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 the piston-drive
    • 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

Abstract

A piston (4) of a fuel injection pump (1 ) of a piston engine, comprising a first inclined control edge (10) located at the side of the piston (4) for determining the starting time of the fuel injection of the injection pump (1) at a certain engine load, and a second inclined control edge (11) located at the side of the piston (4) for determining the ending time of the fuel injection of the injection pump (1) at a certain engine load. The distance between points of the first (10) and second (11) control edges corresponding to the same load in the axial direction (13) of the piston (4) changes linearly or essentially linearly at a range (A-D) corresponding to the engine idle speed and the full load.

Description

The piston of fuel-injection pump and fuel-injection pump
Technical field
The present invention relates to the fuel-injection pump piston of reciprocating engine.This invention still further relates to fuel-injection pump.
Background technique
Jet pump is used for reciprocating engine and is used for periodically pressurized fuel being injected nozzle and injects cylinder by nozzle.A jet pump of reciprocating engine comprises the cylinder element, wherein comprises the pressure chamber of reciprocating piston, and the motion of this piston increases fuel pressure.The cylinder element generally includes at least one inlet passage, by this inlet passage fuel is introduced the pumping chamber from being positioned at its outside inlet chamber.Piston comprises two control limits, and wherein the zero-time that fuel sprays is determined and the concluding time is determined on second limit in first limit.When the first control limit that is arranged in the piston side that moves towards upper dead center the pressure chamber covered the opening of inlet passage, the fuel pressure the pressure chamber in increased and pressurized fuel leads to the feeding-passage of nozzle from pressure chamber's flow direction.When the second control limit of piston side arrived the opening of inlet passage and opens inlet passage, the pressure of pressure chamber was discharged in the inlet chamber by inlet passage and the mobile end of fuel flow nozzle.The second control limit is spiral helicine, and the concluding time of fuel injection can change by piston is rotated around its longitudinal axis whereby.
Summary of the invention
Target of the present invention provides a kind of improvement fuel-injection pump method of operating.
According to the present invention, this can realize as described in claim 1 and 4.
Comprise according to the piston of fuel-injection pump of the present invention and to determine on tilt control limit and determine that fuel under certain engine load sprays second of the concluding time control limit that tilts of first of zero-time that the fuel under certain engine load sprays.In the present invention, at the axial direction of piston, the first and second control limits corresponding to the distance between the point of same load with corresponding to engine idle and fully loaded scope internal linear and the variation of substantially linear ground.
Can realize sizable advantage by the present invention.
First of piston tilts to control the limit and can so form so that the zero-time of spraying changes when engine load changes as required.For example in order to improve engine efficiency or its load acceptance or to discharge in order reducing in the certain load scope, the zero-time of injection can be optimized as required.
The distance along the piston axial direction is being equivalent to the change of no-load speed and flat-out scope internal linear or substantially linear ground to the formation like this of the control limit of piston between the limit so that the first control limit and second is controlled.Therefore, the effective stroke of jet pump and curve of output load range internal linear or the substantially linear ground between idle running and full load changes.Therefore, the curve of output of jet pump does not comprise the sudden change harmful to power operation.
For example first of the piston control limit can so form so that the zero-time that fuel sprays when the intermediate engine loads of about 60-80% during early than low-load.When the high load of about 85-100%, the zero-time that fuel sprays is compared with shoulder load and is postponed, so the firing pressure in the cylinder can not become excessive.In overload, promptly when surpassing 100% load, igniting further is delayed with so that firing pressure remains on acceptable degree with comparing at full capacity.
Description of drawings
Hereinafter, by embodiment the present invention is disclosed in more detail according to additional accompanying drawing.
Fig. 1 is the partial cross section figure according to a jet pump of the present invention.
Fig. 2 is the side view of fuel-injection pump among Fig. 1.
Embodiment
Be used for pressurized fuel and be injected in the cylinder of reciprocating engine according to the fuel-injection pump 1 of Fig. 1 in the moment of hope.This jet pump 1 comprises cylinder element 2, wherein is formed with cylindrical pressure chamber 3.Pressure chamber 3 be included among Fig. 1 and Fig. 2 that section not represents movably, elongated piston 4.When motor moves, piston 4 in pressure chamber 3 along its axial direction, i.e. the direction to-and-fro motion of the longitudinal axis 13 of piston.The pressurization of fuel in the to-and-fro motion build-up of pressure chamber 3 of piston 4.The to-and-fro motion of piston 4 is that the cam 16 by rotating cam axle 15 causes that piston 4 is operably connected to this cam.Piston 4 utilizes the spring (not shown) to be pressed on the cam 16.
Cylinder element 2 has one or more discharge routes 5 that lead in the pressure chamber 3, and via this discharge route, pressurized fuel is introduced into the high voltage terminal of fuel system, for example the nozzle 20 of cylinder.The feeding-passage 29 that leads to nozzle 5 from discharge route 5 has main flow valve 21, opens when the pressure of this main flow valve in pressure chamber 3 surpasses a certain limiting value and the pressure in pressure chamber 3 is reduced to when being lower than this limiting value and closes.This main flow valve 21 is one-way valves, that is to say, its allows from the pressure chamber 3 to the flowing of nozzle 20, but stops from nozzle 20 flowing to pressure chamber 3.In addition, jet pump 1 comprises the return flow line 30 of being furnished with constant pressure valve 28, and first end of this return flow line links to each other with inlet passage 29 between main flow valve 21 and the nozzle 21.Second end of this return flow line 30 links to each other with feeding-passage 29 between discharge route 5 and the main flow valve 21.Open when the pressure of this constant pressure valve 28 in 30 first ends of return flow line surpasses a certain limiting value and be reduced to and close when being lower than this limiting value at pressure.This constant pressure valve 28 also is a check valve type, that is to say, it allows via return flow line 30 flowing from first end to second end, but prevents rightabout flowing.When the injection of jet pump 20 finished, the pressure in the feeding-passage 29 remained on the limiting value of requirement by constant pressure valve 28.
Telescopic main body part 6 is arranged on around the cylinder element 2.Annular inlet chamber 7 is arranged between main body part 6 and the cylinder element 2, and this inlet chamber links to each other with for example fuel source of fuel tank 23 by fuel channel 22.Fuel channel 22 has pump 24, is used for fuel is pumped into inlet chamber 7 from fuel source.Inlet chamber 7 links to each other with pressure chamber 3 by one or more inlet passages 8.
Return flow line 26 is from the inlet chamber 7 logical fuel source of getting back to.Return flow line 26 has pressure regulator valve 27, is used for the fuel pressure that flows in return flow line 26 is adjusted to the maximum value of requirement.In addition, inlet passage 22 comprises throttle valve 31, return flow line 26 comprise throttle valve 31 ', be used for regulating the fuel flow rate in the passage 22,26.
Piston 4 comprises the end face 9 that defines 3 one sides, pressure chamber.First tilts control limit 10 in 9 settings of piston 4 side proximate end face, has determined that the fuel of jet pump 1 sprays zero-time.The second control limit 11 that tilts also is arranged on piston 4 sides, is used for determining the concluding time that the fuel of petrolift 1 sprays.The second control limit 11 is lower than the first control limit 10.The first control limit 10 and the second control limit 11 are with respect to the plane inclination on the radial direction of piston.The cannelure 19 that extends along the direction of the longitudinal axis 13 of piston is arranged on piston 4 sides.
Jet pump 1 further comprises executive component 14, thereby is used to make piston to rotate the zero-time of adjustment fuel injection and the endurance of injection around its longitudinal axis 13.For example executive component 14 comprises gear that is arranged on around the piston rod and the tooth bar that cooperates therewith, and the longitudinal movement of tooth bar makes piston 4 around its longitudinal axis 13 rotations.
Operating in hereinafter of jet pump 1 is described in more detail.When motor moved, camshaft 15 and cam 16 rotated around the longitudinal axis 18 of camshaft.When piston 4 was in its lower dead centre, fuel passed through inlet passage feed pressure chambers 38 from inlet chamber 7.Piston 4 begins to move upward, and promptly moves to upper dead center from lower dead centre in pressure chamber 3.The first control limit lid 10 of the piston 4 that moves upward has lived to lead to the opening of the inlet passage 8 of pressure chamber 3, finishes by the fuel of inlet passage feed pressure chambers 38 is mobile from inlet chamber 7 thus.After this, flow through discharge route 5 and main flow valve 21 of the fuel in the piston moulding pressure chambers 34 that move upward, and the fuel pressure in pressure chamber 3 is when surpassing the cracking pressure of main flow valve 21, fuel left pressure chamber 3.The fuel stream that flows in the discharge route 5 continues to reach the opening of inlet passage 8 and open this opening up to the second control limit 11 of piston 4.Thereby the fuel pressure in the pressure chamber 3 is discharged into inlet chamber 7 by the cannelure 19 and the inlet passage 8 of piston 4 sides.Piston 4 arrives its upper dead center to begin to move downward in pressure chamber 3 subsequently, and the second control limit 11 covers the opening of inlet passage 8 once more thus.The first control limit 10 arrives the opening of inlet passage 8 and opens this opening near lower dead centre, and fuel is by inlet passage feed pressure chambers 38 thus.After this, piston 4 arrives its lower dead centre and stops for a moment at that, and fuel is by inlet passage feed pressure chambers 38 thus.
When piston 4 when its longitudinal axis 13 rotates, the position on the first control limit 10 changes with respect to the opening of the inlet passage 8 that enters pressure chamber 3.According to sense of rotation, piston 4 in pressure chamber 3 when upper dead center moves, the first control limit 10 can arrive the opening of inlet passage 8 sooner or later.Therefore, the fuel that enters discharge route 5 sprays and can correspondingly begin sooner or later.Therefore, the zero-time of fuel injection can postpone or shift to an earlier date.When piston 4 when its longitudinal axis 13 rotates, the position on the second control limit 11 correspondingly changes with respect to the opening of the inlet passage 8 that leads to pressure chamber 3.Therefore, can arrive the opening of inlet passage 8 to the second control limit 11 of the piston of its upper dead center motion, thus, the fuel that enters discharge route 5 sprays and can correspondingly finish sooner or later sooner or later.Therefore, the concluding time of fuel injection can postpone or shift to an earlier date.The fuel quantity of endurance that the fuel of jet pump 1 sprays and injection cylinder can change by piston 4 is rotated around its longitudinal axis 13.
In Fig. 2, alphabetical A refers to the loading point corresponding to the first control limit 10 and the second control limit 11 of no-load speed.When motor moved with idling speed, piston 4 forwarded this position to, overlapped with the opening of inlet passage 8 in axis 13 directions of piston corresponding to the point on the control limit 10,11 of alphabetical A.Correspondingly, alphabetical D refers to the loading point corresponding to the control limit 10,11 of motor full load (100%).When motor during with oepration at full load, piston 4 forwards this position to, overlaps with the opening of inlet passage 8 in axis 13 directions of piston corresponding to the point on the control limit 10,11 of alphabetical D.The first control limit 10 of piston 4 and the second control limit 11 be form like this so that corresponding to the axial distance between the point of same load, promptly along the distance of piston longitudinal axis 13 directions corresponding to no-load speed A and scope internal linear or the change of substantially linear ground of D at full capacity.Therefore, the effective stroke of piston 4 is in idle running and fully loaded output area internal linear or the change of substantially linear ground.The curve of output of jet pump 1 also is linearity or substantially linear at no-load speed with in the scope at full speed.The first control limit 10 and the second control limit 11 can also promptly be formed as described above in the load range above 100% load corresponding to engine overload.
The fuel of petrolift 1 sprays zero-time and changes as the shape on the first control limit 10 is determined, thus piston 4 idle running A and at full capacity in the scope between the D when its longitudinal axis 13 rotates in advance or postpone (incline section) or remain unchanged (straight section).The second control limit 11 so be shaped so that its corresponding to the shape at the some place of similar load as the shape on the first control limit 10 change.In addition, the first control limit 10 and the second control limit 11 change corresponding to the load range internal linear or the substantially linear ground of distance between idle running A and full load D along piston longitudinal axis 13 directions between the point of same load.Therefore, load range internal linear or the substantially linear ground of the curve of output of the effective stroke of piston 4 and jet pump 1 between idle running and full load changes.
The first control limit 10 of the piston 4 among Fig. 2 is shaped so that in the scope (B-C scope) corresponding to the 60-85% load fuel of jet pump 1 sprays zero-time and compared in advance with the scope (scope A-B) of 60% load corresponding to idle running.The zero-time that fuel sprays is shifted to an earlier date at most in the loading point corresponding to about 80%.Correspondingly, in the scope (scope C-D) corresponding to the 85-100% load, the zero-time that fuel sprays is compared with the scope (scope B-C) of loading corresponding to 60-85% and is delayed.
Piston shown in Figure 2 can be used to the reciprocating engine that uses in the power plant for example, cylinder pressure is remained near its maximum value, thereby realize the optimum efficiency of motor in its operating range commonly used.
The present invention also has and is different from aforesaid embodiment.Jet pump 1 can comprise other passage of branch that is positioned at different heights along the axial direction of piston, is used for fuel is guided into pressure chamber 3 and when spray finishing the pressure of pressure chamber 3 is discharged into inlet chamber 7 from inlet chamber 7.

Claims (4)

1. the piston (4) of the fuel-injection pump of a reciprocating engine (1), comprise that being positioned at first of piston (4) side tilts to control limit (10), be used for determining that the fuel of jet pump (1) under certain engine load sprays zero-time, with the second inclination control limit (11) that is positioned at piston (4) side, be used for determining that the fuel of jet pump (1) under certain engine load sprays the concluding time, wherein, first tilt control limit (10) and second tilt control limit (11) corresponding between the point of same load along the distance of the axial direction (13) of piston (4) corresponding to no-load speed and fully loaded scope internal linear or the change of substantially linear ground, it is characterized in that, first tilts to control limit (10) is formed such that in the load range (B-C) corresponding to 60-85% the zero-time that fuel sprays is compared with the zero-time under the low-load by in advance.
2. piston according to claim 1 (4), it is characterized in that, first tilts to control limit (10) is formed such that in the load range (C-D) corresponding to 85-100% the zero-time that fuel sprays is compared with the zero-time of the load range (B-C) of 60-85% and is delayed.
3. the fuel-injection pump of a reciprocating engine (1) comprises
Cylinder element (2) with pressure chamber (3), this pressure chamber be provided be used for from the pressure chamber (3) remove pressurized fuel discharge route (5) and
The inlet passage (8) that at least one leads to pressure chamber (3) is used for fuel is introduced pressure chamber (3),
It is characterized in that piston according to claim 1 and 2 is located in this pressure chamber (3).
4. jet pump according to claim 3 (1) is characterized in that comprising being used to make the device (14) of piston (4) around its longitudinal axis (13) rotation, in order to change the starting and ending time that fuel sprays.
CN2007800439093A 2006-11-27 2007-11-21 A piston of a fuel injection pump and a fuel injection pump Active CN101542106B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FI20065750A FI119950B (en) 2006-11-27 2006-11-27 Piston engine injection piston for fuel and injection pump
FI20065750 2006-11-27
PCT/FI2007/050630 WO2008065248A1 (en) 2006-11-27 2007-11-21 A piston of a fuel injection pump and a fuel injection pump

Publications (2)

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CN101542106A CN101542106A (en) 2009-09-23
CN101542106B true CN101542106B (en) 2011-08-03

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CN2007800439093A Active CN101542106B (en) 2006-11-27 2007-11-21 A piston of a fuel injection pump and a fuel injection pump

Country Status (5)

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EP (1) EP2087226B1 (en)
KR (1) KR101382066B1 (en)
CN (1) CN101542106B (en)
FI (1) FI119950B (en)
WO (1) WO2008065248A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2669504A1 (en) 2012-05-30 2013-12-04 Caterpillar Motoren GmbH & Co. KG Plunger for an internal combustion engine fuel pump
GB2574455B (en) * 2018-06-07 2021-08-04 Caterpillar Motoren Gmbh & Co Fuel injection system

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT311727B (en) * 1971-11-04 1973-11-26 List Hans Injection pump for diesel engines
US5219280A (en) * 1990-02-09 1993-06-15 Zexel Corporation Fuel injection pump plunger
US5591021A (en) * 1994-11-22 1997-01-07 Robert Bosch Gmbh Fuel-injection pump for internal combustion engines

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1084198A (en) * 1900-01-01
FR1011147A (en) * 1948-12-14 1952-06-19 Prec Mecanique Improvements made to variable flow piston pumps, in particular for fuel injection into engines
JPS5118011B2 (en) * 1972-12-06 1976-06-07

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT311727B (en) * 1971-11-04 1973-11-26 List Hans Injection pump for diesel engines
US5219280A (en) * 1990-02-09 1993-06-15 Zexel Corporation Fuel injection pump plunger
US5591021A (en) * 1994-11-22 1997-01-07 Robert Bosch Gmbh Fuel-injection pump for internal combustion engines

Also Published As

Publication number Publication date
CN101542106A (en) 2009-09-23
FI119950B (en) 2009-05-15
WO2008065248A1 (en) 2008-06-05
EP2087226B1 (en) 2012-07-04
EP2087226A4 (en) 2011-03-02
FI20065750A0 (en) 2006-11-27
KR20090082937A (en) 2009-07-31
KR101382066B1 (en) 2014-04-04
EP2087226A1 (en) 2009-08-12
FI20065750A (en) 2008-05-28

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