CN1096568A - A kind of fuel oil injectionpump that is used for reciprocating internal combustion engine - Google Patents
A kind of fuel oil injectionpump that is used for reciprocating internal combustion engine Download PDFInfo
- Publication number
- CN1096568A CN1096568A CN94101418A CN94101418A CN1096568A CN 1096568 A CN1096568 A CN 1096568A CN 94101418 A CN94101418 A CN 94101418A CN 94101418 A CN94101418 A CN 94101418A CN 1096568 A CN1096568 A CN 1096568A
- Authority
- CN
- China
- Prior art keywords
- pump housing
- cylinder shape
- pump
- end position
- oil
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- 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
-
- 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
- F02M51/00—Fuel-injection apparatus characterised by being operated 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
- F02M59/20—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
- F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The present invention relates to a kind of fuel oil injectionpump, it comprises the plunger (4) of at least one cylinder shape pump housing (3) and axial motion therein.This plunger has the first metering edge (5) and second metering edge (7) that decision pump oil finishes of decision pump oil beginning, and two metering edge cooperatively interact with the hole (6) that is arranged in the wall of the cylinder shape pump housing (3) and work, and this hole is connected to oil inlet passage (12) and release of pressure passage (13).This cylinder shape pump housing (3) can be arranged between the position, two end part in the pump housing (1) with axial motion.There is a hydraulic coupling (in the chamber 25) to be applied to it for the cylinder shape pump housing being remained on the one end position, and then can removes this pressure if make this cylinder shape pump housing be in its position, the other end.
Description
The present invention relates to a kind of fuel oil injectionpump that is used for reciprocating internal combustion engine, but it has at least one axial motion and contain the plunger of the cylinder shape pump housing and an axial motion therein of a pump chamber in the pump housing, this plunger pump comprises the first metering edge and second metering edge that definite pump oil finishes of definite pump oil beginning, and two metering edge all cooperatively interact with the hole of the wall that is arranged in the cylinder shape pump housing and work, this hole is connected on oil inlet passage and the release of pressure passage, therefore, the cylinder shape pump housing can be from an end position setting in motion away from the hydraulic coupling on the front surface of plunger actuation side by means of acting on.
Such fuel oil injectionpump is open by EP-A267894.In this class fuel oil injectionpump, pump and oil nozzle constitute an overall structure unit.The purpose of the movable cylinder shape pump housing is to change the fuel injection beginning time, promptly under the continuous control situation, by means of making the pump housing according to running parameter, as speed, boost pressure, therefore the requirement of temperature and/or load and move and change the fuel injection beginning time provides a control corresponding for hydraulic medium.Make the cylinder shape pump housing overcome spring pressure by means of hydraulic coupling and move, this spring is along the described end direction cylinder pressure shape pump housing.In known fuel oil injectionpump, available hydraulic power and spring force substitute in the past the cylinder shape pump housing are only used simple mechanical adjustment.
Fuel oil injectionpump of the present invention is based on other imagination.Along with the continuous operation of internal-combustion engine, oil spout early produces economic running, promptly low oil consumption, and the nitrogen oxides of waste gas (NOx) content is higher than the limiting value that some national environmental protection rules provides slightly.If reciprocating internal combustion engine is oceangoing voyages as the power engine and the boats and ships of boats and ships, so this situation will take in, if the fuel injection beginning point moves to more near upper dead center, then the nitrogen oxides of waste gas (NOx) content can reduce.
The present invention's purpose is to improve the Injection Pump of aforementioned type, this pump can be made two kinds of different drive manners selectively, promptly or be the economic drive manner (oil spout early) or the drive manner (retarded injection) of low NOx content, see that from the viewpoint of structure two kinds of drive manners all carry out in a simple manner.
This purpose so realizes according to the present invention, be that the cylinder shape pump housing can be moved to the second end position by action of hydraulic force and be held in this end position by described trying hard to keep, if and if this cylinder shape pump housing when being in its described first end position this power can remove by the selector valve that moves in the hydraulic medium supply lines.The cylinder shape pump housing that this can move between the position, two end part guarantees that this jet pump can promptly easily switch to or early commencement of fuel injection or later commencement of fuel injection, whether this depends on this reciprocating internal combustion engine is with low oil consumption rate but high slightly NOx content navigates by water on open sea, still navigate by water in the waters, beach with the drive manner that environment is had littler harm, correspondingly in waste gas, contain NOx content still less.
Below by means of accompanying drawing some embodiments of the present invention are elaborated.
Fig. 1 shows the axial sectional view by fuel oil injectionpump, and wherein, the cylinder shape pump housing is in an end position,
Fig. 1 a shows the section axial sectional view by fuel oil injectionpump, and wherein, the cylinder shape pump housing is arranged in position, the other end,
Fig. 2 shows improved injection pumping cylinder shape, and it is corresponding to the axial sectional view of Fig. 1;
Fig. 3 shows another improved injection pumping cylinder shape, and it is corresponding to the axial sectional view of Fig. 1;
Fig. 4 shows another improved injection pumping cylinder shape, and it is corresponding to the axial sectional view of Fig. 2.
As shown in Figure 1, this fuel oil injectionpump comprises a pump housing 1, and end is sealed up by lid 2 on this pump housing, be furnished with a cylinder shape pump housing 3 in the pump housing 1, but the plunger 4 of axial motion stretches under Fig. 1 this cylinder shape pump housing 3.The lower end of the plunger 4 among Fig. 1 controllably is connected on the camshaft drive in known manner, it is not illustrated in greater detail here.The upper end of plunger constitutes the first metering edge 5, itself and hole 6 effect of cooperatively interacting that extends laterally across the cylinder shape pump housing 3, and the beginning of definite pump oil among Fig. 1.The lower part of the first metering edge 5 in Fig. 1, plunger 4 comprise the second metering edge 7 that extends obliquely with respect to plunger axis, this edge also with hole 6 effect of cooperatively interacting and the end of definite Injection Pump pump oil.Be the pump chamber 8 of Injection Pump above the end face of the plunger 4 that constitutes metering edge 5 among Fig. 1, this pump chamber is extended into center protrusions 9 in the hole of the cylinder shape pump housing and limits and form by the cylinder shape pump housing 3 and lid 2.Center tube 10 extends out from pump chamber 8 by covering 2, its upper end is connected on the high-pressure oil passage (not shown), this oil circuit draws on the nozzle of the reciprocating internal combustion engine that is connected to diesel version, and connects a stroke ground through stroke of this nozzle fuel oil is sprayed in the working cylinder of motor.This reciprocating internal combustion engine is used as the power engine of marine vessel.
In the zone of pump chamber 8, gusset is wound with annular space 11 outside the cylinder shape pump housing 3, and the transverse holes 6 of the cylinder shape pump housing 3 is opened and entered in this gap.Be located at a passage 12 in the pump housing 1 and also open and enter this annular space 11, fuel oil infeeds through this passage by unspecified known mode (along arrow A).Passage 13 and an oil circuit (not shown) through being located on the pump housing 1 is back to oil sump tank (along the arrow B direction) to Fuel Remained from annular space 11.
In Fig. 1 in the annular space 11 bottom, on the pump housing 1, be provided with an annular pressure chamber 15, (separating) with annular space 11, the passage 16 of this pressure chamber 15 in being located at the pump housing 1 is connected on the hydraulic medium supply lines 17, in the zone of pressure chamber 15, the outer diameter D of this cylinder shape pump housing 3 reduces to diameter d, therefore constitutes a convex shoulder 18 at this, and this convex shoulder is positioned on the plane type anchor ring 19 of pressure chamber 15 in Fig. 1.This anchor ring 19 comprises that a diameter group d is big, but the outer diameter D' littler than the outer diameter D of the cylinder shape pump housing.Tell a branch road 20 from supply lines 17.In this branch road 20, comprise one or two logical selector valve 21 and feed in the passage 22, this passage 22 be arranged in the cylinder shape pump housing 3 upper area the pump housing 1 and open pressure chamber 25.This pressure chamber 25 between the cylinder shape pump housing 3 upper-end surfaces and the lid 2, and is a disc-annular shape in Fig. 1, and has an outer diameter and that equals the outer diameter D of the cylinder shape pump housing 3 and equal to cover 2 inner diameters of outer diameter d' that stretch into the extended portion 9 of the cylinder shape pump housing.
The working condition of this Injection Pump is described below: in the position of selector valve shown in Figure 1 21, hydraulic medium is introduced pressure chamber 15 and pressure chamber 25.Because by the area difference (D-D') of the pressure medium effect end area (D-d') less than the cylinder shape pump housing in the upward pressure chamber 25, therefore, because the advantage of pressure in the upward pressure chamber 25, the cylinder shape pump housing is pressed on the anchor ring 19 on convex shoulder 18.Because plunger 4 moves upward, therefore, be enclosed in fuel oil in the pump chamber 8 and carve in the top limit position of transverse holes 6 at the first metering edge 5 and begin to rise to elevated pressures.Simultaneously, this fuel oil is delivered to the nozzle of having mentioned through central passage 10, then, through this nozzle fuel oil is sprayed into working cylinder when jet pressure reaches.When the limit inferior position of the second metering edge 7 by transverse holes 6, spray and stop.At this moment, fuel oil in pump chamber 8 produces pressure and discharges, and fuel oil energy is through transverse holes 6, and annular space 11 and passage 13 flow away.When ship navigates by water in open sea, described fuel injection beginning, therefore, this moment, the drive manner of power engine depended on efficient, this moment, the content of NOx was quite high, if ship is near pulling in to shore, at this moment because environmental regulations has determined the drive manner of power engine, promptly require alap NOx content, so selector valve 21 manually or pneumatically or move to the right by electrical signal and enter position shown in Fig. 1 a.In this position, upward pressure chamber 25 releases of pressure, hydraulic medium flows out in the oil sump tank from this chamber.The pressure medium supplied with of via line 17 only acts on the convex shoulder 18 in the downforce chamber 15 then.Therefore, the cylinder shape pump housing 3 moves upward, until the upper-end surface of the cylinder shape pump housing be against cover on 2 till.Therefore, crosspassage 6 also moves upward, and because plunger 4 also moves upward, so pump oil also begins, and oil spout takes place than a little later in the past, because need when longer the chien shih first metering edge 5 by the limes superiors position of crosspassage 6.Therefore, it is lower to leave the content of NOx of waste gas of power engine.This position of the cylinder shape pump housing 3 is kept until ship and is left the waters, beach once more.Then, return back to position shown in Figure 1 by means of suffering to valve 21, the cylinder shape pump housing 3 moves to its lower end position more again, after this just inscribes work again when fuel injection beginning early.
In embodiment illustrated in fig. 2, the pressure chamber of this below and annular space 11 are an integral body, therefore, convex shoulder 18 is by the fuel pressure effect in the annular space, and a circuit 31 that contains one or two logical selector valve 32 is connected on the passage that causes upward pressure chamber 25 22 of the pump housing 1.This circuit 31 and pressure chamber 25 can be connected on the circuit 33 so that provide hydraulic medium through two way selected valve 32.
From Fig. 2, can see, exist pressure medium to connect in selector valve 32 shown positions, so the pressure medium that is present in the pressure chamber 25 makes the cylinder shape pump housing 3 remain in lower position (overcoming the fuel pressure that acts on the convex shoulder 18).This Injection Pump is worked as described in Figure 1, promptly along with early fuel injection beginning constantly and oil spout, at this moment ship is in open ocean navigation.If ship enters the waters, beach, selector valve 32 moves to the right of Fig. 2, so circuit draws and 25 releases of pressure of pressure chamber subsequently.Fuel pressure on convex shoulder 18 makes the cylinder shape pump housing 3 move to its upper end position at this moment, promptly corresponding to the position shown in Fig. 1 a.So far, the transverse holes 6 in the cylinder shape pump housing 3 is in the position higher than the position shown in Fig. 2, so the pump fry dried food ingredients of Injection Pump is living later, and the NOx that forms reduces.
In the embodiment shown in Fig. 1 and 2, via line 17 and 33 hydraulic mediums of supplying with can be diesel oil, but it is to separate with the diesel oil of supplying with Injection Pump through passage 12 to supply with.In the embodiment shown in fig. 3, its hydraulic medium is that branch comes out from the diesel oil of supplying with Injection Pump.Be this purpose, therefore be provided with a passage 36 in the pump housing 1 in the zone of annular space 11, one circuit 37 is connected on this passage 36 and connects in the passage 22 that is connected on the upward pressure chamber 25 by one or two logical selector valve, and the opposite of passage 22 is provided with one and also is communicated with pressure chamber 25 and is connected to passage 39 on the circuit 40 in the pump housing 1.This passage 39 is connected among the circuit 13' that goes into to be connected on the fuel oil discharge route 13.In circuit 13' and 40, have throttle point 41 and 42 respectively.
In selector valve shown in Figure 3 38 positions, the part fuel oil via line 37 that is conducted to Injection Pump through passage 12 is conducted to upward pressure chamber 25.The fuel pressure that acts on this pressure chamber forces the cylinder shape pump housing 3 to enter its lower position, this corresponding to early fuel injection beginning constantly, promptly ship navigates by water the situation on the main sea.When ship entered the waters, beach, the selector valve 38 among Fig. 3 moved to the right, its result, and pressure chamber 25 releases of pressure, the fuel pressure that acts on the convex shoulder 18 makes the cylinder shape pump housing 3 be moved into its upper end position at this moment, as shown in Figure 1a.Owing to designed passage 39, circuit 40 and two throttle point 41 and 42 have guaranteed that fuel oil flows through the pressure chamber 25 of the position that is in the cylinder shape pump housing 3 shown in Figure 3 unchangeably.
Embodiment shown in Figure 4 is to a great extent corresponding to embodiment shown in Figure 2, yet the hydraulic coupling that acts among Fig. 2 on the convex shoulder 18 is replaced by helical spring 30.This spring 30 centers on the lower end of plunger 4 and is pressed on the lower end surface of the cylinder shape pump housing 3 among Fig. 4.In this embodiment, saved special ring surface in the pump housing 1 of convex shoulder 18 bottoms.
Shown in the position of selector valve 32 time when oil pump is worked the cylinder shape pump housing 3 be under pressure in the chamber 25 action of hydraulic force and remain on the lower end position, this is corresponding to fuel injection beginning earlier.When ship entered the waters, beach, selector valve 32 shown in Figure 4 moved to the right, pressure chamber 25 releases of pressure thus.Then, the pressure of helical spring 30 is pressed into its upper end position with the cylinder shape pump housing, so the fuel injection beginning generation is later.
Claims (5)
1, a kind of with the Injection Pump in the reciprocating internal combustion, have at least one can be loaded in the pump housing with axial motion and contain the cylinder shape pump housing and of a pump chamber can be therein each plunger movable of axle, this plunger comprises the first metering edge and second metering edge that decision pump oil finishes of decision pump oil beginning, and the hole in two metering edge and the cylinder shape pump housing wall cooperatively interacts and works, this hole is connected on oil inlet passage and the release of pressure passage, therefore, this cylinder shape pump housing can is characterized in that from an end position setting in motion by means of acting on away from the hydraulic coupling on the end face of plunger actuation side: this cylinder shape pump housing can be moved to a second end position and be remained in this end position by this hydraulic coupling by action of hydraulic force; And if when making this cylinder shape pump housing be in its described first end position, then can remove this hydraulic coupling by the selector valve in the mobile hydraulic medium supply lines.
2, Injection Pump as claimed in claim 1 is characterized in that, the first end position of the cylinder shape pump housing is the position of later commencement of fuel injection.
3, Injection Pump as claimed in claim 2, it is characterized in that, for this cylinder shape pump housing is remained in described first end position, also have a lip-deep hydraulic coupling that acts on the adjacent plunger actuation side of the cylinder shape pump housing, this surface ratio has littler diameter away from the end face of the driving side of plunger.
As the described Injection Pump of one of claim 1 to 3, it is characterized in that 4, the fuel pressure of supplying with Injection Pump is as hydraulic coupling.
5, Injection Pump as claimed in claim 2 is characterized in that, for the cylinder shape pump housing is remained in described first end position, provides a lip-deep spring force that acts on the cylinder shape pump housing of adjacent plunger actuation side.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP93810077.3 | 1993-02-08 | ||
| EP93810077A EP0610641B1 (en) | 1993-02-08 | 1993-02-08 | Fuel injection pump for an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1096568A true CN1096568A (en) | 1994-12-21 |
Family
ID=8214915
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN94101418A Pending CN1096568A (en) | 1993-02-08 | 1994-02-07 | A kind of fuel oil injectionpump that is used for reciprocating internal combustion engine |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0610641B1 (en) |
| JP (1) | JPH10205411A (en) |
| KR (1) | KR100283932B1 (en) |
| CN (1) | CN1096568A (en) |
| DE (1) | DE59307709D1 (en) |
| DK (1) | DK0610641T3 (en) |
| FI (1) | FI106397B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1312395C (en) * | 2003-12-12 | 2007-04-25 | 上海交通大学 | Sealing device for common rail Injector of diesel engine |
| CN100487234C (en) * | 2002-11-21 | 2009-05-13 | 洋马株式会社 | Fuel injection pump |
| CN109196214A (en) * | 2016-04-08 | 2019-01-11 | 德尔福知识产权有限公司 | Petrolift |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19719800C1 (en) * | 1997-05-10 | 1998-12-17 | Kurt Wilhelm | Injector for free piston engine |
| US6773240B2 (en) | 2002-01-28 | 2004-08-10 | Visteon Global Technologies, Inc. | Single piston dual chamber fuel pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0095026B1 (en) * | 1982-03-25 | 1985-06-26 | Deere & Company | Injector pump unit with a sleeve-valve controlled floating piston for internal-combustion engines |
| EP0267894A1 (en) * | 1986-10-30 | 1988-05-18 | VOEST-ALPINE AUTOMOTIVE Gesellschaft m.b.H. | Pump nozzle unit for fuel injection into an internal-combustion engine |
| US5090378A (en) * | 1991-02-22 | 1992-02-25 | The Cessna Aircraft Company | Dual nozzle single pump fuel injection system |
-
1993
- 1993-02-08 DE DE59307709T patent/DE59307709D1/en not_active Expired - Fee Related
- 1993-02-08 EP EP93810077A patent/EP0610641B1/en not_active Expired - Lifetime
- 1993-02-08 DK DK93810077.3T patent/DK0610641T3/en active
-
1994
- 1994-02-01 KR KR1019940001826A patent/KR100283932B1/en not_active IP Right Cessation
- 1994-02-07 CN CN94101418A patent/CN1096568A/en active Pending
- 1994-02-07 FI FI940546A patent/FI106397B/en not_active IP Right Cessation
- 1994-02-08 JP JP6014700A patent/JPH10205411A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100487234C (en) * | 2002-11-21 | 2009-05-13 | 洋马株式会社 | Fuel injection pump |
| CN1312395C (en) * | 2003-12-12 | 2007-04-25 | 上海交通大学 | Sealing device for common rail Injector of diesel engine |
| CN109196214A (en) * | 2016-04-08 | 2019-01-11 | 德尔福知识产权有限公司 | Petrolift |
Also Published As
| Publication number | Publication date |
|---|---|
| FI940546A (en) | 1994-08-09 |
| FI940546A0 (en) | 1994-02-07 |
| KR940019984A (en) | 1994-09-15 |
| DE59307709D1 (en) | 1998-01-02 |
| DK0610641T3 (en) | 1997-12-22 |
| KR100283932B1 (en) | 2001-10-22 |
| EP0610641A1 (en) | 1994-08-17 |
| EP0610641B1 (en) | 1997-11-19 |
| FI106397B (en) | 2001-01-31 |
| JPH10205411A (en) | 1998-08-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0691471B1 (en) | Pressure storage fuel injection system | |
| US4782794A (en) | Fuel injector system | |
| US5012786A (en) | Diesel engine fuel injection system | |
| US4280464A (en) | Fuel injection control system for internal combustion engine | |
| KR20050033575A (en) | Large two-stroke diesel engine of the crosshead type | |
| CN101137832A (en) | Gaseous fuel direct injection system | |
| AU641800B2 (en) | Fuel injection type multiple cylinder engine unit | |
| CN105020079B (en) | With starting the large-sized low-speed turbocharging two-stroke of air system from internal combustion engine | |
| US5645030A (en) | Motorbrake for a diesel engine | |
| WO2010145652A1 (en) | A large turbocharged two-stoke diesel engine running on a fuel mixture of two or more fuel components | |
| CN102691604A (en) | Multi-stage boosting electric-control common-rail oil injection system | |
| CN1096568A (en) | A kind of fuel oil injectionpump that is used for reciprocating internal combustion engine | |
| CN1085773C (en) | Hydraulic system for two-stroke crosshead engine | |
| US6131503A (en) | Piston ring assembly | |
| US6009854A (en) | Arrangement for a injection pump in an internal combustion engine | |
| CN1089401C (en) | Method for operation of hydraulically actuated fuel pump for internal combustion engine, and hydraulically actuated fuel pump | |
| JPS5738629A (en) | Fuel injection control apparatus for multicylindered diesel engine | |
| CN1081740C (en) | Fuel injection pump for IC engines, in particular big, slow marine diesel engines | |
| CN103527374B (en) | Coil-induced pump | |
| WO1995028559A3 (en) | Emulsion running mode for a diesel engine | |
| CN109209709A (en) | Electric control fuel oil jet system with fluid power compensating piston | |
| CN111512035B (en) | Method for operating an internal combustion engine | |
| CN1639458A (en) | Installation for the pressure-modulated formation of the injection behavior | |
| US20010040346A1 (en) | Piston ring assembly | |
| CN1049953C (en) | Hydraulic booster and speed-increasing short time fuel injection piston pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C01 | Deemed withdrawal of patent application (patent law 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |