CN1175993A - Fuel-injection pump for IC engines - Google Patents
Fuel-injection pump for IC engines Download PDFInfo
- Publication number
- CN1175993A CN1175993A CN96192123A CN96192123A CN1175993A CN 1175993 A CN1175993 A CN 1175993A CN 96192123 A CN96192123 A CN 96192123A CN 96192123 A CN96192123 A CN 96192123A CN 1175993 A CN1175993 A CN 1175993A
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- Prior art keywords
- valve
- pressure
- pump
- controlled
- fuel
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- Granted
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- 238000002347 injection Methods 0.000 title claims abstract description 49
- 239000007924 injection Substances 0.000 title claims abstract description 49
- 230000001105 regulatory effect Effects 0.000 claims description 28
- 238000002485 combustion reaction Methods 0.000 claims description 17
- 230000000694 effects Effects 0.000 claims description 8
- 230000005540 biological transmission Effects 0.000 claims description 6
- 230000001276 controlling effect Effects 0.000 claims description 4
- 230000009471 action Effects 0.000 claims description 3
- 230000000087 stabilizing effect Effects 0.000 claims 4
- 241000628997 Flos Species 0.000 claims 2
- 240000000233 Melia azedarach Species 0.000 claims 1
- 230000001143 conditioned effect Effects 0.000 claims 1
- 239000000446 fuel Substances 0.000 abstract description 12
- 238000010420 art technique Methods 0.000 abstract 1
- 239000000463 material Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000033228 biological regulation Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005485 electric heating Methods 0.000 description 1
- 239000000295 fuel oil Substances 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/16—Adjustment of injection timing
- F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
- F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/16—Adjustment of injection timing
- F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/16—Adjustment of injection timing
- F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
- F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
- F02D2001/186—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic using a pressure-actuated piston for adjustment of a stationary cam or roller support
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Abstract
A fuel-injection pump, in which adjustment of the moment injection begins is carried out by a device (31) which is actuated by the fuel pressure in the interior (12) of the pump, this pressure being controlled as a function of certain operating parameters. The pressure is controlled as a function of engine rpm using prior art techniques and is also increased by means of a first pressure-control device (49), via a pressure-control valve (39), so that, when the engine is cold, the beginning of injection is advanced more than usual. The pressure is also controlled as a function of the load on the engine by a second device (50) so that, when the engine is warm, the beginning of injection is retarded relative to the normal setting. Since this does not produce the required results in all engine-operating regimes, the second pressure-control device (50) is controlled as a function of temperature to cut out during cold starting and switch in when the engine is warm, via an electromagnetic valve (66).
Description
Technical background
The present invention relates to fuel-injection pump for IC engines mentioned in the preamble of claim 1, this fuel-injection pump that is disclosed among the DE-A1-4341932, the reset space of its pressure controlled valve are from a certain definite temperature, by a control valve unloading.Should determine that temperature was equivalent to the temperature in the internal combustion engine operation.Light from this work, pressure controlled valve is controlled rpm-dependent pump chamber pressure in the mode of regulation, to regulate the time of injection beginning.Use this known devices, can make the injection beginning time of cold internal-combustion engine only relevant with temperature.
Advantage of the present invention
Compare with above-mentioned, fuel-injection pump with feature described in the claim 1, its advantage is, irrelevant with the control of the controlled valve that depends on temperature, realized that the pump chamber pressure of being adjusted voluntarily by itself causes the unloading of reset space, the working method of pressure controlled valve is transformed into can adapt to the needed working method of the internal-combustion engine that reaches operating temperature, and irrelevant with the real true temperature of internal-combustion engine.Therefore, under the situation that rotating speed increases, pressure controlled valve is not at internal-combustion engine the control action of injection beginning time under the situation of operating temperature and has been cut off, this special operational mode of pressure controlled valve is subjected to the restriction of rotating speed in other words, under high-revolving situation, the adjusting of the injection beginning time that this is special is unnecessary (KSB=cold start-up acceleration).
According to claim 2, a very favourable new development of the present invention is, the control of the control of controlled valve and pump chamber pressure is advantageously combined, make pump chamber pressure not only relevant with load to the influence of control injection beginning time, and relevant with temperature and rotating speed.Stop valve is made the guiding valve form, makes its switch of accurate adjusting become possibility.Described in other favourable formation situations of the present invention such as the claim 3 to 6, its advantage is further accurately control pump cavity pressure.At this moment, compare with the prior art equipment, the extra part that enlarges of the present invention can constitute integral body in simple mode with many existing component.
Description of drawings
Accompanying drawing is depicted as three embodiments of the present invention, and in explanation in detail subsequently.
Fig. 1 is the longitudinal sectional drawing of fuel-injection pump.
Fig. 2 shows main invention parts of the present invention on the fuel-injection pump according to Fig. 1, comprises regulating sleeve, injection beginning regulator, pressure controlled valve and first embodiment's pressure regulator.
Fig. 3 is the structural type that slightly changes with Fig. 2 embodiment.
Fig. 4 is the third structural type of the present invention, has a piston valve that installs separately.
Detailed description to embodiment
On the fuel spray distribution pump shown in Figure 1 a pump piston 1 is housed in a well-known manner, a cam disk 2 that drives and rotate by the transmission shaft 3 of fuel-injection pump, move on the roller 5 of roller circle 6 by its cam locus 4, make pump piston 1 be in a kind of motion state toward the redoubling rotation.At this moment, owing to pump piston 1 is rotating, so it plays a part distributor simultaneously.Pump piston constitutes a pump working chamber 9 with an end of the cylindrical cavity that is installed in the cylindrical body 8 in the fuel-injection pump housing 7.When pump piston is in induction stroke, pump working chamber 9 is by sucking groove 10 and intake line 11, begin in pump chamber 12, to suck fuel, and when pump piston is in compression stroke, fuel begins from pump piston 1 end face, transfers to a plurality of pressure pipings 16 through pipe tunnel 14 with the distribution groove 15 that links to each other with pipe tunnel 14.These pressure pipings 16 are to leave cylindrical cavity, and by well-regulated certain distance be arranged in respectively pump piston 1 around, lead to the fuel oil nozzle that does not add performance among the figure through corresponding pressure valve 17 separately.The fuel quantity of fueling oil nozzle is determined by slip spool valve 18 position in the axial direction.This valve and can be done and vertically moves on pump piston 1 part outstanding in pump chamber 12.The end rib of slip spool valve 18 will be opened a cross through hole 19 that links to each other with pipe tunnel 14 from certain pump piston current drainage stroke, makes pump working chamber 9 to the pump chamber unloading, and finishes the high-pressure jet stage at this point.The position of slip spool valve 18 is by speed regulator 20 controls.This regulator 20 has an adjustment (adjusting) lever 21, and its on the one hand and 18 couplings of slip spool valve is subjected to the load of Regulation spring 22 on the other hand, can add in various degree prestressing force for spring 22 by adjustment (adjusting) lever 23.The Regulation spring opposite, there is the regulating sleeve 24 of a centrifugal revolution transmitter 25 to work, its governor weight 26 is driven through gear drive 27,28 by transmission shaft 3, and increases with revolution regulating sleeve 24 is pushed to rightabout sleeve carrier 30 directions with Regulation spring 22 power.
In addition, be the regulating and controlling fuel-injection pump injection beginning time, an injection beginning regulator 31 is housed on the pump.What represent among the figure is its overturn in paper state of 90 °.It has an injection beginning regulating piston 32, and the one end forms a working room 33 in a cylindrical cavity, is subjected to the active force of Returnning spring 34 on the other end.Injection beginning regulating piston 32 is coupled with roller circle 6 by a connecting rod 36 that is placed within the pump case, during connecting rod 36 turns, the stroke of cam disk 4 is begun, and by this early or late by the turn direction, look the position, angle of transmission shaft 3 or the turn position difference of pump piston, the stroke that drives pump piston 1 begins.To the adjusting of injection beginning regulating piston 32 are pressurized media implementation by sending into working room 33, and this medium is through the throttling connecting passage input service chambers 33 37 in injection beginning regulating piston 32.At this moment, pump chamber 12 is as pressure source.Fuel is not only imported pump chamber 12 by a transfer pump 38, also offers pump working chamber 9 simultaneously.Transfer pump 38 is driven synchronously by transmission shaft 3.Pressure in the pump chamber 12 except that the working pressure of transfer pump raises with revolution, the control of the control valve 39 that additionally is under pressure.Control piston 40 as control unit is arranged on this valve, be placed in and can in cylindrical hole 51, move, limit a pressure chamber 41 that links to each other with pump chamber 12 on the one end face, be subjected to the effect of the power of spring 42 on its another end face, itself and pressure chamber 41 adjacent end face control pump chambers 12 lead to a drainage port 43 of a relief chamber.This relief chamber can be the suction side of fuel transfer pump 38 under current state, and perhaps the fuel reserve container 44.As reset space and the space 54 that holds spring 42, connect together by throttling passage 45 and the pressure chamber 41 that is positioned at control piston, and connect together by unloading pipe 46 and one a controlled valve 52.To do more detailed statement to this among Fig. 2 to Fig. 4.
A spray distribution pump that has a cam disk and a roller circle has been described in the front.It is adjusted by injection beginning regulator 31, so that adjust the injection beginning time.Adopt the also cam drive of the jet pump of other distribution forms of can regulate of this injection beginning regulator, for example, the cam ring of radial piston pump or other devices are for example adjusted the state status of series pump (Reihenpumpen) overhead cam with respect to transmission shaft.Say in principle, both can adjust and be in parts stationary state, that cam is arranged usually, also can adjust, to meet the requirements of the result who adjusts injection beginning point as the parts inswept cam locus of cam follower, carrier roller.
Because pump chamber pressure can be controlled by pressure controlled valve, particularly controlling it makes it to increase with the rotating speed raising, therefore can be with pump chamber pressure as the means of regulating the injection beginning regulator pilot pressure of injection beginning regulator in other words, this regulator is regulated the injection beginning point equally with the revolution that increases via its regulating piston and cam drive.Known, except that revolution, can also attach by other parameters influences pressure in the pump chamber, reaches definite function that jet pump is regulated injection beginning point.For this reason, introduce a number relevant especially with load.This method is that a throttle valve that can change 47 is set on regulating sleeve 24.It is the opening in this orifice sleeve barrel, in the process of regulating regulating sleeve 24, this opening also is communicated with the current drainage pipeline 48 in sleeve 24 carriers gradually, and this current drainage pipeline leads to relief chamber through controlled valve 52, i.e. the suction side of fuel transfer pump 38 fuel reserve container 44 in other words.
Show the pressure controlled valve 39 that constitutes first pressure control device 49 with controlled valve 52 among Fig. 2 in more detail.Here have one to pump chamber pressure produce added influence, by second pressure control device 50 that throttle valve 47 and regulating sleeve 24 constitute, the fuel quantity relevant with load will be shunted away in pump chamber by them.Controlled valve 52 is to be placed in the relief passage 46 of reset space 54.This valve 52 is made of the one way stop peturn valve of a usefulness one spheroid 56 as closure member.Closure member 56 remains on the locking direction by adding certain prestressed spring 57.At this moment, controlled valve 52 is controlled by a characteristic quantity that characterizes engine temperature.This process is to realize by its working state expanding material element 59 relevant with temperature in exemplary embodiments shown in Figure 2.It for example can temporarily interrupt its work because of the cooling water temperature of internal-combustion engine, is as the criterion with temperature or a certain equivalent parameters in other words and carries out electric heating.It promotes a slide-valve component 61 and is moved.This slide-valve component 61 again as piston be installed in one with the coaxial hole 62 of controlled valve 52 in, can in the hole, move, and be subjected to the effect that Returnning spring 63 points to the power of expanding material elements 59.Slide-valve component 61 extends with the form of regulating lever 64, and at one end be that unloading pipeline 46, the other end are holes 62 in the axial direction, outstanding in the pipeline that is interconnected, make when promoting slide-valve components 61 and be moved by expanding material element 59, regulating lever 64 contact spheroids 56 and its jack-up from its fixed position, thereby control valve is opened, unloading pipeline 46 is communicated with relief chamber 44.
Slide-valve component 61 is being controlled the blowdown piping 48 of second pressure control device 50 simultaneously, and this pipeline receives that like this control of the situation of hole 62 inside is: during cold internal-combustion engine, slide-valve component 61 is in position shown in Fig. 2, and passage is sealed.During hot internal-combustion engine, for opening controlled valve 52, slide-valve component 61 is removed channel connection jointly with regulating lever 64.Blowdown piping 48 leads to relief chamber 44 from 62 beginnings of hole through electromagnetic switch valve 66.This valve 66, after slide-valve component 61 was opened blowdown piping 48, its off position on positi in other words was just very important, will be subjected to other Operational Limitss of internal-combustion engine, rather than temperature controlling.
In order to limit the influence to pump chamber 12 internal pressures in off position time of controlled valve 52, to regulating the influence of injection beginning point, additionally add a stop valve 106 in other words, it has a slide member 107, this slide member 107 is installed in the cylindrical hole densely, and slidably.Cross a working space 109 in the end of slide member 107, this space connects together with pump chamber 12 all the time by shutoff valve 108.The adjusting power that the another side of working space 109 has the pressure spring that can regulate separately 110 to form acts on the slide member 107.A passage 111 is arranged in the slide member 107.When slide member 107 was done respective offsets against the power of spring 110, passage 111 can communicate with connecting passage 112.Passage 112 is connected with unloading pipeline 46, therefore is connected together with reset space 54 all the time.On the other hand, passage 111 leads to the space that holds spring 110, and this space links to each other with fuel reserve container 44 with relief chamber in other words by a pipeline 114.This shutoff valve 106 is parts of first pressure control device 49, can accomplish when the internal pressure of pump chamber 12 reaches a certain size with it, sets up reset space 54 and unloads the unloading that cuts between the chamber 44 and get in touch.This situation always occurs in when reaching certain rotating speed regularly.Under this revolution, it is unnecessary adjusting the special in other words adjustment injection beginning point of injection beginning point in advance, because at this moment, and the hot state when internal-combustion engine in fact still is not operation.Can be limited in certain rotating speed by starting of these stop valve 106, the first pressure regulators 49, this revolution can be drawn by the pump chamber pressure inside.
According to the layout among Fig. 2, cutting off the influence that is applied with the relevant pump chamber pressure of loading is by means of slide-valve component 61, realizes by the controlled throttle valve in regulating sleeve 24 47.The regulating lever 64 that is used to operate spheroid 56 connects together with slide-valve component 61.In this layout, pipeline 48 to the connection of relief chamber 44 is controlled by temperature fully.But according to the layout of Fig. 3, cutting off this path is by the parts on the spherical one way stop peturn valve 156,161,157, and current drainage pipeline 48 is closed realization.The spheroid one way stop peturn valve of the spherical valve element form among Fig. 2 also comprises a slide-valve component 161 by one among Fig. 3 now, and around it fluted assembly parts replaces.Spheroid 156 is by slide-valve component 161, and being subjected to blocking force on the locking direction is the pressure of pressure spring 157.On this position, the slide-valve component that slides in cylindrical cavity 161 is the current drainage pipeline 48 by this cylindrical cavity and getting in touch between the pipeline 65 of solenoid valve 66 is housed cut off.If the spheroid one way stop peturn valve is opened under the influence that reset space 54 internal pressures increase, at this moment, as long as connecting tube 112 is closed, this pressure is pump chamber pressure just, then current drainage pipeline 48 also will be communicated with between the pipeline 65, make that under the situation that solenoid valve 66 opens circuit unloading becomes possibility to relief chamber, the pump chamber pressure relevant with load is had an effect.In such a way, the effect of the pump chamber pressure relevant with load will be by the accessible actual state control of internal-combustion engine, needn't the special adjustment injection beginning time under this state, the effect of especially relevant with load pump chamber pressure is basically only when internal-combustion engine reaches desired operating temperature, spherical one way stop peturn valve 156 constantly raises up by expanding material element 59, could realize.
Shown in Figure 4 is the distribution form of another kind of relevant this influence mode.At first shown in pressure control device among Fig. 2 49, present embodiment and its difference are in the pressure control device 249 as shown in Figure 4, have one to be contained in cylindrical cavity 101 interior, transportable piston valves 100 to first pressure control device.The one end is subjected to the pressure of Returnning spring 103, and the other end crosses a working space 102 in the cylindrical cavity 101 of sealing, links to each other with unloading pipe 46 and reset space 54 all the time.By the pressure in the reset space 54, piston valve 100 can be pushed to pin 104 places facing to the power of Returnning spring 103, makes and is sealed by piston valve through the connecting passage of cylindrical cavity 101 connections, can not continue to be communicated with.The eigenvalue that if the pressure in the reset space 54 drop to internal-combustion engine when normally moving, that is to say, not that expanding material element 59 has been opened the spherical one way stop peturn valve of having known 256 from Fig. 2, by the pump chamber pressure that increases stop valve 106 has been opened exactly, then also just unloading thereupon of working space 102, connecting tube 48 and leading between the pipeline 65 of relief chamber 44, under the situation that solenoid valve 66 opens circuit also with connection.The influence that this layout is equally applicable to the pump chamber pressure relevant with load is worked when a kind of state like this, this state is the special injection beginning time to regulate the state that there is no need, and this adjusting is necessary to the internal-combustion engine in operating temperature range not, this state can be that internal-combustion engine does not also reach operating temperature fully, but the state that rotating speed is higher, in other words, internal-combustion engine has reached its operating temperature, the state that expanding material element or temperature controlled adjustable lever have been opened spheroid one way stop peturn valve 256.
Claims (6)
1, a kind of fuel-injection pump for IC engines, has a pump piston (1), this jet pump is operated its running by cam drive, this cam drive is made of parts (2) and fixing parts (6) rotation, that driven by transmission shaft (3), cam locus (4) is arranged on one of two parts, and these parts do relative motion with respect to these another parts, make with two parts in one of the reciprocating pump (1) that is coupled, produce to-and-fro motion perpendicular to cam locus; An injection beginning regulating piston (32) is on the moving direction of cam locus (4) or one of described two parts of direction adjusted opposite with its moving direction, injection beginning regulating piston (32) is on the action direction against return power (34), be subjected to being subjected in the fuel-injection pump chamber (12) pressure control of piezodielectric, this pressure controlled pressure is by providing with the synchronously driven transfer pump of fuel-injection pump (38), and regulate by first pressure control device (49), this device has a pressure controlled valve (39), the drainage port (43) of control piston (40) the control pump chamber (12) of this valve (39), and head on spring (42), be subjected to the active force of this spring, this active force is the pressure in the reset space (54) that control piston (40) is limited, this reset space (54) connects together by throttle valve (45) and pump chamber (12), and additionally adjust by second pressure control device (50), this device (50) has a throttle valve (47) by engine load control, this throttle valve (47) is positioned at blowdown piping (48), this blowdown piping (48) comprise one mainly by the switch valve (66) of other Operational Limitss controls and be positioned at pump chamber (12) and relief chamber (44) between, has a floss hole that leads to relief chamber (44) on the reset space (54), this floss hole is subjected to a valve (52 of being controlled by the Control Parameter that characterizes engine temperature, 152,252) control, described valve (52,152,252) operation, the valve element (61 of its inner valve will directly or indirectly be adjusted, 161,100), and by this adjustment, adjust the blowdown piping (48) between throttle valve of second pressure control device (50) (47) and the relief chamber (44) to such an extent that make at controlled valve (52,152,252) be under the state of opening, be in connected state, at this moment, switch valve (66) is controlled by other parameters rather than by the temperature of internal-combustion engine; It is characterized in that, be parallel to controlled valve (52,152,252) stop valve (106) by the control of the pilot pressure in the pump chamber is housed, when the pressure in the pump chamber (12) surpassed a determined value, this stop valve (106) just made reset space (54) be communicated with relief chamber (44).
2, fuel-injection pump according to claim 1, it is characterized in that, this stop valve (106) has a spool member as valve element (107), it limits a working space (109) that links to each other with pump chamber by throttle valve (108), and can move adjusting against the action direction of adjustable return power (110).
3, fuel-injection pump according to claim 1 and 2, it is characterized in that, controlled valve (52) is a voltage stabilizing throttle valve, its valve element (56) is subjected to the effect of a spring (57), and an available operating element (64) that regulated by corresponding Control Parameter is pushed valve element (56) open, operation along with controlled valve (52), a slide-valve component (61) also is conditioned simultaneously, with the throttle valve (47) of controlling second pressure control device (50) and the break-make between the relief chamber (44).
4, fuel-injection pump according to claim 1 and 2, it is characterized in that, controlled valve (52) is a voltage stabilizing throttle valve, its valve element (156) is subjected to the effect of spring (157), and can push valve element (156) open by an operating element (164) that regulated by corresponding Control Parameter, this valve element (156) slide-valve component of can regulate (161), thus the throttle valve (47) of second pressure control device (50) and the break-make between the relief chamber (44) controlled.
5, fuel-injection pump according to claim 4, it is characterized in that, the valve element of voltage stabilizing throttle valve is a spheroid that concurs with valve seat (70), it it dorsad a side of valve seat contact with slide-valve component (161), with regard to it, its this face is subjected to the active force of spring (157) simultaneously.
6, fuel-injection pump according to claim 4, it is characterized in that, controlled valve (252) is a voltage stabilizing throttle valve, its valve element (256) is subjected to the effect of spring (257), and can push valve element (256) open by an operating element (264) that regulated by corresponding Control Parameter, make pipeline (48,65) valve of Lian Jieing has a piston valve (100) as valve element, this valve element is placed in the cylindrical body (101) between throttle valve (47) and the relief chamber (44), limit a working space (102) that is communicated with reset space (54) all the time, and the active force that heads on Returnning spring (103) power in working space (102) is pushed and moves to a fixed stop place (104), locating this piston valve (100) at this makes the pipeline (48,65) between throttle valve (47) and the relief chamber (44) be in not connected state.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19549046.0 | 1995-12-28 | ||
| DE19549046A DE19549046A1 (en) | 1995-12-28 | 1995-12-28 | Fuel injection pump for internal combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1175993A true CN1175993A (en) | 1998-03-11 |
| CN1079896C CN1079896C (en) | 2002-02-27 |
Family
ID=7781595
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN96192123A Expired - Fee Related CN1079896C (en) | 1995-12-28 | 1996-10-24 | Fuel-injection pump for IC engines |
Country Status (8)
| Country | Link |
|---|---|
| EP (1) | EP0812384B1 (en) |
| JP (1) | JPH11501384A (en) |
| KR (1) | KR100304474B1 (en) |
| CN (1) | CN1079896C (en) |
| BR (1) | BR9607437A (en) |
| DE (2) | DE19549046A1 (en) |
| RU (1) | RU2166658C2 (en) |
| WO (1) | WO1997024519A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100436808C (en) * | 2003-04-01 | 2008-11-26 | Avl里斯脱有限公司 | Internal combustion engine with piston injection pump |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB9725415D0 (en) * | 1997-12-02 | 1998-01-28 | Lucas Ind Plc | Advance arrangement |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3822257A1 (en) * | 1988-07-01 | 1990-01-04 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| DE4341932A1 (en) * | 1993-12-09 | 1995-06-14 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines |
-
1995
- 1995-12-28 DE DE19549046A patent/DE19549046A1/en not_active Withdrawn
-
1996
- 1996-10-24 WO PCT/DE1996/002014 patent/WO1997024519A1/en active IP Right Grant
- 1996-10-24 JP JP9523958A patent/JPH11501384A/en not_active Abandoned
- 1996-10-24 EP EP96934435A patent/EP0812384B1/en not_active Expired - Lifetime
- 1996-10-24 KR KR1019970705985A patent/KR100304474B1/en not_active IP Right Cessation
- 1996-10-24 CN CN96192123A patent/CN1079896C/en not_active Expired - Fee Related
- 1996-10-24 BR BR9607437A patent/BR9607437A/en not_active IP Right Cessation
- 1996-10-24 DE DE59607780T patent/DE59607780D1/en not_active Expired - Fee Related
- 1996-10-24 RU RU97115941/06A patent/RU2166658C2/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100436808C (en) * | 2003-04-01 | 2008-11-26 | Avl里斯脱有限公司 | Internal combustion engine with piston injection pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11501384A (en) | 1999-02-02 |
| KR19980702579A (en) | 1998-07-15 |
| KR100304474B1 (en) | 2001-11-30 |
| RU2166658C2 (en) | 2001-05-10 |
| WO1997024519A1 (en) | 1997-07-10 |
| EP0812384B1 (en) | 2001-09-26 |
| DE59607780D1 (en) | 2001-10-31 |
| BR9607437A (en) | 1998-05-26 |
| DE19549046A1 (en) | 1997-07-03 |
| EP0812384A1 (en) | 1997-12-17 |
| CN1079896C (en) | 2002-02-27 |
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