CN100381697C - Fuel pressure regulation valve - Google Patents
Fuel pressure regulation valve Download PDFInfo
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- CN100381697C CN100381697C CNB2005101136086A CN200510113608A CN100381697C CN 100381697 C CN100381697 C CN 100381697C CN B2005101136086 A CNB2005101136086 A CN B2005101136086A CN 200510113608 A CN200510113608 A CN 200510113608A CN 100381697 C CN100381697 C CN 100381697C
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Abstract
A regulation valve (1) has: a cylinder (20) that has an inlet port (23) at one end side thereof to introduce the fuel thereinto, and a relief port (25) opening on a side face thereof; a piston (21) that is reciprocatably inserted in the cylinder (20) to vary an opening area of the relief port (25) in accordance with a variation of the pressure of the fuel flowing in through the inlet port (23); and a spring (22) that urges the piston (21) in a direction against the pressure of the fuel acting on the piston (21) to regulate the pressure to be a specific value. Further, the cylinder (20) and/or the piston (21) is formed so that the piston (21) opens the relief port (25) at a relatively small speed per a unit displacement thereof in starting opening the relief port (25) and subsequently at a relatively large speed.
Description
Technical field
The present invention relates to a kind of modulating valve of fuel metering pressure.
Background technique
Traditionally, a kind of fuel under high pressure of accumulating in the rail that will be total to is ejected into accumulator fuel injection system known (with reference to U.S. Patent No. 6895936 and patent families JP-2005-36794-A thereof) in the cylinder of internal-combustion engine.This accumulator fuel injection system is provided with a suction of fuel and supply fuel to the supply pump of high-pressure service pump and modulating valve that one is regulated supply pump supply pressure (being fed to the fuel pressure of high-pressure service pump from supply pump) from fuel tank.
As shown in Figure 15 A, this modulating valve by one at one end the cylinder shape valve 110, one of side with inlet can back and forth insert the piston 120 in the valve body 110, a spring 130 that is arranged on piston 120 back etc. and constitute.
This modulating valve by a position co-ordination piston 120 with balance from enter the mouth 1100 fuel pressures that enter and oil storage cavity 160 fuel pressure and the reaction force sum of spring 130 come the fuel pressure (supply pressure of supply pump) of regulating action on piston 120 to a specified value.As shown in Figure 15 B, a plurality of pressure relief openings 140 form circle, have the diameter that is equal to each other, and separate with regular spaces on the circumferencial direction of valve body 110, and place same position on the moving direction (substantially horizontal among the figure) of piston 120.
Therefore, the opening area of pressure relief opening 140 changes according to the displacement opening area characteristic as shown in Figure 16 of piston 120.Piston settling position when figure mid point O represents that the motion of piston 120 obtains stablizing.A1 represents from the piston settling position to the distance of opening valve position (piston 120 is in a position when closing pressure relief opening 140 fully the moving of direction of closing pressure relief opening 140, perhaps the position of piston 120 when beginning to open pressure relief opening 140) in the moving of the direction of opening pressure relief opening 140 among the figure.
But in above-mentioned modulating valve, when air was inhaled in the fuel of supply pump suction, the fuel pressure that acts on the piston 120 became unstable.Therefore, as shown in Fig. 5 A, piston 120 vibrations are with periodically repeat switch action (opening and closing the action of pressure relief opening 140), to such an extent as to produce switch valve noise (unusual overcast noise).The switch valve noise is very ear-piercing, makes the driver uncomfortable, to such an extent as to need measure to solve this uncommon noise.
Summary of the invention
The present invention considers the problems referred to above and finishes, and has the purpose of a kind of modulating valve with fuel metering pressure is provided, and this modulating valve can reduce the switch valve noise that produces according to piston vibration.
This modulating valve has: a cylinder, a piston and a pressing device, wherein cylinder has and is positioned at distolateral being used for of one fuel is introduced wherein inlet, and has a pressure relief opening of opening in its side, piston is inserted in the cylinder in reciprocating mode, changing the opening area that changes pressure relief opening according to the fuel pressure that flows into by inlet, pressing device along the direction pushing piston of the fuel pressure of resistant function on piston with adjusting pressure to one specified value.In addition, at least one of cylinder and piston are formed in the following manner, be that piston is opened pressure relief opening with first speed in the per unit displacement in the phase I, beginning to open pressure relief opening, and in the second stage after the phase I to open pressure relief opening greater than the second speed of first speed.
Description of drawings
The detailed description, appended claims and the accompanying drawing that form this application part below reading it will be appreciated that the operating method and the function of other purpose of the present invention, feature and advantage and relevant portion.Among the figure:
Figure 1A is a sectional view according to the modulating valve of first embodiment of the invention;
Figure 1B is the expansion view according to the valve body of first embodiment's modulating valve;
Fig. 2 is the overall construction drawing that has wherein used according to the accumulator fuel injection system of first embodiment's modulating valve;
Fig. 3 is the figure of demonstration according to the opening area characteristic of first embodiment's modulating valve;
Fig. 4 is the figure of demonstration according to the supply pressure characteristic of first embodiment's modulating valve;
Fig. 5 A shows the piston operation of traditional modulating valve and the figure of switch valve noise generation time;
Fig. 5 B is that demonstration is according to the piston operation of first embodiment's modulating valve and the figure of switch valve noise generation time;
Fig. 6 A is a sectional view according to the modulating valve of second embodiment of the invention;
Fig. 6 B is the expansion view according to the valve body of second embodiment's modulating valve;
Fig. 7 is the figure of demonstration according to the opening area characteristic of second embodiment's modulating valve;
Fig. 8 A is a sectional view according to the modulating valve of third embodiment of the invention;
Fig. 8 B is the expansion view according to the valve body of the 3rd embodiment's modulating valve;
Fig. 9 is the figure of demonstration according to the opening area characteristic of the 3rd embodiment's modulating valve;
Figure 10 A is a sectional view according to the modulating valve of fourth embodiment of the invention;
Figure 10 B is the expansion view according to the piston of the 4th embodiment's modulating valve;
Figure 11 is the figure of demonstration according to the opening area characteristic of the 4th embodiment's modulating valve;
Figure 12 A is a sectional view according to the modulating valve of fifth embodiment of the invention;
Figure 12 B is the expansion view according to the piston of the 5th embodiment's modulating valve;
Figure 12 C is the enlarged side view according to the piston of the 5th embodiment's modulating valve;
Figure 13 is the figure of demonstration according to the opening area characteristic of the 5th embodiment's modulating valve;
Figure 14 A is a sectional view according to the modulating valve of sixth embodiment of the invention;
Figure 14 B is the expansion view according to the piston of the 6th embodiment's modulating valve;
Figure 14 C is the enlarged side view according to the piston of the 6th embodiment's modulating valve;
Figure 15 A is a kind of sectional view of traditional modulating valve;
Figure 15 B is the expansion view of the valve body of traditional modulating valve;
Figure 16 is the figure that shows the opening area characteristic of traditional modulating valve.
Embodiment
(first embodiment)
Figure 1A is an a kind of sectional view of modulating valve, and Figure 1B is the expansion view of valve body, and Fig. 2 is the overall construction drawing of a kind of accumulator fuel injection system.
Have the function of the supply pressure (from supply pump 2 supplied fuel pressure) of regulating supply pump 2 according to first embodiment's modulating valve 1, wherein supply pump uses and exists, for example in the diesel engine accumulator fuel injection system shown in Fig. 2.
This accumulator fuel injection system is known as being mainly used in fuel injection systems of diesel, and this system is provided with a fuel injection pump that comprises supply pump 23, one and accumulates sparger 6 cylinder 5 that common rail 4 from fuel injection pump 3 supplied fuel pressure, fuel under high pressure that will be total to rail 4 supplies be ejected into diesel engine etc.The discharge time of the fuel pressure of an ECU (Electrical Control Unit) (ECU) 7 control fuel injection pumps 3 and delivery volume, sparger 6 and emitted dose etc.
Fuel injection pump 3 is provided with: a cylinder 11 and a plunger 12 that inserts in the cylinder 11 that is formed in the pump case (not shown).Plunger 12 is according to the to-and-fro motion in the cylinder 11 that is rotated in of camshaft 10.
Next the structure of modulating valve 1 will be described.
As shown in Figure 1A, modulating valve 1 can back and forth insert piston 21 in the valve body 20 and one formations such as spring 22 to a certain direction (among the figure left) pushing piston 21 by a cylinder shape valve 20, one.
One distolateral (left surface among the figure) of valve body 20 forms a fuel inlet 23, and the other end is blocked.Inlet 23 link to each other with branch road 24 (with reference to figure 2) from fuel channel 15 branches.Flow to the inlet 23 by branch road 24 from supply pump 2 supplied fuel parts.
On a sidewall of valve body 20, form a plurality of pressure relief openings 25 and a floss hole 26.Pressure relief opening 25 link to each other with a pressure release passage 27 (with reference to figure 2).So, when piston 21 is opened pressure relief opening 25, flow out pressure relief openings 25, by pressure release passage 27 and turn back to the suction side of supply pump 2 from 23 fuel that enter that enter the mouth.
Piston 21 moves in valve body 20 with according to from 23 fuel pressures that enter that enter the mouth, and the variation that promptly acts on the fuel pressure of piston 21 fronts changes the opening area of pressure relief opening 25.
Next will with the feature of the above-mentioned modulating valve 1 of traditional modulating valve comparative descriptions.
At first be defined as follows term.
(a) " threshold switch position ": piston 21 is in a position when closing pressure relief opening 25 fully in the motion of the direction (among Figure 1A, the 1B left) of closing pressure relief opening 25, and perhaps piston 21 is in a position when buttoned-up status begins to open pressure relief opening 25 in the moving of the direction of opening pressure relief opening 25.
(b) " piston settling position ": when the motion of piston 21 obtains stablizing, promptly for example, equal at the rotational speed N E of motor under 2000 rev/mins the situation, when the supply pressure of supply pump 2 is adjusted to a specified value, the front position of piston 21 (front position is the position of piston front of bearing the supply pressure of supply pump 2).
(c) " valve cuts out the side piston stroke ": distance from the piston settling position to the threshold switch position.
As shown in Figure 15 B, in traditional modulating valve 100, a plurality of (for example, four) pressure relief opening 140 of opening to having circular cross section all is arranged on same position along the moving direction of piston 120.By contrast, modulating valve 1 according to the present invention is provided with the first pressure relief opening 25a1 and the second pressure relief opening 25b1 that opens on the position of setovering mutually along piston 21 moving direction.Specifically, as shown in Figure 1B, three first pressure relief opening 25a1 are arranged on the mutually the same position, and one second pressure relief opening 25b1 is arranged on valve with respect to the first pressure relief opening 25a1 and closes side (spring opposition side).The first and second pressure relief opening 25a1,25b1 have mutually the same diameter, are set to overlap each other along the moving direction of piston 21.
Therefore, the modulating valve 1 according to first embodiment is provided with: with first opened areas of little gradient or slope (gradient) increase pressure relief opening 25 total opening areas with to increase by second opened areas of pressure relief opening 25 total opening areas greater than the big gradient of the medium and small gradient of first opened areas.Being arranged on valve with respect to the first pressure relief opening 25a1, to close the second pressure relief opening 25b1 of side all open-minded in first and second opened areas, and the first pressure relief opening 25a1 is open-minded in second opened areas.
Therefore, if the opening area of pressure relief opening 25 is shown the opening area characteristic according to the change list of piston 21 displacements, shown in solid line among the figure of Fig. 3, modulating valve 1 so according to the present invention constitutes that to close side gradient ratio tradition modulating valve (among the figure shown in the dotted line) with respect to the valve of piston point of safes (figure mid point O) little, and wherein the piston point of safes is represented according to flex point of the present invention.Specifying the valve of traditional modulating valve to close the side piston stroke is A1, closes the side piston stroke according to the valve of modulating valve 1 of the present invention so and is the A2 greater than A1.
Next the operation of modulating valve 1 will be described.
If air is inhaled into by supply pump 2 from the fuel of fuel tank 8 suctions, the fuel pressure that acts on piston 21 fronts so will become unstable.Therefore, in modulating valve traditional shown in Figure 15 A, piston vibration is to repeat to open and close pressure relief opening 140, to such an extent as to produce the switch valve noise.
When piston 21 repeat switches motions (opening and closing the motion of pressure relief opening 25), piston 21 can overshoot in the moving of valve closing direction the threshold switch position of (motion above) pressure relief opening 25.In other words, the motion of piston 21 repeat switches restrains up to overshoot.Therefore, by increasing the distance (valve cuts out side piston stroke A2) from the piston settling position to the threshold switch position, the overshoot that piston 21 surpasses the threshold switch position can reduce.
In the modulating valve 1 according to this embodiment, valve cuts out side piston stroke A2 and the second pressure relief opening 25b1 is set is set at greater than the A1 in traditional modulating valve by cut out side at the valve of the first pressure relief opening 25a1.Therefore, when the fuel pressure that acts on piston 21 fronts (supply pressure of supply pump 2) when changing fast, the overshoot of piston 21 is less than the overshoot of traditional modulating valve, to such an extent as to the vibration of piston 21 restrains (with reference to figure 5B) at short notice.
As a result, switch valve noise generation time is shorter than traditional modulating valve, to such an extent as to even also can reduce the uncomfortable of driver in ambient noise very little dead time.
The gradient of the opening area characteristic gradient by reducing modulating valve 1 only, it is big that supply pressure just becomes in very big speed range, and as shown in Figure 4, and supply pump 2 is possible stuck.By contrast, in first embodiment, the gradient of opening area characteristic only in the very little rotary area at a slow speed of supply pump 2 rotating speeds (NE=2000 rev/min) be set at very little, to such an extent as to supply pressure can not increase in the fast rotational zone.That is to say that the opening area characteristic in fast rotational zone is identical with traditional product, to such an extent as to the increase of restriction supply pressure is stuck to prevent supply pump 2.
(second embodiment)
Fig. 6 A is the sectional view of modulating valve 1, and Fig. 6 B is the expansion view of valve body 20.In the modulating valve 1 according to second embodiment, the position of the quantity of the first pressure relief opening 25a2 and the second pressure relief opening 25b2 and diameter are different from the pressure relief opening 25 described in first embodiment.
The first pressure relief opening 25a2 is arranged on four positions along the circumferencial direction of valve body 20 with equidistant from distance.The second pressure relief opening 25b2 has the diameter less than the first pressure relief opening 25a2.The second pressure relief opening 25b2 is set to close side than the more close valve of the second pressure relief opening 25b1 among first embodiment, so that separate along the moving direction and the first pressure relief opening 25a2 of piston 21.
Fig. 7 has described the opening area characteristic of modulating valve 1.The valve of piston point of safes (figure mid point O) cuts out the side gradient less than traditional modulating valve (being illustrated by the broken lines in the drawings), and closes side piston stroke A2 according to the valve of second embodiment's modulating valve 1 and close side piston stroke A1 greater than the valve of traditional modulating valve.Therefore, obtain and first embodiment's identical operations and the effect, and the vibration of piston 21 restrains at short notice to reduce switch valve noise generation time.
As long as can obtain to close with respect to valve the A2＞A1 that concerns of side piston stroke, other formation that is different from first and second embodiments can be adopted in diameter, quantity and the position of the first and second pressure relief opening 25a2,25b2.
(the 3rd embodiment)
Fig. 8 A is the sectional view of modulating valve 1, and Fig. 8 B is the expansion view of valve body 20.Have the first pressure relief opening 25a1,25a2 and the second pressure relief opening 25b1,25b2 at the modulating valve 1 described in first and second embodiments, one of them is open-minded in the position that is different from other pressure relief opening along the moving direction of piston 21.The first pressure relief opening 25a1,25a2 and the second pressure relief opening 25b1,25b2 are independent of each other and form.By contrast, as shown in Fig. 8 B, have: the first perforate part 25c that opens at the piston settling position and close the second perforate part 25d that side (spring opposition side) is opened at the valve of piston settling position according to the 3rd embodiment's modulating valve 1.The first perforate part 25c and the second perforate part 25d open continuously so that form a pressure relief opening 25.
In addition, in the 3rd embodiment's formation, shown in Fig. 9 opening area characteristic, obtain to close the A2＞A1 that concerns of side piston stroke, to reach the effect identical with first and second embodiments with respect to valve.Figure mid point O representative indication is according to the piston point of safes of flex point of the present invention (inflection point).
(the 4th embodiment)
Figure 10 A is the sectional view of modulating valve 1, and Figure 10 B is the expansion view of piston 21.
As shown in Figure 10 B, in modulating valve 1, bear the end of piston 21 front-end faces (spring opposition side) of supply pump 2 supply pressures and on diameter, shrink, so that path part 21a to be provided with step-wise manner according to the 4th embodiment.By spring opposition side the path part that diameter shrinks is set, can reaches identical effect with first to the 3rd embodiment at piston 21.Therefore, do not need as among first to the 3rd embodiment, to provide the second pressure relief opening 25b1,25b2 for pressure relief opening 25.In the similar mode of traditional modulating valve shown in Figure 15 A, modulating valve 1 is provided with four pressure relief openings 25 that are positioned at same position along piston 21 moving direction.
Modulating valve 1 according to the 4th embodiment has: first opened areas and second opened areas, wherein in first opened areas, pressure relief opening 25 is closed the side circumferential section by the side of path part 21a towards the valve of pressure relief opening 25 and is opened, and in second opened areas, pressure relief opening 25 is by moving to respect to first opened areas that valve is opened side with piston 21 and opening with the perforate greater than first opened areas.That is to say that pressure relief opening 25 is provided with in the same manner with traditional modulating valve, but the piston settling position is provided with path part 21a and opens side shifting with respect to traditional modulating valve to valve by the front-end face at piston 21.As a result, when piston 21 moved along the direction of opening pressure relief opening 25, the side circumferential section was closed in the face of valve in the side (outer peripheral surface) of path part 21a, so that opened pressure relief opening 25 before the front-end face arrival valve of piston 21 cuts out the side circumferential section.As a result, shown in Figure 11 opening area characteristic, obtain to close with respect to valve the A2＞A1 that concerns of side piston stroke, therefore, as among first to the 3rd embodiment, the vibration of piston 21 can restrain at short notice to reduce switch valve noise generation time.Figure mid point O representative indication is according to the piston point of safes of flex point of the present invention.
(the 5th embodiment)
Figure 12 A is the sectional view of modulating valve 1, and Figure 12 B is the side view of piston 21, and Figure 12 C is the side view that shows the tapering part 21b of piston 21.
As shown in Figure 12B, in the modulating valve 1 according to the 5th embodiment, the end of piston 21 fronts (spring opposition side) is taper (part of shrinking in the taper mode is called tapering part 21b).As shown in Figure 12 C, if think that the length of tapering part 21b is L, and cone angle is θ, and L is that 0.4mm or longer and θ are rational at 4 degree between 50 degree.As the traditional modulating valve situation as shown in Figure 15 A, four pressure relief openings 25 are arranged at mutually the same position along the moving direction of piston 21.
The same with the 4th embodiment's situation, in modulating valve 1 according to the 5th embodiment, the same same position that is arranged at of pressure relief opening 25 with traditional modulating valve.By spring opposition side tapering part 21b is set at piston 21, the piston settling position moves to valve with respect to traditional modulating valve and opens side, to such an extent as to can obtain to close the A2＞A1 that concerns of side piston stroke with respect to valve, shown in Figure 13 split shed area performance, therefore the vibration of piston 21 can restrain at short notice to reduce switch valve noise generation time, as first to the 3rd embodiment.Figure mid point O representative indication is according to the piston point of safes of flex point of the present invention.
(the 6th embodiment)
Figure 14 A is the sectional view of modulating valve 1, and Figure 14 B is the expansion view of piston 21, and Figure 14 C is the side view that shows the fillet part 21c of piston 21.
As shown in Figure 14 B, in the modulating valve 1 according to the 6th embodiment, its full girth of end of piston 21 fronts (spring opposition side) is provided with fillet part 21c.As shown in Figure 14 C, fillet part 21c is that radius is the curved surface of R.Radius R be 0.4mm or bigger be rational.As the traditional modulating valve situation as shown in Figure 15 A, four pressure relief openings 25 are arranged at mutually the same position along the moving direction of piston 21.
The same with the 4th and the 5th embodiment's situation, in modulating valve 1 according to the 6th embodiment, the same same position that is arranged at of pressure relief opening 25 with traditional modulating valve.By the spring opposition side at piston 21 fillet part 21c is set, the piston settling position moves to valve with respect to traditional modulating valve and opens side.Therefore, opening area characteristic and the 4th embodiment's situation the same (with reference to Figure 11) is so can obtain to close with respect to valve the A2＞A1 that concerns of side piston stroke.As a result, with respect to traditional modulating valve, the vibration of piston 21 restrains at short notice to reduce switch valve noise generation time.
(remodeling embodiment)
Fuel injection pump 3 according to first embodiment has the structures of supply pump 2 wherein being installed and being driven by camshaft 10 integral body with supply pump 2.As selection, might separate with fuel injection pump 3 provides supply pump 2, to such an extent as to supply pump 2 and fuel injection pump 3 each free two camshaft actuated that are independent of each other.
Above the present invention is done description and in fact only be used for example, therefore, the modification that does not break away from marrow of the present invention is considered to be located within the scope of the present invention.This modification is not considered to break away from marrow of the present invention and scope.
Claims (14)
1. the modulating valve of a fuel metering pressure (1) comprising:
Cylinder (20), described cylinder have and are positioned at distolateral being used for of one fuel is introduced wherein inlet (23), and have the pressure relief opening of opening in its side (25);
Piston (21), described piston is inserted in the cylinder (20) in reciprocating mode, to change the opening area that changes pressure relief opening (25) according to the fuel pressure that flows into by inlet;
The direction pushing piston (21) of pressing device (22), the described pressing device fuel pressure on (21) along resistant function in piston is to be adjusted to specified value with pressure;
Wherein, in described cylinder (20) and the piston (21) at least one formed in the following manner, be that piston (21) is opened pressure relief opening (25) with first speed in the per unit displacement in the phase I, beginning opening pressure relief opening (25), and in the second stage after the phase I to open pressure relief opening greater than the second speed of first speed.
2. modulating valve according to claim 1 (1) is characterized in that, the stroke of piston (21) comprising:
Open first opened areas of pressure relief opening (25) in the phase I;
Open second opened areas of pressure relief opening (25) in second stage, in described second opened areas, the opening area of the pressure relief opening in the per unit displacement (25) is greater than the opening area in the per unit displacement in first opened areas.
3. modulating valve according to claim 2 (1) is characterized in that, pressure relief opening (25) comprises first pressure relief opening (25a1,25a2,25c) and second pressure relief opening (25b1,25b2,25d) of vertically setovering mutually along cylinder (20).
4. modulating valve according to claim 3 (1) is characterized in that:
First pressure relief opening (25a1) and second pressure relief opening (25b1) vertically form separately and are set to overlap each other along cylinder (20).
5. modulating valve according to claim 3 (1) is characterized in that:
First pressure relief opening (25a2) and second pressure relief opening (2562) vertically form separately and are set to separate each other along cylinder (20).
6. modulating valve according to claim 3 (1) is characterized in that, first pressure relief opening (25c) and second pressure relief opening (25d) form continuously.
7. according to the arbitrary described modulating valve of claim 2 to 6 (1), it is characterized in that, piston (21) is provided with path part (21a, 21b, 21c) at its longitudinal end that bears fuel pressure, and forms the gap between the internal surface of the cylindrical body of path part (21a, 21b, 21c) and cylinder.
8. modulating valve according to claim 7 is characterized in that, piston (21) shrinks with step-wise manner at an one longitudinal end, to provide path part (21a).
9. modulating valve according to claim 7 is characterized in that, piston (21) shrinks in the taper mode at an one longitudinal end, so that described gap extends to described longitudinal end gradually, thereby provides path part (21b).
10. modulating valve according to claim 9 is characterized in that:
The longitudinal length of path part (21b) be 0.4mm or more than;
The circumferential surface of path part (21b) with respect to piston (21) longitudinally the inclination angle be that 4 degree are between 50 degree.
11. modulating valve according to claim 7 is characterized in that, piston (21) is circular at the circumferential edges of an one longitudinal end, to provide path part (21c).
12. modulating valve according to claim 11 is characterized in that, the fillet radius of path part (21c) be 0.4mm or more than.
13., it is characterized in that it is used to regulate the pressure of the fuel of being supplied with by oil-engine driven supply pump (2) according to the arbitrary described modulating valve of claim 2 to 6 (1), wherein:
The opening area characteristic of the speed variable when opening pressure relief opening (25) as piston (21) in the per unit displacement has at least one flex point (O) in internal-combustion engine rotational speed is 2000 rev/mins or following zone;
First opened areas is arranged on the slow-speed of revolution side of flex point (O);
Second opened areas is arranged on the high rotating speed side of flex point (O).
14., it is characterized in that according to the arbitrary described modulating valve of claim 1 to 6 (1):
Modulating valve is applied to the accumulator fuel injection system, this system supplies with the fuel that is aspirated by supply pump (2) from fuel tank (8), and by high-pressure service pump (3) fuel is pressurizeed to be fed to common rail (4), be ejected in the cylinder of internal-combustion engine (5) with the fuel that will be accumulated in from sparger (6) the common rail (4);
Modulating valve is regulated the fuel pressure that is supplied to high-pressure service pump (3) from supply pump (2).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP299109/2004 | 2004-10-13 | ||
| JP2004299109 | 2004-10-13 | ||
| JP238799/2005 | 2005-08-19 |
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| CN1760531A CN1760531A (en) | 2006-04-19 |
| CN100381697C true CN100381697C (en) | 2008-04-16 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2005101136086A Active CN100381697C (en) | 2004-10-13 | 2005-10-11 | Fuel pressure regulation valve |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP4893294B2 (en) * | 2006-12-20 | 2012-03-07 | 株式会社デンソー | Piston valve |
| DE102013013231A1 (en) * | 2013-08-08 | 2015-02-12 | Man Diesel & Turbo Se | Valve arrangement for a fuel supply system and fuel supply system |
| CN110215887B (en) * | 2019-06-27 | 2023-03-21 | 重庆赛迪热工环保工程技术有限公司 | Intermittent discharge device of supercritical water gasification system and control method |
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| JPH1193797A (en) * | 1997-09-25 | 1999-04-06 | Denso Corp | Fuel injection pump |
| US20020000217A1 (en) * | 2000-06-26 | 2002-01-03 | Tohru Takahashi | Flow amount control device |
| EP1298307A2 (en) * | 2001-09-28 | 2003-04-02 | Isuzu Motors Limited | Control device of common rail fuel injection system of an engine |
| JP2003120845A (en) * | 2001-10-12 | 2003-04-23 | Denso Corp | Metering valve device and fuel injection pump using the same |
| US20030136384A1 (en) * | 2001-12-19 | 2003-07-24 | Linden Dietmar Van Der | Fuel injection system for an internal combustion engine |
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2005
- 2005-10-11 CN CNB2005101136086A patent/CN100381697C/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6045735A (en) * | 1983-07-30 | 1985-03-12 | ロ−ベルト・ボツシユ・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング | Fuel injection pump for internal combustion engine |
| CN1131723A (en) * | 1994-12-09 | 1996-09-25 | 罗伯特-博希股份有限公司 | Fuel injection pump for internal combusion engines |
| JPH1193797A (en) * | 1997-09-25 | 1999-04-06 | Denso Corp | Fuel injection pump |
| US20020000217A1 (en) * | 2000-06-26 | 2002-01-03 | Tohru Takahashi | Flow amount control device |
| EP1298307A2 (en) * | 2001-09-28 | 2003-04-02 | Isuzu Motors Limited | Control device of common rail fuel injection system of an engine |
| JP2003120845A (en) * | 2001-10-12 | 2003-04-23 | Denso Corp | Metering valve device and fuel injection pump using the same |
| US20030136384A1 (en) * | 2001-12-19 | 2003-07-24 | Linden Dietmar Van Der | Fuel injection system for an internal combustion engine |
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