Source: http://www.google.com/patents/US7163162?dq=7,682,496
Timestamp: 2017-03-24 00:37:43
Document Index: 503147827

Matched Legal Cases: ['art 8', 'art 63', 'art 62', 'art 62', 'art 63', 'art 62']

Patent US7163162 - Fuel-injection valve - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign inPatentsA fuel-injection valve includes a fuel-injection hole, a valve element and a valve seat for opening and closing the fuel-injection hole, a force-applying member for applying force to the valve element in a direction of motion of the valve element, and a drive unit for applying force to the valve element...http://www.google.com/patents/US7163162?utm_source=gb-gplus-sharePatent US7163162 - Fuel-injection valveAdvanced Patent SearchTry the new Google Patents, with machine-classified Google Scholar results, and Japanese and South Korean patents.Publication numberUS7163162 B2Publication typeGrantApplication numberUS 10/284,407Publication dateJan 16, 2007Filing dateOct 31, 2002Priority dateApr 13, 1999Fee statusLapsedAlso published asDE60008158D1, DE60008158T2, EP1045135A2, EP1045135A3, EP1045135B1, US6474572, US20030111563, US20070075166Publication number10284407, 284407, US 7163162 B2, US 7163162B2, US-B2-7163162, US7163162 B2, US7163162B2InventorsMasahiro Tsuchiya, Tosuke Hirata, Yoshio Okamoto, Tohru Ishikawa, Noriyuki Maekawa, Yoshiyuki Tanabe, Atsushi Sekine, Yuzo Kadomukai, Makoto Yamakado, Motoyuki AbeOriginal AssigneeHitachi, Ltd.Export CitationBiBTeX, EndNote, RefManPatent Citations (17), Referenced by (7), Classifications (18), Legal Events (3) External Links: USPTO, USPTO Assignment, EspacenetFuel-injection valve
US 7163162 B2Abstract
1. A fuel injection valve, which comprises:
a valve seat disposed in the vicinity of a fuel injection hole;
a valve element that sits on or lifts from said valve seat to close or open a fuel path;
a linked movable member installed on said valve element in a manner such that said linked movable member can slide in an axial direction of said valve element and can contact with or separate from said valve element;
a spring to press said valve element to said valve seat via said linked movable member; and
an attracting means to attract said valve element to separate from said valve seat against said spring,
wherein said valve element and said linked movable element are disposed in a manner such that they can mutually contact through a flat-ring-shaped leaf spring or can separate from each other;
wherein an outer edge of said leaf spring is secured to said valve element;
wherein said linked movable member is arranged in a manner such that an end part of said linked movable member touches to an inner bore of said leaf spring; and wherein a natural frequency of a secondary oscillation system comprised of said linked movable member and said leaf spring is set at such a value that said natural frequency substantially accords with a frequency of an impact force caused from a collision of said valve element with said valve seat.
2. A fuel injection according to claim 1, which further comprises a stopper to regulate the position of the valve element at the end of its stroke in separating movement from said valve seat, wherein the natural frequency of a secondary oscillation system comprised of said linked movable member and said leaf spring is set at a such value that said natural frequency substantially accords with a frequency of an impact force caused from a collision of said valve element with said stopper.
3. A fuel injection valve according to claim 1, wherein a plurality of notches are provided on a perimeter of the inner bore of said flat-ring-shaped leaf spring.
4. A fuel injection valve according to claim 2, wherein a plurality of notches are provided on a perimeter of the inner bore of said flat-ring-shaped leaf spring.
5. A fuel injection valve according to claim 3, wherein said notches are provided at three positions on the perimeter of said inner bore.
6. A fuel injection valve according to claim 4, wherein said notches are provided at three positions on the perimeter of said inner bore.
7. An internal combustion engine including a fuel injection valve which comprises:
8. An internal combustion engine according to claim 7, which further comprises a stopper to regulate the position of the valve element at the end of its stroke in separating movement from said valve seat, wherein the natural frequency of a secondary oscillation system comprised of said linked movable member and said leaf spring is set at a such value that said natural frequency substantially accords with a frequency of an impact force caused from a collision of said valve element with said stopper.
9. An internal combustion engine according to claim 7, wherein a plurality of notches are provided on a perimeter of the inner bore of said flat-ring-shaped leaf spring.
10. An internal combustion engine according to claim 8, wherein a plurality of notches are provided on a perimeter of the inner bore of said flat-ring-shaped leaf spring.
11. An internal combustion engine according to claim 9, wherein said notches are provided at three positions on the perimeter of said inner bore.
12. An internal combustion engine according to claim 10, wherein said notches are provided at three positions on the Perimeter of said inner bore.
13. A fuel injection valve according to claim 1, wherein a mass of the linked movable member is 0.3–1.5 g and a spring constant of the leaf spring is 100–1000 KgF/mm.
This application is a Divisional application of application Ser. No. 09/517,046, filed Mar. 2, 2000, now U.S. Pat. No. 6,474,572.
Japanese Patent Application Laid-Open Hei 1-1594060 discloses an electromagnetic fuel-injection valve for opening/closing an opening in a valve seat based on an ON/OFF signal having a duty which is determined by a control unit. In this electromagnetic valve, a magnetic circuit is composed of a yoke with a bottom part, a core with a plug part to fill the aperture of the yoke and with a cylinder extending through the core center line, and a plunger facing the core, separated by a gap. A spring is inserted inside the cylinder of the core, and the spring exerts pressure on a movable element of the valve, which is composed of the plunger, a rod, and a ball member, towards the face of the valve seat. The top part of the spring, on the side opposite the plunger, contacts the bottom part of a spring-adjuster inserted in the cylinder of the core, and adjusts the load set to the spring. A coil for exciting the magnetic circuit is wound around the outside of the core and inside the yoke. In the bottom part of the yoke, there is a plunger hole for admitting the plunger, along with a valve-guide hole to admit a stopper and a valve guide, which penetrates the bottom part of the yoke, and whose diameter is larger than that of the plunger hole. The stopper is provided to set the lift value (the stroke) of the ball-valve, and the thickness of the stopper is set so that the top of the plunger does not directly contact the bottom of the core when the movable element of the valve is pulled upward. On the rod, there is a stopping face which butts against the stopper. The valve guide is a housing for containing the ball valve, a fuel-swirl-flow generating element for applying a swirling force to the fuel, and on the rod, the stopping face of the rod; and a valve-seat face and a fuel-injection hole are also located at the bottom of the valve guide.
In the above-described conventional injection valve, only the spring is inserted between the bottom of the spring adjuster and the plunger.
FIG. 1 is a vertical cross section of an electromagnetic fuel-injection valve representing an embodiment according to the present, invention;
FIG. 2 is a diagram showing a dynamic model of a system with two degrees of freedom;
FIG. 3(A) is a diagram depicting a graph showing the movement trajectory of the linked movable member;
FIG. 3(B) is a diagram depicting a graph showing the movement trajectory of the valve element, which are simulated with the dynamic model shown in FIG. 2;
FIG. 4 is a three-dimensional graph showing changes in the amount xT of the secondary fuel injection obtained by simulations in which the mass quantity m2 of the mass 32 and the spring constant k1 of the spring 31 is given and fixed, and the mass quantity ml of the mass 30 and the spring constant k2 of the spring 33 are parametrically changed;
FIG. 5A is a vertical cross section of an electromagnetic fuel-injection valve representing another embodiment according to the present invention, in which the spring 17′ is provided in the form of a plate spring;
FIG. 5B is a horizontal cross section, of the plate spring 17′ viewed from the line A–A′.
FIG. 6 is a diagram showing the succession of states in the process of suppressing the bouncing in the state transition depicted from the state (a) showing the open-valve condition to the state (e) showing the closed-valve condition, which is achieved by the fuel-injection valve shown in FIG. 5;
FIG. 7A is a graph showing changes in the displacement of the valve element without the plate spring 17 in the fuel-injection valve shown in FIG. 5;
FIG. 7B is a graph showing changes in the displacement of the valve element with the plate spring 17 in the fuel-injection valve shown in FIG. 5;
FIG. 8 is a diagram showing the succession of states in the process of suppressing the bouncing in the state transition depicted from the state (a) showing the close-valve condition to the state (e) showing the open-valve condition, which is achieved by the fuel-injection valve shown in FIG. 5;
FIG. 9A is a graph showing changes in the displacement of the valve element without the plate spring 17 in the fuel-injection valve shown in FIG. 5;
FIG. 9B is a graph showing changes in the displacement of the valve element with the plate spring 17 in the fuel-injection valve shown in FIG. 5;
FIG. 10 is a vertical cross section showing another example of the composition of the spring 17;
FIG. 11 is a vertical cross section showing another example of the composition of the spring 17;
FIG. 12 is a vertical cross section showing another example of the composition of the spring 17;
FIG. 13 is a vertical cross section showing an example of the composition of a mechanism for preventing the occurrence of a centering error between the spring adjuster and the spring;
FIG. 14 is a vertical cross section showing another example of the composition of a mechanism for preventing the occurrence of a centering error between the spring adjuster and the spring; and
The nozzle body 1 is a casing containing the ball 7, a fuel-swirling-flow generating device 25 in which a fuel passage for exerting a swirling force on the fuel is provided, and the rod 6. Also, in the bottom of the nozzle body 1, there is a fuel-injection hole 2, as well as a valve seat 3 (a seat face) upstream of the fuel-injection hole 2. The ball 7, which closes the fuel-injection hole 2, is connected to the bottom of the rod 6, and the top of the rod 6 is connected to the movable iron core (the plunger) 5. The ball 7 is guided in the same direction as the valve axis by an inner wall surface, which has a diameter slightly larger than that of the ball 7, and which is formed inside the fuel-swirling-flow generating device 25. Moreover, there is a precision-processed slide surface 26 on the rod 6, which slide surface 26 of the rod 6 is guided in the direction of the valve axis by the inner surface of the nozzle body 1.
On the rod 6, there is a shoulder 8 facing the stopper 9 disposed above the slide surface 26. The valve element 4 can slide from the bottom position at which the ball 7 contacts the valve seat 3 to the top position at which the shoulder part 8 contacts the stopper 9. The thickness of the stopper 9 is set such that a gap is formed between the movable iron core 5 and the inner iron core 10 when the valve element 4 is located at the top position. Fuel is fed from the fuel-feed inlet 16, and introduced to the fuel-injection hole 2 through the fuel passages 51–59.
In the hole which passes through the center part of the inner iron core 10 along the axis, a spring adjuster 11, the first spring 12, a linked movable member 13, and the second spring 17 are disposed in succession. The spring adjuster 11 is fixed to the inside surface of the inner iron core 10. The top and bottom of the spring 12 contact the bottom of the spring adjuster 11 and the top of the linked movable member 13, respectively, and the spring 12 is set in a compressed state. Also, the top and bottom of the second spring 17 contact the bottom of the linked movable member 13 and the top of the valve element 4, respectively, and the spring 17 is set in a compressed state. The linked movable member 13 can slide along the axis in the hole which passes through the center part of the inner iron core 10.
The spring force due to the spring 12 is transmitted to the valve element 4 via the linked movable member 13; and the ball 7 of the valve element 4 is pressed against the valve seat 3. In this state of the valve element 4, since the fuel passage is closed, fuel is not injected from the fuel-injection hole 2.
Expressing the mass quantity of the mass 32, the displacement of the mass 32, the mass quantity of the mass 30, and the displacement of the mass 30, the spring constant of the spring 33, and the spring constant of the spring 31 by m2, x2, m1, x1, k2, and k1, respectively, the equations of motion are described by the following equations (1) and (2).
In the following steps 91–96, which obtain both the values of the spring constants k1 and k2, and those of the mass quantities m1 and m2 of the mass 30 and the mass 32, which minimize the amount of the fuel secondarily injected by the rebound, will be explained.
Table 3 for the analysis of variance is created based on the relational list between values of the objective function and combinations of values for the design variables in Table 2. Further, the reliability and the confidence limit of the obtained equation expressing a curved surface for estimating the amount of the fuel secondarily injected due to rebound are calculated based on Table 3. The values of the reliability and the confidence limit correspond respectively to those of the mass quantities m1 and m2, and the spring constants k1 and k2 minimizing the amount of the secondarily injected fuel, which is obtained by the process of steps 91–96.
The obtained equation expressing a curved surface for estimating the amount of the fuel secondarily injected due to rebound is graphically expressed along with the region of the design variables minimizing the fuel secondarily injected due to rebound; that is, the conditions of the mass quantities m1 and m2, and the spring constants k1 and k2 minimizing the amount of the fuel secondarily injected due to rebound are obtained. An example of the graphic expression is shown in FIG. 4, which shows a three-dimensional graph expressing the amount of the fuel secondarily injected due to rebound with respect to the mass quantity m1 of the mass 30 and the spring constant k2 of the spring 33, when the mass quantity m2 of the mass 32 and the spring constant k1 of the spring 31 are given. The region 50 of the design variables minimizing the fuel secondarily injected due to rebound is read off the three-dimensional graph shown in FIG. 4. If the region 50 does not satisfy the design conditions, another optimal-region candidate is searched out.
m1*m2 1st*1st
1st*2nd
1st*3rd
2nd*1st
2nd*2nd
2nd*3rd
3rd*1st
The plate spring 17′ can be used in place of the spring 17 as shown in FIG. 5A, and this makes it possible to provide a shorter fuel-injection valve 100′. The plate spring 17′ includes a stopping face against which the bottom of the linked movable member 13′ butts, and, with the stopping face oriented upward, is set inside the hole, which possesses an aperture at the top of the movable iron core 5. In this embodiment, the plate spring 17′ is shaped as a ring plate member which possesses notches 170 on its inner periphery, as shown in FIG. 5B, which represents a cross section of the plate spring 17′, as seen along line A–A′ in FIG. 5A. The outer peripheral side face of the plate spring 17′ is fixed to the inner surface of the hole in the top part of the movable iron core 5. There are parts projecting from the inner periphery of the plate spring, and they form the stopping face against which the bottom of the linked movable member 13′ butts.
(c) The valve element 4 butts against, the valve seat 3.
(d) Just after the collision, the linked movable member 13′ rebounds upward due to the shock of the collision. FIGS. 7A and 7B show two different cases of displacement changes of the valve element 4 and the linked movable member 13′, respectively. FIG. 7A and FIG. 7B are graphs showing changes in the displacement of the valve element with and without the plate spring 17′ in the fuel-injection valve shown in FIG. 5, respectively. The secondary oscillation system composed of the linked movable member 13′ and the spring 17′ is adjusted such that the characteristic frequency of this secondary oscillation system is equal or almost equal to the frequency of the shock force due to the collision. For example, it is appropriate to set the mass quantity of the linked movable member 13′ and the spring constant of the plate spring 17′ to 0.3–1.5 g and 100–1000 kgf/mm, respectively. By these settings, the secondary oscillation system functions as a shock absorber. That is, only the linked movable member 13′ rebounds significantly upward due to the shock force of the collision, which in turn suppresses the bouncing of the valve element 4.
The spring 17′ functions as a plate spring whose inner peripheral part is displaced in the valve axis direction, that is, it is bent. A load of about 2–10 kgf, due to the force caused by the spring 12, the force of inertia of the linked movable member 13′ and so on, is applied to the inner peripheral area of the spring 17′. If there are no notches 170 on the inner peripheral part, the stress in the inner peripheral area due to the above load becomes very large, and this makes it difficult to maintain the durability of the spring 17′. On the other hand, if the thickness of the spring 17′ is increased so as to decrease the stress, the spring constant of the spring 17′ becomes to large, and the bounce-suppressing effect is lost. By providing the notches 110, the stress generated in the inner peripheral area of the spring 17′ is reduced. Thus, it has become possible to create a spring with an appropriate spring constant and a high durability, in which there is no high degree of stress.
There are three notches in the plate spring 17′. By making the linked movable member 13′ contact three parts of the spring 17′, stable contact between the linked movable member 13′ and the spring 17′ can be always attained even if the spring is not completely flat, and the spring constant designated as the design value can be accurately attained. Therefore, it is not necessary to precisely control the flatness when fabricating the spring 17′, and this decreases its fabrication cost. Thus, the stable bounce-suppressing effect of the fuel injection valve according to this embodiment can be obtained. Further, since the support of the linked movable member 13′ is stable, the member rarely inclines, which in turn prevents the abrasion of the slide portion in the inner surface of the inner iron core 10.
A press working is suitable for fabricating the spring 17′ at a low cost. Although it is difficult to precisely control the flatness of the spring 17′ with a press working, since the precise control of the flatness is not necessary since the linked movable member 13′ is made to contact three positions of the spring 17′, a press working can be used to fabricate, the spring 17′.
Furthermore, it is possible to fabricate the linked movable member 13′ and the movable iron core 5 so as to provide a united structure, if this does not cause a problem from the viewpoint of shock-resistance between the linked movable member 13′ and the spring 17′, or a problem when determining the spring constant during the design of the spring 17′. This structure decreases the number of parts used in making the fuel-injection valve.
Although bouncing can be suppressed by making use of the viscosity resistance force of the fuel, since it is necessary to provide a narrow bypass passage for the fuel, precise size-control of the parts or portions, which form the narrow bypass passage is required. Further, since the change in the fuel viscosity due to an increase in the fuel temperature, etc. makes the bounce-suppressing effect unreliable a countermeasure to this problem is necessary.
Furthermore, it is desirable to reduce the slide-abrasion by applying surface-processing, such as quenching, nitrification, plating, and so on, to at least one among the outer surface of the linked movable member 13′, the inner surface' of the inner iron core 10, and the inner surface of the movable iron core 5.
Also, it is desirable to reduce the slide-abrasion by applying surface-processing, such as quenching, nitrification, plating, and so on, to one or both of the butting faces. of the linked movable member 13′ and the spring 17′.
An example of the bounce-suppressing process is shown in FIG. 6 and FIG. 7, and other processes may be possible depending on the spring load, and the shapes of the fuel passage, the magnetic circuit, the stopper, etc. For example, it be possible that if the electromagnetic force is interrupted during the open-valve state, the valve element 4 may become separated from the linked movable member 13′, and collide with the valve seat 3, while a very slight gap remains between the valve element 4 and the linked movable member 13′. In this situation, when the valve element 4 rebounds from the valve seat 3, since the linked movable member 13′ collides with the valve element 4 after a short time lag, the bouncing is suppressed.
If a decrease in the viscosity of the fuel does not cause a severe problem, the viscosity resistance force of the fuel between the outer surface of the linked movable member 13′ and the inner-wall surface of the inner iron core 10 can be used for bounce suppression. Since it is possible to make the linked movable member 13′ longer by making use of the fuel passage space inside the inner iron core 10, a large and stable fuel based viscosity resistance force can be obtained. In this composition also, the spring 17′ is not always necessary.
FIGS. 7A and 7B show two different cases of displacement changes of the valve element 4 and the linked movable member 13′, respectively. FIG. 9A and FIG. 9B are graphs showing changes in the displacement of the valve element with and without the plate spring 17′ in the fuel-injection valve shown in FIG. 5, respectively. In FIG. 9A, it is seen that a large bounce by the valve element 4 is occurring at the stroke end. On the other hand, in the fuel-injection valve 100′ with the linked movable member 13′, the bouncing of the valve element 4 is suppressed or completely prevented as shown in FIG. 9B.′
Tp in FIGS. 9A and 9B indicates the time interval of the interruption of the electromagnetic force to the starting of the motion of the valve element 4, from the closed position to the open position. When it is required that a small amount of fuel be injected with a single injection, Tp is shortened. In a conventional fuel-injection valve, if Tp is significantly shortened, the valve element 4 moves towards the valve seat 3 during the bouncing.
Although it is desirable for the spring 17′ to be made of a metallic material, resin can be used for the spring 17′ if the durability is ensured. Resin is advantageous if the spring constant is set to a comparatively small value.
Another embodiment of the spring 17 will be explained with reference to FIG. 10. By providing a smaller outer-diameter portion (a constricted portion) 17″ on the bottom part of the linked movable member 13″ the stiffness of the bottom part is decreased, allowing it to possess a spring-like property. If one attempts to prevent the deterioration of the magnetic property of the movable iron core 5 due to the remaining processing strain caused by processing the core 5 to either create a spring portion in the core 5 or fix a spring member to the core 5, it is desirable to use the constricted portion 17″ provided in the bottom part of the linked movable member 13″ as a spring. In this embodiment, a large-diameter portion 61 is also formed below the constricted portion 17″, so as to increase the butting area between the linked movable member 13″ and the valve element 4 (the top face of the rod 6). In this way, the butting pressure applied to the bottom face of the linked movable member 13″ and the top face of the rod 6 can be reduced, which in turn prevents butting abrasion. If butting abrasion can be prevented by other measures, the large-diameter portion of the linked movable member 13″ is not necessary.
Further, another embodiment of the spring 17 is explained below with reference to FIG. 11. In this embodiment, the spring portion 17′″ is composed of a support part 63 and a deformed part 62. The deformed part 62 is bent with respect to the support part 63, which functions as a fulcrum. Thus, the deformed part 62 works as a spring. If the composition of a spring with a weak spring constant is attempted by adopting the structure of the spring 17′ using the compression deformation, as shown in FIG. 10, it is inevitable in some cases that the smaller-diameter portion becomes too thin, and the necessary strength cannot be secured. On the other hand, in this embodiment, since the spring 17′″ uses a force due to a bending deformation, it is possible to create a comparatively weak spring constant while securing the necessary thickness.
Furthermore, another embodiment of the spring 17 will be explained with reference to FIG. 12. In this embodiment, the circular bottom face of the linked movable member 13″″ has a convex surface, and the top face of the rod 6 of the valve element 4 has a flat surface. With the above shapes, a spring function can be obtained due to Hertzian contact. According to this embodiment, since the linked movable member 13″″ contacts the valve element 4 in a line-contact manner, both the member 13″″ and the valve element 4 contact each other more uniformly on the periphery as compared to when the member 13″″ and the valve element 4 contact to each other in a surface-contact manner. Thus, the variation in the spring force is small, and a stable bounce-suppression effect can be obtained.
The internal combustion engine 1000 includes a plurality of cylinders 1002, and each cylinder 1002 also includes a piston 1001, an air-intake valve 1003, an ignition plug 1005, and a fuel-injection valve 100. The air-intake valve 1003 is opened and closed in synchronization with the reciprocal motion of the piston 1001, and intake, air is introduced into each cylinder 1002. Fuel is fed to the fuel-injection valve 100 from a fuel feed system composed of a fuel tank, pumps, and so on, which are not shown in this figure. Current is fed to the fuel-injection valve 100 by an engine control unit 1007 and a fuel-injection valve-drive circuit 1008, and fuel injection is further performed according to the operational state of the internal combustion engine 1000. A mixture of intake-air and fuel is ignited and burned with the ignition plug 1005. Gas generated by this process is expelled by opening an exhaust valve 1004. By fabricating an internal combustion engine with an electromagnetic fuel-injection valve according to the present invention, an internal combustion engine with excellent fuel-consumption, engine power, and gas-exhaustion characteristics can be implemented, because the amount of fuel injected can be accurately controlled.
Additionally, although an electromagnetic force is used to drive the valve element 4 along the axis, use of another drive means can achieve the same effects as those obtained by means of electromagnetic force. For example, a drive means for driving the valve element 4 along the axis by using the fuel pressure to create a pressure difference between the upper and lower sides of the valve element 4, can be applied to the fuel-injection valve according to the present invention.
Although the range of motion along the axis of the valve element 4 is determined by the stopper 9, if the valve element 4 has a range of motion which is restricted by the bottom face of the inner iron core 10, it will naturally achieve the same effects as the above embodiments.
Patent CitationsCited PatentFiling datePublication dateApplicantTitleUS4515343Mar 28, 1984May 7, 1985Fev Forschungsgesellschaft fur Energietechnik und ver Brennungsmotoren mbHArrangement for electromagnetically operated actuatorsUS4749892Jun 18, 1987Jun 7, 1988Colt Industries Inc.Spring arrangement with additional mass for improvement of the dynamic behavior of electromagnetic systemsUS4798188 *Nov 30, 1987Jan 17, 1989Aisan Kogyo Kabushiki KaishaMethod of controlling injectorUS4883025Feb 8, 1988Nov 28, 1989Magnavox Government And Industrial Electronics CompanyPotential-magnetic energy driven valve mechanismUS4917352May 6, 1988Apr 17, 1990Regie Nationale Des Usines RenaultInjector for engine with spark ignition and direct injectionUS4986246Oct 20, 1989Jan 22, 1991Robert Bosch GmbhValve for the metered admixture of volatilized fuel to the fuel-air mixture of an internal combustion engineUS5127585Aug 26, 1991Jul 7, 1992Siemens AktiengesellschaftElectromaagnetic high-pressure injection valveUS5348224Nov 24, 1992Sep 20, 1994Hydro Flame CorporationGas flow modulatorUS5358005Oct 28, 1993Oct 25, 1994Honeywell Inc.Solenoid valve with dirt trapUS5458294Apr 4, 1994Oct 17, 1995G & L Development, Inc.Control system for controlling gas fuel flowUS5464191Jan 6, 1994Nov 7, 1995Envirovac, Inc.Solenoid actuated valveUS5813654Apr 24, 1997Sep 29, 1998Lucas IndustriesElectrically operated trigger valve for fuel injection pumpUS6474572 *Mar 2, 2000Nov 5, 2002Hitachi, Ltd.Fuel-injection valveJPH01159460A Title not availableJPH06127962A Title not availableJPH06146886A Title not availableJPS59205084A Title not available* Cited by examinerReferenced byCiting PatentFiling datePublication dateApplicantTitleUS7722342Mar 9, 2007May 25, 2010Hitachi, Ltd.Pump apparatus and power steeringUS7819344Jan 18, 2007Oct 26, 2010Hitachi, Ltd.Electro-magneto fuel injectorUS8371515Apr 9, 2009Feb 12, 2013Hitachi, Ltd.Electro-magneto fuel injectorUS20070075166 *Dec 5, 2006Apr 5, 2007Masahiro TsuchiyaFuel-injection valveUS20070253855 *Mar 9, 2007Nov 1, 2007Hitachi, Ltd.Pump Apparatus and Power SteeringUS20090188996 *Apr 9, 2009Jul 30, 2009Hitachi, Ltd.Electro-Magneto Fuel InjectorUS20120305822 *May 9, 2012Dec 6, 2012Delphi Technologies, Inc.Electronic control valve having an integral non-contact noise mitigation device* Cited by examinerClassifications U.S. Classification239/585.1, 251/129.21, 239/900, 239/533.9, 239/585.5International ClassificationF02M61/20, F02M61/10, F02M51/06, F02M63/00, F02M51/00Cooperative ClassificationY10S239/90, F02M51/061, F02M2200/306, F02M61/205, F02M51/0682European ClassificationF02M61/20B, F02M51/06B2E2B, F02M51/06BLegal EventsDateCodeEventDescriptionAug 23, 2010REMIMaintenance fee reminder mailedJan 16, 2011LAPSLapse for failure to pay maintenance feesMar 8, 2011FPExpired due to failure to pay maintenance feeEffective date: 20110116RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services