Patent Grant
7124966
Not Applicable
Not Applicable
Not Applicable
The present invention generally relates to check valves used in fuel injectors and, more particularly, to check valves used in high pressure unit fuel injectors for diesel engines.
Fuel injectors typically use a check valve in the fuel path between an injector pumping element and an injector nozzle element. The check valve is designed to prevent a back flow of fuel into the pumping element once the delivery of fuel is complete. The check valve also prevents combustion gases from entering the pumping element in the event such gasses pass through valve associated with the nozzle element.
In engines with high ratings, flow irregularities often referred to as knocking has occurred in some injectors during high output operation. This knocking is believed to be due to unstable motion of the check valve disk during the pumping stroke when the disk should be seated on a ledge spaced from the valve seat. It is believed that rapid radial outflow of fuel over the upper side of the disc to passages through the disk, typically in the form of scallops at edges of the disk, causes momentary reductions in pressure above the disk sufficient to allow system pressure below the disk to lift it erratically from the ledge. In an effort to reduce knocking, attempts have been made to reduce the radial flow path of fuel over the top surface of the check valve disk.
U.S. Pat. No. 5,328,094, the disclosure of which is expressly incorporated herein in its entirety by reference, discloses a fuel injector check valve having a plurality of equally spaced holes. The plurality of holes are equally spaced in a ring near the fuel delivery opening.
U.S. Pat. No. 5,797,427, the disclosure of which is expressly incorporated herein in its entirety by reference, discloses a fuel injector check valve having a plurality of notches or slots. The notches or slots have inner edges that are concave in shape and are located near the fuel delivery opening to reduce the radial distance between the fuel delivery opening and the notches.
While these prior attempts may have somewhat reduced flow irregularities, they have reduced the seal area and require relatively large loads to open. Accordingly, three is a need in the art for an improved fuel injector check valve.
The present invention provides a fuel injector check valve which overcomes at least some of the above-noted problems of the related art. According to the present invention, a high pressure unit fuel injector includes, in combination, a member with a fuel delivery opening to be intermittently supplied with high pressure fuel and a valve seat encircling the fuel delivery opening. A valve cage includes a check-valve chamber adjacent the valve seat. The check-valve chamber includes an annular ledge facing the valve seat and an inwardly facing wall surrounding the ledge. A disk is located within the check-valve chamber and has opposite first and second faces alternately seatable against the valve seat and the ledge respectively. The disk has an outer edge in opposed relation to the wall and having limited radial clearance therefrom when centered in the check-valve chamber. The disk has a plurality of openings between the first and second faces and a groove formed in the first face.
According to another aspect of the present invention, a high pressure unit fuel injector comprises, in combination a member with a fuel delivery opening to be intermittently supplied with high pressure fuel and a valve seat encircling the fuel delivery opening. A valve cage includes a check-valve chamber adjacent to the valve seat. The check-valve chamber includes an annular ledge facing the valve seat and an inwardly facing wall surrounding the ledge. A disk is located within the check-valve chamber and has opposite first and second faces alternately seatable against the valve seat and the ledge respectively. The disk has an outer edge in opposed relation to the wall and having limited radial clearance therefrom when centered in the check-valve chamber. The disk has a plurality of openings between the first and second faces and a circular-shaped groove formed in the first face about a center of the disk. The groove intersects the plurality of openings and is located radially outward of the fuel delivery opening.
From the foregoing disclosure and the following more detailed description of various preferred embodiments it will be apparent to those skilled in the art that the present invention provides a significant advance in the technology of fuel injector check valves. Particularly significant in this regard is the potential the invention affords for providing a high quality, reliable assembly with improved operational performance. Additional features and advantages of various preferred embodiments will be better understood in view of the detailed description provided below.
These and further features of the present invention will be apparent with reference to the following description and drawings, wherein:
It should be understood that the appended drawings are not necessarily to scale, presenting a somewhat simplified representation of various preferred features illustrative of the basic principles of the invention. The specific design features of the fuel injector check valve as disclosed herein, including, for example, specific dimensions, orientations, and shapes of the openings and grooves will be determined in part by the particular intended application and use environment. Certain features of the illustrated embodiments have been enlarged or distorted relative to others to facilitate visualization and clear understanding. In particular, thin features may be thickened, for example, for clarity or illustration. All references to direction and position, unless otherwise indicated, refer to the orientation of the fuel injector check valve illustrated in the drawings. In general, up or upward refers to an upward direction within the plane of the paper in
It will be apparent to those skilled in the art, that is, to those who have knowledge or experience in this area of technology, that many uses and design variations are possible for the improved fuel injector check valve disclosed herein. The following detailed discussion of various alternative and preferred embodiments will illustrate the general principles of the invention with reference to a fuel injector of the high pressure, unit fuel injection type and, more particularly, a fuel injector intended for use in engines manufactured by Electro-Motive Division (EMD) of General Motors. It is noted, however, that other high pressure direct injection fuel injectors for diesel fuel and other liquid and semi-liquid fuels are within the scope of the present invention. Other embodiments suitable for other applications will be apparent to those skilled in the art given the benefit of this disclosure.
Referring now to the drawings,
Clamped main injector components include a spray tip 16 carrying a nozzle valve 18, a spring cage 20 carrying a valve spring 22, a check-valve cage 24 carrying a check valve disk 26, a spacer or body 28, and a bushing 30. The bushing 30 forms a vertically extending central passage at the central axis 32 of the fuel injector 10 which receives a reciprocable plunger 34. Passages 36, 38 in the main body and the bushing supply fuel to the central passage for pumping under high pressure by the plunger 34. A follower 40 engages the upper end of the plunger 34 for downwardly actuating the plunger 34 in response to the engagement of a cam.
The amount and timing of fuel injected each cycle is mechanically controlled in a known manner. A rack 42 engages a gear 44 secured to the plunger 34 to selectively rotate the plunger 34 within the bushing 30 to vary the length of the pumping stroke. It is noted that other known means for mechanically or electronically controlling the fuel rate and timing can alternatively be utilized.
As best shown in
The spacer or body 28 includes a flat lower surface which sealingly engages the upper surface of the check valve cage 24. A central fuel delivery opening or orifice 60 extending through the spacer 28 connects the pumping chamber 62 formed in the bushing 30 and bounded by the plunger 34 with the check-valve chamber 46. The lower surface of the spacer 28 forms a check valve seat 64 formed around the fuel delivery opening 60.
As best shown in
Formed in the upper surface 66 of the disk 26 is an annular-shaped groove 74 coaxial with a central axis 76 of the disk 26. The illustrated groove 74 is arcuate or arched in cross-section but other suitable shapes can be utilized. The groove 74 is sized and shaped to intersect the openings 72 and provide a generally equal fuel path in a radial direction even at locations between the openings 72. The illustrated groove 74 has an inner edge 78 radially inward of the openings 72 and an outer edge 80 which intersects the openings 72. The groove 74 provides a fuel pathway along the upper surface of the disk 26 which is generally equal in each radial direction. The groove 74 is also spaced away from the fuel delivery opening 60 to provide an increased seal area.
A preferred embodiment of the check valve disk 26 for injectors of EMD engines, the disk 26 is made of alloy steel and has a thickness of about 0.047 inches and a diameter of about 0.375 inches. Three equally spaced scallops 72 have a radius of about 0.141 inches and a depth of about 0.076 inches. The groove 74 has an inner edge 78 located at a radius of about 0.107 inches, a depth of about 0.004 inches, and a cross-sectional radius of about 0.015 inches.
In operation, low pressure fuel is admitted through the supply passages to a supply or fill port 82 and into the pumping chamber 62. Rotation of the cam against the follower 40 cyclically reciprocates the plunger 34 down and up within the pumping chamber 62 to pressurize and pump controlled amounts of fuel from the pumping chamber 62. The volume of fuel is controlled by the position of the rack 42 and the gear 44 which mechanically rotate the plunger 34. When the plunger 34 covers the fill port 82, a pressure wave is generated which opens the check valve by downwardly moving the disk 26 off the valve seat 64, and travels down through the passages within the check valve cage 24, the spring cage 20, and the nozzle tip to act on the nozzle valve 18. Usually the first pressure wave is sufficient to lift the nozzle valve 18 off its seat and injection begins. If the pressure wave is insufficient to lift the nozzle valve 18, the pressure build-up which immediately follows will do so.
As the plunger 36 descends, fuel discharged from the pumping chamber 62 is passed at high pressure down through the fuel delivery opening 60, radially outward from the fuel delivery opening over the upper surface 66 of the disk 26 to the groove 74, and along the groove 74 to the openings 72 to break the seal between the check valve disk 26 and the valve seat 64. This initial flow path which break the seal is best shown in
The nozzle valve 18 stays lifted during the time fuel is being delivered by the plunger 36 to the spray tip 16. When a helix edge 84 of the plunger 36 uncovers the spill port 86, pressure above the plunger 36 drops to fuel supply pressure and the check valve disk 26 upwardly seats onto the valve seat 64 formed by the spacer 28 to close the check valve and seal the fuel delivery opening 60 leading through the spacer 28 to the check valve chamber 46. As these event s occur, pressure in the nozzle or spray tip 16 drops rapidly and the nozzle valve 18 closes and fuel injection ends when pressure in the spray tip 16 drops to the closing pressure of the nozzle valve 18. Residual pressure in the check valve chamber 46 holds the check valve disk 26 upward against the valve seat 64 closing the fuel delivery opening 60 against the return flow of fuel and maintaining a barrier against the intrusion of cylinder combustion gases into the injector passages 36, 38 and the pumping chamber 62.
It is apparent from the foregoing disclosure that fuel injector check valve of the present invention provides substantial performance improvements by increasing the radial flow path, compared to prior art designs, but providing a generally equal flow path in each radial direction. The performance improvements include a larger seal area, even and steady opening, and lower opening load requirements.
From the foregoing disclosure and detailed description of certain preferred embodiments, it will be apparent that various modifications, additions and other alternative embodiments are possible without departing from the true scope and spirit of the present invention. The embodiments discussed were chosen and described to provide the best illustration of the principles of the present invention and its practical application to thereby enable one of ordinary skill in the art to utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated. All such modifications and variations are within the scope of the present invention as determined by the appended claims when interpreted in accordance with the benefit to which they are fairly, legally, and equitably entitled.
| Number | Name | Date | Kind |
|---|---|---|---|
| 3249308 | Cadiou | May 1966 | A |
| 3379374 | Mekkes | Apr 1968 | A |
| 3403632 | Hulsing | Oct 1968 | A |
| 5251871 | Suzuki | Oct 1993 | A |
| 5328094 | Goetzke | Jul 1994 | A |
| 5797427 | Buescher | Aug 1998 | A |
| 6817546 | Battistini et al. | Nov 2004 | B1 |
| 6881331 | Barnes | Apr 2005 | B1 |
| Number | Date | Country | |
|---|---|---|---|
| 20050263622 A1 | Dec 2005 | US |
