High pressure fuel pump

Abstract

A fuel pump includes a housing provided with an axial bore defining a compression chamber. The pump is further provided with a cylindrical piston slidably arranged in the bore, the piston extending from a top extremity that is inside the bore, defining a high pressure extremity, to a lower extremity, defining a low pressure extremity. The piston is able to reciprocally slide between a lower position where fuel at low pressure enters the compression chamber via an inlet and, a top position where fuel present in the compression chamber is pressurized before being expelled via an outlet. The piston is also provided with a recess surrounded by a peripheral wall arranged on its high pressure extremity, the recess and peripheral wall enabling the piston to expand radially when fuel in the compression chamber is pressurized.

Claims

1. A fuel pump of a fuel injection equipment of an internal combustion engine, said fuel pump comprising: a housing provided with an axial bore defining a compression chamber; and a cylindrical piston slidably arranged in the axial bore, the cylindrical piston extending from a top extremity that is inside the axial bore, defining a high pressure extremity, to a lower extremity, defining a low pressure extremity, the cylindrical piston being able to reciprocally slide between a lower position where fuel at low pressure enters the compression chamber via an inlet and, a top position where fuel present in the compression chamber is pressurized before being expelled via an outlet, wherein the cylindrical piston is provided with a dilation mean arranged on its high pressure extremity, said dilation mean enabling the cylindrical piston to expand radially when fuel in the compression chamber is pressurized; wherein the dilation mean is a recess provided on a top face of the cylindrical piston, said recess being surrounded by a peripheral wall integral to the cylindrical piston; wherein the dilation mean further comprises a pressure drop feature enabling pressurized fuel to drop in pressure and to flow toward a low pressure circuit, the location of said pressure drop feature limiting the portion of the cylindrical piston that expands under fuel pressure; and wherein the pressure drop feature comprises a groove ring arranged on the outer cylindrical face of the peripheral wall and a fuel path extending from said groove ring toward the low pressure circuit.

2. A fuel pump as set in claim 1 wherein the recess defines a cylindrical volume.

3. A fuel pump as set in claim 1 wherein said fuel path comprises a flat arranged on the outer cylindrical face of the cylindrical piston.

4. A fuel pump as set in claim 1 wherein the diameter of the cylindrical piston is larger above the groove ring than below the groove ring so that the clearance between the cylindrical piston and the axial bore is increased below the groove ring creating the fuel path wherein pressurized fuel in the groove ring flows toward the low pressure circuit.

5. A fuel pump as set in claim 1 wherein the dilation mean is a circular groove extending from a top face of the cylindrical piston, said circular groove being surrounded by a peripheral wall integral to the cylindrical piston.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present invention is now described by way of example with reference to the accompanying drawings in which:

(2) FIG. 1 is a schematic axial section of a pump as per a main embodiment of the invention.

(3) FIG. 2 is a schematic axial section of an alternative embodiment of a pump of the invention.

(4) FIG. 3 is a schematic axial section of yet another alternative embodiment of a pump of the invention.

(5) FIG. 4 is a schematic diagram of the radial forces distribution.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

(6) In the following description, similar elements will be designated with the same reference numbers. Also, to ease and clarify the description a top-down orientation will be followed in reference to the orientation of the figures. Therefore, words and expressions such as top, upper, lower, over, under . . . may be utilized without any intention to limit the scope of the invention.

(7) A main embodiment is now described in reference to FIG. 1 where an axial section of a high pressure pump 10 is schematically represented. The pump 10 has a housing 12 in which is provided a bore 14 extending along a main axis A from a top end, defining a compression chamber 16, to a lower end, not represented, opening outside the housing 12. Inside the bore 14 is slidably arranged a piston 18. A functional clearance C is maintained between the inner cylindrical face of the bore 14 and the outer cylindrical face of the piston 18 enabling displacement of the piston. 18. The pump 10 is further provided with non-represented controlled inlet and outlet enabling fuel to flow in and out the compression chamber 16.

(8) In the main embodiment of FIG. 1, the piston 18 is provided with a top cylindrical recess 20 upwardly opening in the compression chamber 16. The recess 20 is surrounded by a peripheral wall 22 integral to the piston 18 and, the volume of the compression chamber 16 of this first embodiment comprises the volume of the bore 14 that is above the piston 18 to which is added the volume of the recess 20.

(9) In operation the piston 18 is actuated by a non-represented rotating cam that reciprocally displaces the piston 18 between a top position PT, FIG. 1, and a low position PL, FIGS. 2 and 3. The fuel can be pressurized at several thousand bars that generate dilation of the pump constituents. The top part of the housing 12 expends and has the tendency to open-up the upper end of the functional clearance C. The pressurized fuel inside the recess 20 generates outwardly oriented radial forces F1 on the peripheral wall 22 that creates radial expansion of the peripheral wall 22. This expansion compensates the dilation of the bore 14 and avoids the opening of the functional clearance C. The pressurized fuel entering the functional clearance C generates on the peripheral wall 22 inwardly oriented forces F2, opposed in direction of the outward forces F1, whose intensity decreases as being more distant from the compression chamber 16.

(10) The deformation of the peripheral wall 22 is a consequence of the outwardly oriented forces F1 and of the inwardly oriented F2. The skilled person will understand that the barrel-type expansion of the peripheral 22, as represented on FIG. 1, is a non-limiting exaggerated illustration.

(11) An alternative to the main embodiment is now described in reference to FIG. 2, by ways of differences with the main embodiment of FIG. 1. In said alternative, the recess 20 is limited to a deep circular groove 24 axially extending from the top of the piston 18 and upwardly opening in the compression chamber 16. As visible on FIG. 2, the peripheral wall 22 is identical as in the main embodiment. It externally surrounds the deep circular groove 24 and, inwardly, the circular groove 24 is bordered by an inner cylindrical core 26 that fills the majority of the volume of the recess 20 of the main embodiment. Therefore, in this alternative, the volume increase of the compression chamber 16 is limited to the volume of the circular groove 24.

(12) In operation, the pressure inside the groove 24 generates on the peripheral wall 22 the same outwardly oriented radial forces FR generating similar expansion as in the main embodiment and also, generates inwardly oriented radial forces on the inner cylindrical core, said inward forces not generating any noticeable deformation of the inner core.

(13) In this alternative, the opening of the functional clearance C is compensated by the deformation of the peripheral wall 22 without important increase of the volume of the compression chamber 16.

(14) In non-represented further alternatives, the inner core 26 could be non-integral to the piston 18 and fixed inside the recess 20. Also, the recess 20 of the main embodiment is described as a cylindrical volume but, other shapes such as a conical recess or, two or more adjacent cylindrical volumes on the top of each other are possible alternatives.

(15) In FIG. 3, the piston 18 is provided with a groove ring 28 arranged on the external face of the peripheral wall 22. From said groove ring 28 downwardly extends a fuel path 30. The purpose of the ring 28 and associated path 30 is to enable a fuel pressure drop, the location of the ring 28 defining where said pressure drop occurs and where to limit the expansion of the peripheral wall 22.

(16) The fuel path 30, as represented on FIG. 3, can be a flat arranged on the outer cylindrical surface of the piston 18, directing the fuel from the annular groove 28 to the backleak. In this case, the groove ring 28 acts as a pressure relief since the pressurized fuel, entering the functional clearance C, generates inwardly oriented forces F2 from the top of the piston down to the groove 28 only. When arriving at the groove 28, the fuel pressure suddenly decreases to a low pressure level generating no deformation of the wall.

(17) An alternative to the passage 30 is represented on FIG. 4 where, instead of a flat wherein can flow fuel, the diameter of the piston 18 below the groove 28 is smaller than the diameter above the groove 28. Therefore the clearance below the groove 28 is larger and it enables fuel flow at low pressure below the groove 28.

(18) The following references have been utilized in this description: 10 pump 12 housing 14 bore 16 compression chamber 18 piston 20 recess 22 peripheral wall 24 circular groove 26 inner cylindrical core 28 groove ring 30 fuel passage A main axis C functional clearance PT top position PL low position FR Radial forces