Patent Application
20250154925
The invention relates to a pump for use in a fuel delivery system. Aspects of the invention relate to a pump and to a fuel delivery system for an automotive vehicle comprising a pump.
In combustion engine systems, a fuel pump is used to pressurise fuel before it is injected into the cylinders of the engine. Modern compression-ignition engine systems often use a high-pressure fuel pump to feed a pressurised accumulator, known as a common rail, which acts as a reservoir to store the pressurised fuel and feed the individual fuel injectors. In compression-ignition internal engines, the fuel is pressurised to very high levels, typically in excess of 2000 bar. Such high pressures are difficult to manage and engine designers have to pay careful attention to controlling fuel leakages and protecting against damage to parts.
It is against this background that the invention has been devised.
According to an aspect of the invention there is provided a pump for a fuel injection system. The pump comprises: a main housing; a plunger housing arranged to be coupled to the main housing; and a gasket for arrangement between respective first and second opposed faces of the main housing and the plunger housing, in assembly, so as to seal a compression chamber defined between the main housing and the plunger housing as the gasket is compressed therebetween (i.e. between the main housing and the plunger housing) under an assembly load. The main housing comprises a valve bore extending to the first face of the main housing for supplying fuel to the compression chamber. The plunger housing comprises a plunger bore extending to the opposing second face of the plunger housing, defining a central axis of the compression chamber. In assembly, a central axis of the valve bore is radially offset from the central axis of the compression chamber such that a stiffness of the main housing varies circumferentially around the compression chamber to define a region of relatively low stiffness proximal to the valve bore and a region of relatively high stiffness distal from the valve bore. The gasket is arranged, when compressed under the assembly load, to reduce the load applied to the low stiffness region of the main housing relative to the load applied to the high stiffness region of the main housing.
In particular, the valve bore extends through the main housing to the first face, thereby reducing the stiffness of the main housing around the valve bore, particularly at the first face of the main housing. In assembly, the central axis of the valve bore is radially offset from the central axis of the compression chamber, and the offset (or misalignment) means that the stiffness of the main housing varies around the circumference of the compression chamber, i.e. varying circumferentially around an area of the main housing encircling the compression chamber in assembly. In particular, the main housing is relatively flexible in a circumferential region that is close, or proximal, to the central axis of the valve bore compared to a relatively stiff circumferential region of the main housing that is relatively distal from the central axis of the valve bore. Advantageously, the gasket is arranged, when compressed under the assembly load, to reduce the load applied to the low stiffness region of the main housing relative to the load applied to the high stiffness region of the main housing, thereby producing more uniform deformation of the main housing under the assembly load. Consequently, the sealing pressure is substantially uniform, mitigating wear and sliding movement between the main housing and the plunger housing.
Optionally, the gasket includes a body having: an opening for the compression chamber; a radially outer portion comprising a base portion extending in a base plane; and a radially inner portion comprising an uneven sealing surface that extends around the opening with a height (or axial distance), relative to the base plane, that varies circumferentially so that, in situ, compression of the sealing surface between the main housing and the plunger housing counteracts the assembly load to reduce the load applied to the low stiffness region of the main housing relative to the load applied to the relatively high stiffness region of the main housing. In this manner, flattening of the sealing surface under the assembly load generates a spring force acting to counteract the assembly load applied to the main housing to a greater extent in the relatively flexible region compared to the relatively stiff region.
For example, the sealing surface may include first and second circumferential sections, where the first circumferential section is being defined at a greater height, relative to the base plane, than the second circumferential section.
Optionally, the first circumferential section is at least 5% higher than the second circumferential section, relative to the base plane. Preferably, the first circumferential section is at least 10% higher than the second circumferential section, relative to the base plane. The first circumferential section may, for example, be less than, or equal to, 20% higher than the second circumferential section, relative to the base plane. In this manner, a suitable spring force is generated corresponding to the relative stiffness of the flexible region of the main housing compared to the stiff region of the main housing.
The first circumferential section may, for example, extend circumferentially through an angle of less than, or equal to, 180 degrees. Preferably, the first circumferential section may extend circumferentially through an angle of less than, or equal to, 160 degrees. The first circumferential section may, for example, extend circumferentially through an angle of greater than, or equal to, 90 degrees. Preferably, the first circumferential section may extend circumferentially through an angle of greater than, or equal to, 120 degrees. In this manner, the span of the first circumferential section may suitably correspond to the size of the valve bore and/or the offset of the central axis of the valve bore from the central axis of the pumping chamber.
Optionally, the first and second circumferential sections of the sealing surface are planar and extend parallel to the base plane. The sealing surface may further includes sloped, and/or curved, sections extending between the first and second circumferential section, for example.
In an example, the base portion of the gasket is arranged on the first face of the main housing, the first circumferential section is arranged relatively proximal to the central axis of the valve bore, aligned with the region of relatively low stiffness, and the second circumferential section is arranged relatively distal from the central axis of the valve bore, aligned with the region of relatively high stiffness. In another example, the base portion of the gasket is arranged on the second face of the plunger housing, the first circumferential section is arranged relatively distal to the central axis of the valve bore, aligned with the region of relatively high stiffness, and the second circumferential section is arranged relatively proximal to the central axis of the valve bore, aligned with the region of relatively high stiffness. In each example, the flattening of the sealing surface under the assembly load therefore acts to reduce the assembly load exerted on the relatively flexible region of the main housing compared to the assembly load exerted on the relatively stiff region of the main housing.
Optionally, the sealing surface is defined by a non-axisymmetric bead arrangement of the gasket. For example, the non-axisymmetric bead arrangement may be formed in the body of the gasket.
Optionally, the first and/or the second face comprises a protruding annular sealing portion that encircles the compression chamber, in assembly. For example, the annular sealing portion may be defined on the first face of the main housing, and the relatively flexible region of the main housing may be defined in a circumferential region of the annular sealing portion that is arranged proximally to the central axis of the valve bore and the relatively stiff region of the main housing may be defined in a circumferential region of the annular sealing portion that is arranged relatively distally from the central axis of the valve bore. Optionally, the gasket may include a step portion, between the radially outer portion and the radially inner portion, providing a step in the height of the gasket, relative to the base plane, for locating the gasket on the annular sealing portion, for example such that the opening of the gasket is aligned concentrically with the central axis of the pumping chamber.
Optionally, the gasket includes an upstanding locating member, received in an opening of the main housing, and/or of the plunger housing, for orienting the sealing surface of the gasket, in situ, with respect to the central axis of the compression chamber.
According to a further aspect of the invention there is provided a gasket of a pump for a fuel injection system. The gasket is arrangeable between a main housing and a plunger housing of the pump so as to seal a compression chamber defined between the main housing and the plunger housing as the gasket is compressed therebetween (i.e. between the main housing and the plunger housing) under an assembly load. The gasket includes a body having: an opening for the compression chamber; a radially outer portion comprising a base portion extending in a base plane; and a radially inner portion comprising an uneven sealing surface that extends around the opening. The sealing surface includes first and second circumferential sections, where the first circumferential section is defined at a greater height, relative to the base plane, than the second circumferential section.
According to another aspect of the invention there is provided a fuel delivery system comprising a pump or a gasket as described in a previous aspect of the invention.
According to yet another aspect of the invention there is provided a pump for a fuel injection system. The pump comprises: a main housing; a plunger housing arranged to be coupled to the main housing; and a gasket for arrangement between respective first and second opposed faces of the main housing and the plunger housing, in assembly, so as to seal a compression chamber defined between the main housing and the plunger housing as the gasket is compressed therebetween under an assembly load. The main housing comprises a valve bore extending to the first face of the main housing for supplying fuel to the compression chamber.
The plunger housing comprises a plunger bore extending to the opposing second face of the plunger housing, defining a central axis of the compression chamber. In assembly, a central axis of the valve bore is radially offset from the central axis of the compression chamber such that a stiffness of the main housing varies circumferentially around the compression chamber to define a region of relatively low stiffness proximal to the valve bore and a region of relatively high stiffness distal from the valve bore. The gasket comprises a body having: an opening for the compression chamber; and an uneven sealing surface that extends around the opening with a height, relative to a base plane of the body/gasket, that varies circumferentially so that, in situ, compression of the sealing surface between the main housing and the plunger housing counteracts the assembly load to reduce the load applied to the low stiffness region of the main housing relative to the load applied to the relatively high stiffness region of the main housing.
It will be appreciated that the various features of each aspect of the invention are equally applicable to, alone or in appropriate combination with, other aspects of the invention.
In order that the invention may be more readily understood, preferred non-limiting embodiments thereof will now be described, by way of example only, with reference to the accompanying drawings, in which like features are assigned like reference numbers, and in which:
In the following description, directional or relative references such as ‘upper’, ‘lower’, ‘above’ and ‘below’, relate to the orientation of the features as illustrated in the drawings, but such references are not to be considered limiting. The skilled reader will appreciate that pumps in accordance with embodiments of the invention may be oriented differently to the manner depicted in the drawings in practice.
The pump 1 generally comprises a main housing 12 and a plunger housing 14. The plunger housing 14 is coupled to the main housing 12, for example by threaded fastening means. In this manner, interfacing surfaces of the main housing 12 and the plunger housing 14 are compressed together by an assembly load, thereby sealing a compression chamber 16 defined between the main housing 12 and the plunger housing 14.
The main housing 12 comprises an inlet valve 20 and an outlet valve (not shown). The inlet valve 20 controls the flow of fuel into the compression chamber 16. The outlet valve (not shown) allows pressurised fuel to be conveyed from the compression chamber 16 to the downstream components of the fuel delivery system.
In more detail, the inlet valve 20 comprises a valve member 22 arranged for reciprocating movement within a valve bore 24 defined by the main housing 12. The valve bore 24 extends though the main housing 12 to a lower face 13 thereof, where the valve bore 24 opens into the compression chamber 16 and defines a valve seat 28. The valve member 22 comprises a valve stem 25 and a valve head 26. In assembly, the valve head 26 projects partially into the compression chamber 16. The diameter of the valve head 26 is sized so as to be larger than the diameter of the valve seat 28 at the lower face 13 of the main housing 12 such that, when the inlet valve 22 is in a closed state, the valve head 26 closes against the valve seat 28 so as to prevent the flow of fuel into the compression chamber 16.
Movement of the inlet valve 22 may, for example, be effected by means of an actuator (not shown), such as a solenoid actuator, and/or a valve spring (not shown). For example, the valve spring may be arranged so as to urge the valve head 26 away from the valve seat 28 toward an open position. When the pressure in the compression chamber 16 rises during a pumping stroke of the pump 1 this produces a force which acts against the valve spring. Closing of the inlet valve 20 can then be effected by energizing the actuator to exert an additional closing force on the valve stem 25. The additional closing force is sufficient to overcome the force of the valve spring such that the valve head 26 closes against the valve seat 28.
The plunger housing 14 comprises an axial plunger bore 40 within which a plunger (not shown) is arranged for reciprocating movement therein. The plunger bore 40 extends though the plunger housing 14 to an upper face 18 thereof, where an opening of the plunger bore 40 is defined. The plunger may be substantially cylindrical in shape and driven in a reciprocating linear motion with a close clearance fit with respect to the adjacent wall of the plunger bore 40. To give an example, a lower end of the plunger (not shown) may be arranged, in use, to contact an engine-driven cam (not shown). Accordingly, a plunger return spring (not shown) may also be disposed around the plunger housing 14, abutting a shoulder of the plunger housing 14 at one end thereof and, at the opposite end thereof, the return spring may abut against a cap, or equivalent shoulder feature, affixed to the lower end of the plunger, so as to urge the lower end of the plunger against the engine-driven cam.
The plunger bore 40 defines a central axis of the pumping chamber 16 in assembly, which extends from the plunger bore 40 to a corresponding area on the lower face 13 of the main housing 12, encompassing the respective openings of the inlet and outlet valves 20.
Accordingly, in use, fuel is admitted into the compression cylinder 16 through the inlet valve 20 and the plunger is driven upwards during a pumping stroke of the pump 1 to reduce the volume of the compression chamber 16 and thereby to pressurise the fuel disposed therein. Accordingly, the upper end of the plunger features an end face or compression surface for pressuring the fuel in the compression chamber 16. When the pressure of the fuel in the compression chamber 16 reaches a threshold value it is sufficient to cause the outlet valve (not shown) in the main housing 12 to open such that the pressurised fuel can be conveyed downstream, for example to the common rail accumulator.
In order to achieve the desired pressure in the compression chamber 16 during the pumping stroke, the compression chamber 16 must be substantially sealed so as to prevent or substantially eliminate egress of fuel from the compression chamber 16 other than via the outlet valve (not shown).
To provide sufficient sealing, the lower face 13 of the main housing 12 and/or the upper face 18 of the plunger housing 14 are therefore complementary to one another and may feature complementary annular sealing portions 17, as shown in
To provide effective sealing, the annular sealing portions 17 may feature a knife-edge design, as shown in
However, an issue with pumps of the design described above is that the valve bore 24 has the effect of reducing the stiffness of the surrounding region of the main housing 12, particularly toward the lower face 13 thereof. In a typical pump, the valve bore is arranged coaxially with the pumping chamber, so that any detrimental effects of the valve bore on the stiffness of the main housing are not too problematic.
However, in the example pump 1, a central axis of the valve bore 24 is radially offset from, or eccentric to, the central axis of the compression chamber 16, as shown in
Consequently, when subjected to the assembly loads that hold the main housing 12 and the plunger housing 14 together, there is relatively little resistance to deformation at the flexible region of the main housing 12, leading to non-uniform deformation of the main housing 12 and the plunger housing 14 around the compression chamber 16.
As a further consequence, the sealing pressure, i.e. the pressure on the interfacing surfaces 13, 18 of the main housing 12 and the plunger housing 14, also varies circumferentially around the compression chamber 16, which compromises the seal of the compression chamber 16 and promotes wear and sliding between the main housing 12 and the plunger housing 14. Radial dilation of the compression chamber 16 is also increased and radial movement of the inlet valve 22 is more pronounced, leading to sliding and wear on the valve head 28.
The degradation due to wear at the interface of the main housing 12 and the plunger housing 14 is further exacerbated in examples where the lower face 13 of the main housing 12, and/or the upper face 18 of the plunger housing 14, feature annular sealing portions with a knife-edge design as described above. In such examples, the small surface area provided for effective sealing generates a significant contact stress at the interface. Consequently, relative sliding of the main housing 12 and/or the plunger housing 14, during the pumping stroke, generates significant wear, which can lead to damage and increased leakage from the compression chamber 16, ultimately impairing the operation of the pump 1.
To mitigate these issues, a pump in accordance with embodiments of the present invention includes a gasket arranged at the interface between the opposing surfaces of the main housing and the plunger housing. Advantageously, when compressed under the assembly load, the gasket is configured to reduce the load applied to the low stiffness region of the main housing relative to the load applied to the high stiffness region of the main housing.
For example, the gasket may include a non-axisymmetric bead arrangement, which defines an uneven sealing surface that varies around its circumference in height, or axial distance, relative to a base plane of the gasket so that, in situ, compression of the sealing surface between the main housing and the plunger housing compensates for variations in the stiffness of the underlying (i.e. axially adjacent) regions of the main housing. In particular, flattening the sealing surface between the main housing and the plunger housing generates a spring force that acts to counteract the assembly loads to a greater extent in the region of relatively low stiffness than in the region of relatively high stiffness, thereby producing more uniform deformation of the main housing in the area encircling the pumping chamber.
Consequently, uneven sealing pressures, and friction, at the interfacing surfaces may be reduced, leading to an increased load capacity and/or fatigue life of the pump.
An exemplary pump 101 in accordance with an embodiment of the invention is provided in
The pump 101 generally comprises a main housing 112, a plunger housing 114, and a gasket 115. The plunger housing 114 is coupled to the main housing 112, with the gasket 115 arranged between the plunger housing 114 and the main housing 112. In this manner, the gasket 115 is compressed by the assembly loads between the interfacing surfaces of the main housing 112 and the plunger housing 114 so as to seal a compression chamber 116 defined therebetween.
The main housing 112 comprises an inlet valve 120 and an outlet valve (not shown). The inlet valve 120 controls the flow of fuel into the compression chamber 116. The outlet valve (not shown) allows pressurised fuel to be conveyed from the compression chamber 116 to the downstream components of the fuel delivery system.
In more detail, the inlet valve 120 comprises a valve member 122 arranged for reciprocating movement within a valve bore 124 defined by the main housing 112. The valve bore 124 extends though the main housing 112 to a lower face 113 thereof, where the valve bore 124 opens into the compression chamber 116 and defines a valve seat 128. The valve member 122 comprises a valve stem 125 and a valve head 126. In assembly, the valve head 126 projects partially into the compression chamber 116. The diameter of the valve head 126 is sized so as to be larger than the diameter of the valve seat 128 at the lower face 113 of the main housing 112 such that, when the inlet valve 122 is in a closed state, the valve head 126 closes against the valve seat 128 so as to prevent the flow of fuel into the compression chamber 116.
Movement of the inlet valve 122 may, for example, be effected by means of an actuator (not shown), such as a solenoid actuator, and/or a valve spring (not shown). For example, the valve spring may be arranged so as to urge the valve head 126 away from the valve seat 128 toward an open position. When the pressure in the compression chamber 116 rises during a pumping stroke of the pump 101 this produces a force which acts against the valve spring. Closing of the inlet valve 120 can then be effected by energizing the actuator to exert an additional closing force on the valve stem 125. In particular, the additional closing force is sufficient to overcome the force of the valve spring such that the valve head 126 closes against the valve seat 128.
The plunger housing 114 comprises an axial plunger bore 140 within which a plunger (not shown) is arranged for reciprocating movement therein. The plunger bore 140 extends though the plunger housing 114 to an upper face 118 thereof, where an opening of the plunger bore 124 is defined. The plunger may be substantially cylindrical in shape and driven in a reciprocating linear motion with a close clearance fit with respect to the adjacent wall of the plunger bore 140. To give an example, a lower end of the plunger may be arranged, in use, to be in contact with an engine-driven cam (not shown). Accordingly, a plunger return spring (not shown) may also be disposed around the plunger housing 114, abutting a shoulder of the plunger housing 114 at one end thereof and, at the opposite end thereof, the plunger return spring may abut against a cap, or equivalent shoulder feature, affixed to the lower end of the plunger, so as to urge the lower end of the plunger against the engine-driven cam.
The plunger bore 140 defines a central axis of the pumping chamber 116 in assembly, which extends from the plunger bore 140, through the intermediate gasket 115, to a corresponding area on the lower face 113 of the main housing 112, encompassing the respective openings for the inlet and outlet valves 120.
Accordingly, in use, fuel is admitted into the compression cylinder 116 through the inlet valve 120 and the plunger is driven upwards during a pumping stroke of the pump 101 to reduce the volume of the compression chamber 116 and thereby to pressurise the fuel disposed therein. Accordingly, the upper end of the plunger features an end face or compression surface for pressuring the fuel in the compression chamber 116. When the pressure of the fuel in the compression chamber 116 reaches a threshold value it is sufficient to cause the outlet valve (not shown) in the main housing 112 to open such that the pressurised fuel can be conveyed downstream, for example to the common rail accumulator.
In order to achieve the desired pressure in the compression chamber 116 during a pumping stroke, the compression chamber 116 must be substantially sealed so as to prevent or substantially eliminate egress of fuel from the compression chamber 116 other than via the outlet valve (not shown). To promote such sealing, the lower face 113 of the main housing 112 and/or the upper face 118 of the plunger housing 114 are complementary to one another and may feature complementary annular sealing portions 117, as shown in
The annular sealing portions 117 encircle the compression chamber 116 defined between the main housing 112 and the plunger housing 114, extending circumferentially around the opening of the plunger bore 140 and the corresponding area on the lower face 113 of the main housing 112, and protruding therefrom. As shown in
However, the valve bore 124 has the effect of reducing the stiffness of the surrounding region of the main housing 112 and a central axis of the valve bore 124 is radially offset from, or eccentric to, the central axis of the compression chamber 116. Consequently, the stiffness of the main housing 112 varies circumferentially in the region encircling the compression chamber 116, defining a region of relatively low stiffness (i.e. a flexible region) proximal to the valve bore 124, and a region of relatively high stiffness (i.e. a stiff region) distal from the valve bore 124. In particular, considering an annular region of the main housing 112 that is concentric with and encircles the compression chamber 116, the relatively flexible region may be defined in a circumferential section that is proximal to the valve bore 124 (due to the radial offset of the valve bore 124), and the relatively stiff region may be defined in another circumferential section that is distal from the valve bore 124, i.e. in a section arranged at a greater radial distance from the central axis of the valve bore 124. To give an example, the relatively flexible region and the relatively stiff region may be arranged on diametrically opposed portions of the annular sealing portion 117 of the main housing 112, aligned with the direction of the radial offset of the valve bore 124 from the central axis of the pumping chamber 116. Consequently, when subjected to the assembly loads that hold the pump 101 together, there is less resistance to deformation at the relatively flexible region than at the relatively stiff region.
In embodiments of the pump 101 in accordance with the present invention, the gasket 115 is advantageously designed to counteract the effects of such areas of reduced stiffness and thereby to mitigate relative movement of the plunger housing 114 during the pumping stroke, as shall be described in more detail with additional reference to
In the example shown in
The gasket 115 also includes an upstanding locating member 153, such as an axially extending foot, that extends away from the annular body 150 for orienting the gasket 115 in situ by engaging a corresponding opening of the main housing 112, and/or of the plunger housing 114. For example, as shown in
The body 150 of the gasket 115 features a concentric arrangement of a base portion 152, a step portion 154, and a non-axisymmetric bead arrangement 156. The base portion 152 therefore forms a radially outer portion of the gasket 115, taking the form of a substantially planar ring in this example, which is complementary to a corresponding mounting area on the lower surface 113 of the main housing 112. As best shown in
The step portion 154 extends radially inward from the base portion 152 and is designed to accommodate the protrusion of the annular sealing portion 117 from the lower surface 113 of the main housing 112. The step portion 154 therefore includes an axial step, or increment in the height of the gasket 115, relative to the base plane 158, for locating the gasket 115 on the annular sealing portion 117. The axial step may be achieved by a sloped, or otherwise curved, region that extends at an inclined angle to the base plane 158. The step portion 154 also includes a further region, radially inward of the sloped/curved region, configured to rest on the surface of the annular sealing portion 117. In this manner, the step portion 154 effectively defines an inner tier of the gasket 115, which extends at a greater height, or axial distance, from the base plane 158 to accommodate the raised surface of the annular sealing portion 117. Since the step portion 154 encloses the raised surface of the annular sealing portion 117, the step portion 154 also serves to locate the gasket 115 between the main housing 112 and the plunger housing 114 such that the opening 151 of the gasket 115 is substantially aligned with the opening of the plunger bore 140.
The non-axisymmetric bead arrangement 156 extends radially inward from the step portion 154 to the opening 151, and extends axially away from the base plane 158, to define an uneven sealing surface 160 around the opening 151 of the gasket 115. When the sealing surface 160 is compressed between the main housing 112 and the plunger housing 114, in situ, the uneven sealing surface 160 is substantially flattened. The deformation required to flatten the sealing surface 160 compensates for the variable stiffness of the underlying regions of the main housing 112. In particular, flattening the sealing surface 160 between the main housing 112 and the plunger housing 114 generates a spring force that acts to reduce the assembly loads at the relatively flexible region of the main housing 112, thereby producing more uniform deformation of the main housing 112 around the pumping chamber 116. For example, the compressed gasket 115 may generate a spring force having a larger axial component in an area underlying the relatively flexible region of the main housing 112, than the spring force produced in an area underlying the relatively stiff region of the main housing 112. Consequently, the deformation of the main housing 112 is reduced across that relatively flexible region, producing a more uniform sealing pressure around the circumference of the compression chamber 116.
To generate a suitable spring force, the uneven sealing surface 160 defined by the non-axisymmetric bead arrangement 156 therefore has a height, or axial distance, relative to the base plane 158, that varies around the circumference of the sealing surface 160 in a manner corresponding to the variation in the stiffness of the main housing 112 around the pumping chamber 116. The skilled person shall appreciate that this may be embodied in various suitable forms.
For example, around the circumference of the sealing surface 160, the height of the sealing surface 160 may vary between a maximum height and a minimum height relative to the base plane 158. A high point, or peak, of the sealing surface 160 may therefore be diametrically opposed to a low point, or trough, of the sealing surface 160 and, in situ, the locating member 153 may therefore orient the gasket 115 such that the high point lies in the direction of the central axis of the valve bore 124 relative to the central axis of the plunger bore 140. In which case, the low point may therefore lie in an opposing direction relative to the central axis of the plunger bore 140. In this manner, the high point may underlie the relatively flexible region of the main housing 112 and the low point may underlie the relatively stiff region of the main housing 112, such as the respective diametrically opposed portions of the annular sealing portion 117. Here it shall be appreciated that the term underlie is made with reference to the orientation shown in
In the present example, the arrangement of the sealing surface 160 is best shown with reference to
In this example, the first circumferential section 162 extends circumferentially through an angle of approximately 120 degrees, which corresponds to the span of the relatively flexible region of the main housing 112, and is suitable for mitigating the effects of the variable stiffness. However, in other examples, the first circumferential section 162 may extend circumferentially through an angle of less than, or equal to, 180 degrees, preferably, less than, or equal to, 160 degrees, according to the offset of the valve bore 124 and the resulting effects on the stiffness of the main housing 112. In general though, the first circumferential section 162 may extend circumferentially through an angle of at least 90 degrees, for example.
Referring again to
Accordingly, when the sealing surface 160 is compressed, and substantially flattened, in situ, the first circumferential section 162 is displaced to a greater extent than the second circumferential section 164, which generates a corresponding spring force acting to counteract the assembly loads. In particular, as the first circumferential section 162 is arranged proximal to the central axis of the valve bore 162, the spring force generated by the compression therefore acts to counteract the assembly loads to a greater extent at the relatively flexible region of the main housing 112 than at the relatively stiff region of the main housing 112. This has the effect of producing more uniform deformation of the main housing 112.
Accordingly, the sealing pressure, i.e. the pressure on the annular sealing portions 117 of the main housing 112 and the plunger housing 114, and the gasket 115, is substantially uniform, mitigating wear and sliding movement between the main housing 112 and the plunger housing 114. Additionally, radial dilation of the compression chamber 116 is reduced and radial movement of the inlet valve 122 is mitigated because of the uniform deformation, leading to reduced sliding and wear on the valve head 128.
It is envisaged that the pump 101 of the present invention will therefore provide a higher load capacity, and fatigue life, allowing for higher pumping loads and increased fuel pressures.
It will be appreciated by a person skilled in the art that the invention could be modified to take many alternative forms to that described herein, without departing from the scope of the appended claims.
For example, in an alternative embodiment, it shall be appreciated that the inlet valve 120 may be a passive valve such that the actuator may be omitted. In this case, the valve spring may be arranged so as to urge the valve member toward a closed state, i.e. such that the valve head is biased toward the valve seat. With such an arrangement, the spring constant of the valve spring can be selected such that opening of the inlet valve against the force of the valve spring is effected by means of a vacuum created within the plunger bore as the plunger makes its return stroke. As the pressure differential across the valve head increases it will cause the valve head to lift away from the valve seat against the force of the valve spring thereby allowing fuel to flow into the compression chamber. This, in turn, reduces the difference in the pressure above and below the valve head until the pressure differential is no longer sufficient to hold the inlet valve open against the force of the valve spring.
Furthermore, in the example shown in
Moreover, in other examples, the gasket 115 may instead be designed for arrangement on the upper surface 118 of the plunger housing 114. In which case, it shall be appreciated that the base portion 152 of the gasket 115 may instead correspond to the upper face 118 of the plunger housing 114 and the sealing surface 160 may extend away from the base plane 158 defined by the base portion 152 to define a high point distal from the central axis of the valve bore 124, and a low point proximal to the central axis of the valve bore 124 instead. For example, the first circumferential section 162 may be arranged to underlie the stiff region of the main housing 112 instead and, accordingly, the lower second circumferential section 164 may be arranged in alignment with the flexible region of the main housing 112 In this manner, when the gasket 115 is compressed under the assembly load, the spring force generated by the gasket 115 would again act to reduce the lad applied to the flexible region of the main housing 112 compared to the load applied to the stiff region of the main housing 112. In this example, it shall be appreciated that circumferential span of each of the first and second circumferential sections 162, 164 may also be adapted accordingly.
Furthermore, in the example shown in
Additionally, as described above, the bead arrangement 156 of the gasket 115 is non-axisymmetric, extending circumferentially around the opening 151 of the gasket 115, with a varying axial distance from the base plane 158 that defines the uneven sealing surface 160. However, as shown in the example of
Furthermore, in the example shown in
It shall be also appreciated that, in the examples described above, the gasket 115 may, for example, be formed from a suitable gasket material for high pressure pumps with a surface finish for reducing wear. To give an example, the gasket 115 may be formed of stainless steel, such as EN 10088-2 X10 CrNi 18-8+2H.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2117546.8 | Dec 2021 | GB | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2022/084292 | 12/2/2022 | WO |
