[0001] The invention relates to a drive arrangement for use in pump of the type suitable
for use in a common rail fuel injection system of an internal combustion engine. In
particular, the invention relates to a drive arrangement for a pump having at least
one pumping plunger that is driven by means of a drive member co-operating with a
cam rider mounted upon the engine cam shaft.
[0002] In a known common rail fuel pump of radial pump design, for example as described
in EP 1 184 568A, three pumping plungers are arranged at equi-angularly spaced locations
around an engine driven cam. Each plunger is mounted within a respective plunger bore
provided in a pump housing and, as the cam is driven, each of the plungers is caused
to reciprocate. As the plungers reciprocate, each causes pressurisation of fuel within
an associated pump chamber. The delivery of fuel from the pump chambers to a common
high pressure supply line is controlled by means of respective delivery valves associated
with each of the pumps. The high pressure line supplies fuel to a common rail, or
other accumulator volume, for delivery to the downstream injectors of the common rail
fuel system.
[0003] In one known fuel pump of the aforementioned type, each of the plungers is coupled
to a respective drive member in the form of a tappet. The cam carries a cam ring or
cam rider that travels over the surface of the cam as it is driven by the engine.
Each tappet is located within a tappet bore provided in a main pump housing and is
arranged so that, as the cam is driven, each tappet is caused to reciprocate within
its respective bore, resulting in reciprocating motion to the plungers.
[0004] As the rider rides over the cam surface to impart drive to the tappet in an axial
direction, a base surface of the tappet is caused to translate laterally over a co-operating
region of the rider surface. As the tappet is driven radially outward from the shaft,
its respective plunger is driven to reduce the volume of the pump chamber. This part
of the pumping cycle is referred to as the pumping stroke of the plunger, during which
fuel within the associated pumping chamber is pressurised to a relatively high level.
[0005] As the tappet is driven outwardly from the shaft and the tappet base slides over
the surface of the cam rider, a frictional force is generated between the two surfaces.
This gives rise to a local increase in the surface temperature of the tappet, resulting
in adhesive wear or "scuffing". This is undesirable and, in the worst case, can lead
to pump failure.
[0006] It is known to provide a lubrication means between the sliding surfaces of the tappet
base and the cam rider to reduce these disadvantageous effects. Typically, this is
achieved by providing a relatively thin fluid film between the two surfaces to generate
a transient fluid pressure between them which supports loading of the tappet and improves
lubrication. This solution, however, is unsatisfactory in meeting the high expectations
of evolving fuel pumps of the aforementioned type, particularly of the type intended
for use in common rail diesel fuel engines.
[0007] It is one object of the present invention to overcome or alleviate the aforementioned
problem.
[0008] According to the present invention, there is provided a drive arrangement for a pumping
plunger of a pump assembly, the drive arrangement comprising; a drive member that
is firstly co-operable with the pumping plunger and secondly co-operable with a cam
rider so as to impart axial drive to the plunger to perform a plunger pumping stroke
whilst permitting lateral sliding movement of the rider relative to the drive member,
wherein the drive member and the cam rider are co-operably shaped to define
(i) an increased volume for lubricating fluid which is variable throughout the pumping
cycle, and
(ii) restricted flow means through which fluid within said volume is dispelled at
a relatively low rate as the plunger is driven through the pumping stroke so as to
prolong transient fluid pressure within the volume through that period of the pumping
stroke for which return loading of the drive member is a maximum.
[0009] It will be understood from the following description that variable return loading
of the drive member arises due to the hydraulic load exerted on the drive member by
fuel within the pump chamber, the pressure of which increases and decreases throughout
a pumping cycle, and that the maximum return load applied to the drive member occurs
part way between BDC and TDC when fuel within the pump chamber is pressurised to its
maximum value, just prior to associated outlet or delivery valve means of the pump
chamber being opened to permit high pressure fuel delivery.
[0010] The invention provides the advantage that lubrication between the drive member and
the cam rider is improved during the plunger pumping stroke. The "squeeze film effect",
which is provided as fluid within the variable volume is dispelled through said restricted
flow means, is prolonged, to ensure a transient fluid pressure condition exists to
support return loading of the drive member during that part of the pumping cycle when
it is a maximum. Transient fluid pressure within the variable volume therefore supports
return loading of the drive member for a longer period of duration than is provided
by known drive arrangements of similar type.
[0011] Typically, the transient fluid pressure condition occurs part way between bottom-dead-centre
(BDC) and top-dead-centre (TDC) of the pumping stroke. This has the beneficial effect
that return loading of the drive member is supported during the most critical point
in the pumping cycle (i.e. when the return loading is a maximum) and friction between
the co-operating surfaces of the cam rider and the drive member is reduced. The effects
of wear due to scuffing are therefore limited.
[0012] The drive arrangement may be incorporated within a pump assembly of the type having
three plungers, wherein the plungers are radially spaced around a cam rider which
is common to all three plungers, this being a so-called radial fuel pump.
[0013] In one embodiment, at least one of the drive member and the rider is shaped to define
a recessed surface to define, together with a surface of the other of the drive member
and the rider, said variable fluid volume.
[0014] For example, the surface of the drive member may be shaped so as to be substantially
concave.
[0015] In this case the cam rider may include a substantially flattened surface which defines,
together with the concave surface of the drive member, the variable fluid volume.
[0016] Alternatively, or in addition, the cam rider may include a substantially concave
surface which defines, together with the surface of the drive member, the variable
fluid volume.
[0017] In one embodiment the drive member may be shaped to include a drive member side wall
of annular form defining an annular surface that is co-operable with the surface of
the rider to define the restricted flow means. For example, the drive member may be
provided with a recessed surface of substantially U-shaped cross section.
[0018] In any of the embodiments of the invention, the drive member may be shaped to define
a radiussed surface to define the restricted flow means with the surface of the rider.
This provides the benefit that lubricating fluid is encouraged to flow into the variable
fluid volume during the return stroke of the drive member, and also in some configurations
provides the benefit that the surface contact area between the drive member and the
cam rider is increased, thereby reducing contact stresses.
[0019] According to a second aspect of the present invention, a drive arrangement for a
pumping plunger of a pump assembly comprises;
a drive member that, in use, is firstly co-operable with the pumping plunger and secondly
co-operable with a cam rider so as to impart drive to the plunger to perform a plunger
pumping stroke during which fuel within a pump chamber is pressurised to a high level,
whereby, in use, the rider moves laterally relative to the drive member, and wherein
respective surfaces of the drive member and the cam rider are co-operably shaped to
define a variable volume for lubricating fluid throughout the pumping cycle, and to
provide a transient pressure condition between said surfaces during a stage of the
pumping stroke for which relative velocity between lateral movement of the drive member
and the rider is substantially zero.
[0020] According to a third aspect of the present invention, there is provided a pump assembly
including;
a plunger, and
a drive arrangement for the plunger as claimed in the accompanying claim set.
[0021] The preferred and/or optional features of the first aspect of the invention may therefore
be provided, alone or in appropriate combination, in either the second or the third
aspect of the invention also.
[0022] In a particularly preferred embodiment of each of the first, second and third aspects
of the invention, the drive member takes the form of a tappet, for example a bucket
tappet of substantially U-shaped cross-section.
[0023] The present invention will now be described, by way of example only, with reference
to the accompanying drawings in which:
Figure 1 is a sectional view of a pump assembly of the type in which the drive arrangement
of the present invention may be employed,
Figure 2 is an exaggerated view of a tappet and cam rider surface forming part of
a first embodiment of the drive arrangement of the present invention,
Figure 3 is a diagram to show the relative velocity between the tappet and the cam
rider surface throughout a 360° pumping cycle,
Figure 4 is a diagram to show the displacement of the tappet, with time, throughout
the pumping cycle, with the position of the tappet relative to the cam rider surface
also indicated,
Figures 5(a) to (c) show views of the tappet during first, second and third stages
of a pumping stroke of the pumping cycle,
Figures 6, 7 and 8 are exaggerated views, similar to Figure 2, of alternative tappet
and cam rider surface configurations for use in the pump assembly of Figure 1.
[0024] The present invention relates to drive arrangement for a pump assembly, generally
of the type shown in Figure 1. The pump assembly 10 includes a first housing part
12 in the form of a main pump housing provided with an axially extending opening through
which a cam drive shaft extends when the assembly 10 is installed within the engine.
In the section shown in Figure 1, the central axis 16 of the drive shaft is identified,
although the drive shaft itself is not visible. The drive shaft co-operates with a
drive arrangement which includes an eccentrically mounted cam 18 carrying cam ring
or rider 20 having a generally circular-like cross section.
[0025] Mounted around the cam 18 are first, second and third pump heads or units, generally
referred to as 22a, 22b, 22c. Each pump unit is identical and so only one will be
described in detail.
[0026] The first pump head 22a includes a plunger 24 which is reciprocal within a plunger
bore 26 to cause pressurisation of fuel within a pump chamber 28 defined at a blind
end of the bore 26. Fuel at relatively low pressure is supplied to the pump chamber
28, in use, and is pressurised to a high level suitable for injection as the plunger
24 is driven to perform a pumping stroke, that is between bottom-dead-centre (BDC)
and top-dead-centre (TDC).
[0027] Figure 2 shows a first embodiment of a drive arrangement for the pump assembly in
Figure 1. The plunger has an associated a drive member 30 in the form of a tappet
is co-operable with the plunger 24. The tappet 30 may be a bucket tappet, of generally
U-shaped or channelled cross section, and includes a base 32 and first and second
side walls 34. The upper surface of the tappet base 32 may be provided with recess
(not shown) for locating one end of a plunger return spring (item 36 - Figure 1),
mounted concentrically with the plunger 24, which serves to drive a plunger return
stroke between TDC and BDC. A circlip (not shown) couples the return spring 36 to
the plunger 24 at its lower end. Although the tappet 30 and the plunger 24 are not
physically coupled to one another, so that relative axial movement is permitted between
these parts 24, 30, the spring 36 tends to maintain tappet and plunger contact during
movement.
[0028] Examples of how the tappet and the plunger may be coupled together, if required,
are described in our co-pending UK patent application GB 0229367.8.
[0029] A lower surface 37 of the tappet base 32 is co-operable with a flattened surface
region 38, or flat, of the rider 20. The generally circular cam rider 20 is provided
with three flattened surface regions 38 in total, equi-angularly spaced around the
rider 20 so that each is co-operable with a respective one of the three tappets. The
rider 20 may therefore be considered to be of generally prismatic-type form. The lower
surface 37 of the tappet base 32 defines a surface edge 37a and the flattened surface
38 of the rider 20 defines a surface edge 38a. The surface edge 37a of the tappet
is of annular form and, effectively, defines a 'surface line'.
[0030] In known fuel pumps of the type including a tappet driving a plunger, the facing
co-operable surfaces of the tappet and the rider are flat and aligned in parallel
to define a very small clearance between them which supports a thin film of lubricating
fluid. As the tappet is driven through the pumping cycle, the thin fluid film between
these two surfaces serves to reduce friction between the sliding surfaces, and as
fluid it dispelled between the surfaces transient fluid pressure supports return loading
of the tappet. This so-called "squeeze film" effect is well known, and mechanisms
relying on this are known to exhibit reduced friction. It has been found, however,
that this squeeze film effect does not reduce friction between the tappet and the
rider to a sufficient extent, so that an unsatisfactory level of tappet wear occurs.
[0031] It is a particular feature of the present invention that the surface 37 of the tappet
base 32 and the facing flattened surface 38 of the cam rider 20 are co-operably shaped
to provide an increased volume between them for lubricating fluid. In Figure 2, for
example, the lower surface of the tappet base 32 is provided with a recess to define
a substantially concave surface 37, rather than being flat as is known in conventional
tappet drive arrangements. This relatively large fluid volume 44 is variable throughout
the pumping cycle and provides a prolonged transient fluid pressure condition which
serves to reduce friction between the surfaces 37, 38 as they translate or slide relative
to one another, in use. The reason for this is described in further detail below.
It should be noted that the extent to which the surface 37 of the tappet base 32 is
concave is exaggerated greatly in Figure 2.
[0032] In use, as the cam rider 20 is caused to ride over the surface of the cam 18 upon
rotation of the drive shaft, an axial drive force is imparted to the tappet 30, and
in turn to the plunger 24, causing the plunger 24 to reciprocate within its bore 26.
The tappet 30 and the plunger 24 are thus driven together to perform a pumping cycle
including a pumping stroke and a return stroke. During the pumping stroke the tappet
30 and the plunger 24 are driven radially outward from the shaft (i.e. vertically
upwards in Figure 1) to reduce the volume of the pump chamber 28. During the plunger
return stroke, effected by means of the return spring 36, the tappet 30 and the plunger
24 are urged in a radially inward direction (i.e. vertically downwards in Figure 1)
to increase the volume of the pump chamber 28. As the tappet 30 is driven in a radially
outward direction, to impart drive to the plunger 24 in an axial direction, a degree
of lateral or sliding movement of the tappet 30 across the flattened rider surface
38 occurs, in a back and forth manner. The tappet slides across the flattened rider
surface 38 in a similar manner during the return stroke.
[0033] The pump assembly is provided with an appropriate inlet metering valve (not shown)
with appropriate inlet and outlet valves (also not shown) being provided for each
of the three pump chambers. Pressurisation of fuel within the pump chamber 28 occurs
during the pumping stroke of the plunger 24, during a period for which both the inlet
and outlet valves are closed. When fuel is pressurised to a level that is sufficient
to open the outlet valve, pressurised fuel is supplied through a delivery passage
to the common rail. Typically, the pressure of fuel supplied through the outlet valve
is in the range of between 1500 and 2000 bar. During the return stroke of the plunger
24, fuel pressure downstream of the pump chamber 28 is higher than that within the
pump chamber 28 and the outlet valve is urged closed. During the period of the return
stroke for which the inlet valve is urged open, fuel at relatively low pressure is
supplied to the pump chamber 28 to fill the chamber 28 ready for commencement of the
following pumping stroke.
[0034] As the tappet 30 and the plunger 24 are driven through the pumping cycle, the surface
37 of the rider 20 moves laterally, back and forth, relative to the surface 37 of
the tappet 30. The relative velocity between the sliding surfaces 37, 38 varies through
the pumping cycle, as shown in Figure 3 (it should be appreciated particularly that
the vertical axis in Figure 3 represents relative velocity and not tappet displacement).
As the surfaces 37, 38 are displaced laterally, relative to one another, the volume
44 defined between them fills with, and dispels, lubricating fluid, in a cyclic manner,
as described below with reference to Figures 4 and 5.
[0035] For the purpose of the following description it should be noted in particular that,
in practice, the tappet 30 is constrained laterally and so it is the rider 20 which
moves relative to the tappet 30 to provide relative movement between their respective
surfaces 37, 38. However, to aid the clarity of the following description Figure 4
shows relative displacement between the tappet 30 and the rider 20, with the tappet
30 being illustrated, relative to the moving rider 20, at different relative tappet
positions.
[0036] Figure 5(a) shows the tappet 30 and the plunger 24 at the start of the pumping stroke,
at or just after BDC (a first stage of the pumping stroke), when the relative velocity
between the sliding surfaces 37, 38 is, approximately, at its maximum value. In Figure
4, this point in the pumping cycle is identified at 50 and at this point fuel pressure
in the pump chamber 28 is relatively low so that only a relatively low return load
is exerted on the plunger 24 and the tappet 30 due to fuel pressure in the chamber
28. The volume 44 of lubricating fluid between the surfaces 37, 38 is large at this
stage due to the concavity of the tappet base 32, which volume 44 includes a small
clearance defined between the surfaces 37, 38 in the region of the tappet edge 37a
at the surface line. It is this large volume 44 of fluid between the surfaces 37,
38 which supports the hydraulic return loading of the tappet 30 due to fuel pressure
in the pump chamber 28.
[0037] Figure 5(b) illustrates the tappet 30 and the plunger 24 at a point further through
the pumping stroke, a part of the way between BDC and TDC, at which the relative velocity
between the flattened rider surface 38 and the tappet surface 37 has decreased, progressively,
to a minimum (a second stage of the pumping stroke). The return load on the plunger
24 and tappet 30 is increasing at this stage, as fuel pressure in the pump chamber
28 is increasing. The tappet base 32 has a degree of compliance so that, as the return
load increases the base 32 is caused to be depressed slightly, thereby reducing the
volume 44 between the surfaces 37, 38. As the volume 44 is reduced, lubricating fluid
is dispelled from the volume 44 at a relatively low rate, as determined by the size
of the gap or clearance between the tappet edge 37a at the surface line and the flattened
surface 38. The dispelling of fluid from the volume 44 provides a squeeze film effect,
which serves to reduce friction between the surfaces 37, 38.
[0038] Partly due to the large volume of lubricating fluid between the surfaces 37, 38 which
is dispelled from the volume 44, and partly due to the restricted clearance between
the surfaces at the tappet edges 37a, transient fluid pressure between the surfaces
37, 38 is prolonged such that, at the point at which the return load on the plunger
24 and tappet 30 is at a maximum and friction between the surfaces 37, 38 is most
significant, transient fluid pressure between the surfaces 37, 38 is sufficient to
support return loading of the tappet 30. This critical point in the pumping cycle
occurs just prior to the outlet valve opening to deliver pressurised fuel within the
pump chamber 38 to the rail, as it is at this point that fuel pressure in the chamber
28 is at a maximum.
[0039] Continuing through the pumping stroke, the volume 44 defined between the tappet and
rider surfaces 37, 38 is reduced further still, with fluid continuing to be dispelled
between the surfaces 37, 38, through the restricted clearance at a low rate until.
This is the second stage of the pumping stroke, as shown in Figure 5(c).
[0040] Eventually at TDC (point 52 in Figure 4), the surfaces 37, 38 are, effectively, in
contact so that substantially all fluid has been dispelled from the now collapsed
volume, hence no fluid exists between them. This is the third stage of the pumping
stroke, as shown in Figure 5(c)).
[0041] Between the second and third stages of the pumping stroke, progressive edge surface
contact between the surfaces 37, 38 eventually increases until the surfaces contact.
It will therefore be appreciated that it is only for part of the pumping stroke that
fluid is dispelled from the reducing volume 44. Compared to known arrangements making
use of the squeeze film effect, however, the period for which transient fluid pressure
supports return loading of the tappet is significantly prolonged.
It will be appreciated especially from Figure 4 that, for all stages of the pumping
stroke, as the surfaces 37, 38 move laterally relative to one another, back and forth,
the surfaces 37, 38 are nonetheless substantially aligned. The rate at which fluid
is dispelled from the volume 44, between the surfaces at the tappet edge 37a, is therefore
maintained relatively low. It is an important feature of the invention that the flow
area through which fuel is dispelled from the volume 44 is small so as to sustain
transient fluid pressure within the volume 44 for a significant period of time, and
particularly during that part of the pumping stroke when loading of the tappet is
at a maximum (part way between BDC and TDC). This is achieved by shaping the tappet
base 32 and the cam rider 20 to provide a restricted flow means between the tappet
surface edge 37a and the flattened surface 38 of the rider 20. Any increased areas
available for fluid flow from the volume 44 will serve to reduce the time for which
transient fluid pressure supports return loading of the tappet 30, which is undesirable.
In this embodiment, for example, it is therefore important that the surface 37 of
the tappet is made accurately concave to sustain the restricted fluid flow between
the surfaces 37, 38 from the volume 44 at all stages of the pumping stroke.
[0042] After the tappet has reached TDC and subsequently starts its return stroke, a cavity
is drawn between the two edge-contacting surfaces 37, 38 as the plunger 24 is withdrawn
from the pump chamber 28 and, thus, the volume 44 between the surfaces 37, 38 starts
to increase. Eventually, when loading of the retracting plunger is reduced sufficiently,
the seal between the surfaces 37, 38 is broken until, part way through the return
stroke, filling of the volume 44 commences at the point in the stroke when the tappet
30 is displaced relative to the rider surface, in a positive direction, by a sufficient
amount for the edge 37a of the tappet surface 37 to extend beyond the edge 38a of
the flattened surface 38 of the rider 20. The period for which the volume 44 is expanding
and filling is identified by the shaded region 46 in Figure 4 (two shaded regions
46 are identified for subsequent pumping cycles). During the initial stage of the
return stroke, lubricating fluid is drawn into the volume 44 through the clearance
gap between the edges 37a, 38a of the surfaces 37, 38. Part way through the return
stroke the direction of motion of the tappet 30 reverses and, subsequently, filling
of the volume 44 stops at the point in the cycle, just prior to BDC, when the edge
37a of the tappet surface 37 is again re-aligned with the edge 38a of the flattened
rider surface 38 to close the clearance gap.
[0043] As described previously, during the following pumping stroke the tappet and the rider
surfaces 37, 38 remain aligned, and transient fluid pressure within the volume supports
the return loading of the tappet for a prolonged period due to the relatively large
volume 44 of fluid between the surfaces 37, 38 at the tappet edge 37a being dispelled
at a very low rate.
[0044] Figure 6 shows an alternative embodiment to that shown in Figures 2 and 5, in which
the surface 137 of the tappet base 32 is not made concave but instead is provided
with a recess, of generally U-shaped cross section, to define an annular outer wall
48. A lower annular surface 137a of the outer wall 48 is substantially flat and defines,
together with the surface 38 of the cam rider 20, a restricted flow means for permitting
fluid within the volume 44 to be dispelled at a relatively low rate as the tappet
30 performs the pumping stroke. It is one advantage of this embodiment that the contact
area between the two surfaces 137a, 38 is increased during the final stages of the
pumping stroke, and this has the effect of reducing surface contact stress.
[0045] Operation of this embodiment is similar to that described previously with reference
to Figures 2 to 5, with the exception that the restricted flow means is defined between
an annular surface 137a of the outer wall 48, rather than being defined by a surface
edge such as 37a in Figures 2 to 5. As before, during the initial stages of the pumping
stroke the volume 44 is gradually reduced as the load on the tappet 30 increases and
the base 32 of the tappet 30 is depressed slightly to dispel fluid from the volume
44. During the final stage of the pumping stroke, just prior to TDC, the compliance
of the tappet base 32 causes its lower recessed surface 137 to substantially flatten,
with surface contact between the annular surface 137a of the tappet outer wall 48
and the rider surface 38 eventually providing a seal.
[0046] It is a further feature of the embodiment of Figure 6 that the tappet base 32 cannot
distort as much as for the first embodiment due to the shaping of the recessed surface
137, so that the volume 44 between the surfaces 137, 38 does not collapse totally
at the third stage of the pumping stroke.
[0047] In a further alternative embodiment, as shown in Figure 7, the surface 37 of the
tappet base 32 and the surface 138 of the cam rider 20 are both shaped to be concave
so as to further increase the volume 44 available for lubricating fluid. In this case
it is important that both surfaces 37, 138 are shaped with a high degree of accuracy
so as to ensure a sufficiently restricted flow area for fluid is maintained at all
times through the pumping stroke in the region of their surface contact.
[0048] Once again, it should be noted that the extent to which the surface 137 of the tappet
30 is shown to be recessed in Figure 6, and the extent to which the surfaces 37, 138
of the tappet 30 and the rider 20 are shown to be concave in Figure 7, is greatly
exaggerated.
[0049] Figure 8 shows a further alternative embodiment in which the tappet 30 is shaped
in a similar manner to that shown in Figures 2 to 5, with the tappet base 32 being
provided with a substantially recessed lower surface 237, but with its edge surface
237a being radiussed or 'rolled'. Radiussing of the edge surface 237a provides a first
advantage that, during the return stroke of the plunger and tappet when the volume
44 is being filled with lubricating fluid through the clearance gap between the edges
237a, 38a, the radiussed outermost edge encourages fluid to be drawn between the surfaces
237a, 38 into the volume 44. A second advantage is obtained in that the contact area
between the two surfaces 237a, 38 is increased during the final stages of the pumping
stroke, thereby reducing surface contact stress.
[0050] In other variations the tappet and rider arrangements having the general constructions
shown in Figures 6 and 8 may also be configured such that the surface edge of the
tappet, which co-operates with the surface of the rider 20 to define the restricted
flow means, is radiussed or rolled.
[0051] In any of the aforementioned embodiments, it may be further desirable to provide
the recessed surface 37, 137, 237 of the tappet 30 with a plurality of small indentations
or pockets to further enhance the available volume 44 for lubricating fluid. This
may be achieved, for example, by forming laser pockets over the recessed tappet surface
37, 137, 237, or by rough grinding the recessed surface followed by super finishing.
[0052] In a three-plunger radial pump it will be appreciated that each of the three flattened
surfaces of the rider 20, and the respective co-operable surfaces of the three tappets,
may be shaped in the same manner as described for any of the aforementioned embodiments,
or in an otherwise co-operably shaped manner to provide the functional benefit of
the drive arrangement set out in the accompanying claims.
[0053] It will be appreciated that the drive arrangement of the present invention may or
may not be manufactured to include the cam 18 and/or the plunger 24. It will also
be appreciated that drive arrangement of the present invention may be employed in
other types of pump assembly, not necessarily radial pump assemblies and not necessarily
pump assemblies of the type having three plungers.
1. A drive arrangement for a pumping plunger (24) of a pump assembly, the drive arrangement
comprising;
a drive member (30) that is firstly co-operable with the pumping plunger (24) and
secondly co-operable with a cam rider (20) so as to impart axial drive to the plunger
(24) to perform a plunger pumping stroke whilst permitting lateral sliding movement
of the rider (20) relative to the drive member (30),
wherein the drive member (30) and the cam rider (20) are co-operably shaped to define
(i) an increased volume (44) for lubricating fluid which is variable throughout the
pumping cycle and (ii) restricted flow means through which fluid within said volume
(44) is dispelled at a relatively low rate as the plunger (24) is driven throughout
the pumping stroke so as to prolong transient fluid pressure within the volume (44)
through that period of the pumping stroke for which return loading of the drive member
(30) is a maximum.
2. The drive arrangement as claimed in claim 1, wherein at least one of the drive member
(30) and the rider (20) is shaped to define a recessed surface (37, 38; 137, 38; 37,
138; 237, 38) which defines, together with a surface of the other of the drive member
(30) and the rider (20), said variable fluid volume (44).
3. The drive arrangement as claimed in claim 2, wherein the recessed surface (37) of
the drive member (30) is substantially concave.
4. The drive arrangement as claimed in claim 2 or claim 3, wherein the cam rider (20)
includes a substantially flattened surface (38) which defines, together with the concave
surface (37) of the drive member (30), the variable fluid volume (44).
5. The drive arrangement as claimed in claim 2 or claim 3, wherein the cam rider (20)
includes a substantially concave surface (138) which defines, together with the surface
(37) of the drive member (30), the variable fluid volume (44).
6. The drive arrangement as claimed in any one of claims 3 to 5, wherein the restricted
flow means is defined by a surface edge (37a) of the recessed surface (37) of the
drive member (30) and the surface (38) of the rider (20).
7. The drive arrangement as claimed in claim 2, wherein the drive member (30) is provided
with a substantially U-shaped recess to define the recessed surface (137).
8. The drive arrangement as claimed in claim 7, wherein the drive member (30) is shaped
to define a drive member side wall (48) of annular form defining an annular surface
(137a) that is co-operable with the surface of the rider (20) to define the restricted
flow means.
9. The drive arrangement as claimed in any one of claims 6 to 8, wherein the restricted
flow means is defined by a radiussed surface (237a) of the drive member (30) and the
surface (38) of the rider (20).
10. The drive arrangement as claimed in any one of claims 1 to 9, wherein the drive member
is a tappet (30).
11. A drive arrangement for a pumping plunger (24) of a pump assembly, the drive arrangement
comprising;
a drive member (30) that, in use, is firstly co-operable with the pumping plunger
(24) and secondly co-operable with a cam rider (20) so as to impart drive to the plunger
(24) to perform a plunger pumping stroke,
whereby, in use, the rider (20) moves laterally relative to the drive member (30),
and wherein respective surfaces (37, 38; 137, 38; 37, 138; 237, 38) of the drive member
(30) and the cam rider (20) are co-operably shaped to define a variable volume (44)
for lubricating fluid throughout the pumping cycle, and to provide a transient pressure
condition between said surfaces during a stage of the pumping stroke for which relative
velocity between lateral movement of the drive member (30) and the rider (20) is substantially
zero.