"Fuel Evaporators"
This invention relates to evaporators for evaporation of fuel into an air flow,
and is concerned more particularly, but not exclusively, with carburettor metering
systems for small gasoline engines.
Small gasoline engines are typically single cylinder four-stroke engines of low
cost, and are used in applications such as lawnmowers and outboard motors. Such
single cylinder engines draw in air/fuel mixture intermittently, and this causes a
problem in relation to fuel metering which is not encountered to the same extent in
multi-cylinder engines as are typically used in the automotive field. Furthermore
such single cylinder engines, unlike automotive engines, operate either at a governor
controlled speed or with a fixed relationship between speed and load, and in addition
usually have fixed ignition timing. Existing carburettor metering systems for such
small engines have a tendency to produce inhomogeneous air/ fuel mixtures containing
unevaporated fuel droplets which tend to increase the quantity of hydrocarbons in the
exhaust emissions. It is desirable for carburettor metering systems to produce highly
homogenous air/fuel mixtures as this not only tends to decrease the hydrocarbons in
the exhaust emissions, but also allows engine operation with a leaner air/fuel mixture
at part load, thus reducing emissions of oxides of nitrogen and of carbon monoxide.
Generally carburettor metering systems produce a pressure difference related
to air flow, and use this pressure difference to propel fuel from a constant pressure
fuel reservoir into the air flow, usually as a more or less atomised spray. In order to
produce an air/fuel mixture of highly uniform consistency, with the above mentioned
benefits in terms of exhaust emissions, it is known to supply the fuel to a fabric wick
through which the warmed air is passed to produce a substantially dry fuel vapour.
International Published Application No. WO 94/16211 discloses an evaporator
consisting of a stack of plates which are spaced apart so as to define narrow air
passages therebetween and so as to provide porous evaporation surfaces for fuel along
the sides of the passages, the evaporation surfaces being formed from sintered metal
or from fabric. The bottoms of the plates are immersed in liquid fuel so that the fuel
is caused to diffuse over the evaporation surfaces by capillary action, and the air flow
along the passages causes fuel to be evaporated from the evaporation surfaces into the
air flow to produce a homogeneous air/fuel mixture. However such an evaporator
suffers from a number of disadvantages in practice when produced at a sufficiently
low cost to render it feasible in a small engine application. One of the main
disadvantages is that, under high transients, it is possible for droplets of fuel to break
away from the evaporation surfaces into the air flow, thus causing inhomogeneity of
the resulting air/fuel mixture and a consequent increase in hydrocarbons in the
exhaust emissions.
It is an object of the invention to provide a novel fuel evaporator which can
be produced at low cost and which provides uniform consistency of the air/fuel
mixture for different engine loads.
The invention is defined in the accompanying claims.
In order that the invention may be more fully understood, several
embodiments of the invention will now be described, by way of example, with
reference to the accompanying drawings, in which:
Figure 1 shows a fuel evaporator in accordance with the invention;
Figures 2, 3 and 4 are diagrams illustrating the supply of fuel to the
evaporation surfaces of the evaporator;
Figures 5, 6, and 7 show different spacer arrangements for the evaporator;
Figures 8, 9, 10 and 11 show a carburettor metering system in accordance
with the invention incoφorating a fuel valve and an air control valve;
Figure 12 is a graph illustrating the operation of the fuel valve;
Figure 13 is a diagram of an alternative carburettor metering system in
accordance with the invention, in vertical section;
Figure 14 is a section taken along the line A-A in Figure 13;
Figures 15 and 16 are diagrammatic sections through details of an alternative
evaporator which may be used in the system of Figure 13,
Figure 16 shows a section taken along the line C-C in Figure 15;
Figure 17 is a diagrammatic section through a further altemative evaporator
which may be used in the system of Figure 13;
Figure 18 is a graph of air flow and fuel flow against pressure difference in
use of an evaporator according to the invention; and
Figures 19 and 20 show a modification of the carburettor metering system of
Figures 8 to 11.
The evaporators to be described below are intended to produce a highly
homogenous mixture of gasoline vapour in air for supplying to a small gasoline
engine, typically a single cylinder 4-stroke engine of low cost, and will be described
when used in a carburettor system for supplying such an engine However similar
evaporators may also be used to supply larger engines, such as multi-cylinder
automotive engines, and it is also possible to utilise such evaporators for supplying
an air/fuel mixture to other types of combustion apparatus, such as furnaces.
The illustrated carburettor metering system is provided for supplying an
air/fuel mixture to a single cylinder lawnmower engine and is dimensioned to fit
within the space available in such an application. In such governor controlled engines
the mixture quantity varies in a known way with load and can thus be used to control
the mixture strength so as to minimise exhaust emissions. Current legislation in
California specifies emissions of carbon monoxide, and of combined hydrocarbons
and oxides of nitrogen. For lean engine operation with air/fuel ratios greater than
about 17: 1 the nitrogen oxide emissions fall as the mixture is made leaner, while, at
very lean mixtures, hydrocarbon emissions start to rise. Carbon monoxide emissions
are low and practically constant for ratios greater than about 16: 1. Thus the total
emissions are low over a reasonable range of mixture strengths, and this allows some
tolerance in optimising the mixture strength for low emissions. The legislation
specifies limits based on tests at idle, quarter load, half load, three quarter load and
full load, and a typical engine might require air/fuel ratios of 17: 1, 18: 1, 19: 1 and
12: 1 respectively at these load conditions.
Figure 1 shows an evaporator 50 consisting of a flow duct 51 of generally
rectangular cross-section within which a stack of flat brass plates 52 having non¬
porous, non-reticulated surfaces is accommodated. The plates 52 are spaced apart by
brass spacers 53 disposed between each pair of adjacent plates 52 so as to define
narrow passages for flow of air therebetween, the figure being broken away to show
four such spacers 53 which would normally be disposed between two of the plates 52.
Each of the spacers 53 is provided with two through holes 54 extending through
recessed parts of the spacer 52 which have recesses 55 in their front and rear faces,
the through holes 54 being aligned with corresponding holes (not shown) in the plates
52 so that four pairs of passages extend through the complete stack of plates 52. If
required wires may be threaded through the passages in order to accurately align the
plates 52 with one another, although the primary function of the passages is to permit
supply of fuel along the passages so that fuel is emitted from the recesses 55 onto the
evaporation surfaces transversely of each of the spacers 53 in both directions and thus
transversely of the air flow supplied to the inlet of the flow duct 51 in the direction
of the arrow 57.
Such fuel supply to the evaporation surface of a plate 52 from a supply recess
55, as shown diagrammatically Figure 2, results in the fuel spreading laterally by a
combination of the momentum of the fuel passing through the recess 55 and surface
wetting, so that a fuel film 56 is produced having a thickness which reduces
downstream of the supply point. Furthermore the air flow in the direction of the
arrow 57 results in variation of the local air flow velocity V in the manner shown
graphically in broken lines by the velocity distribution curve 58, resulting in a
velocity gradient in the air flow downstream of the fuel supply point producing a
shear stress in the fuel film 56 which assists downstream spreading of the fuel. In
practice the effect of gravity on fuel spreading is small compared with the air flow
shear stress. The object of the fuel supply system is to supply fuel to the evaporation
surfaces close to the point of air entry and at a substantially uniform rate. To this end
each supply point should offer a small consistent restriction to flow of fuel
therethrough.
Figure 3 shows the supply of fuel to the evaporation surface at one side of a
spacer 53 by way of the recess 55, it being understood that a corresponding supply
of fuel to the evaporation surface will also be provided from the recess 55 at the other
side of the spacer 53 (and similar fuel supply will be provided at the opposite face of
the spacer 53 to the evaporation surface on the opposite side of the passage).
Figure 4 shows corresponding supply of fuel to an evaporation surface in a
modified arrangement in which spacers 59 are provided which are similar to the
spacers 53 but which do not include recesses 55. Instead each of the plates 52 is
provided with slots 60 extending outwardly from the holes through the plates 52 to
positions beyond the sides of the spacers 59 so that fuel supply to the evaporation
surfaces takes place from the ends of the slots 60 extending through the plates 52
themselves (rather than through recesses in the spacers).
Figure 5 is a section in the vicinity of one wall 62 of the flow duct 51 showing
a milled fuel manifold 63 having an inlet 64 for the supply of fuel thereto from a fuel
reservoir (not shown). From the fuel manifold 63 fuel is supplied along the passage
65 extending through the stack of plates 52 to permit fuel supply to the evaporation
surfaces of the individual plates 52 in the manner already described. As shown in
Figure 5 the spacers 53' are in the form of washers provided with grooves (not
shown) in both faces for fuel supply to the evaporation surfaces, this representing a
modification of the spacer arrangement shown in Figure 1. The plates 52 are held
in register by a guide wire 66 extending through the passage 65 with clearance.
A further possible spacer arrangement is shown in Figures 6 and 7 in which
each pair of adjacent plates 52 is separated by a single unitary spacer member 70.
Each spacer member 70 has parts 71 provided with through holes 72 and front and
rear recesses 73 in a generally similar manner to the spacers 53 of Figure 1 , the parts
71 being interconnected by integral web parts 74 of reduced thickness so as to provide
the required throughflow cross-section for the input of air as shown by the arrows 75
and for the output of the air/fuel mixture as shown by the arrows 76. Locating nibs
77 may be provided on the spacer members 70, as shown in Figure 7, in order to
correctly locate the plates 52 relative to the spacer members 70 so that the holes 72
in the spacer parts 71 are aligned with the holes 78 in the plates 52. Fuel supply to
the evaporation surfaces through the recesses 73 occurs in the manner previously
described. Numerous other spacer arrangements are possible within the scope of the
invention, and in particular spacers may be constituted by integral portions of the
plates.
Figures 8 and 9 show a carburettor metering system 1 comprising a housing
2 having two parts 3 and 4. Figure 8 shows a vertical section through the housing
part 3 which incorporates an air control valve 5, a fuel valve 6, an air cleaner 7 and
a float bowl 8. The air control valve 5 comprises an air valve gate 9 in the form of
an arm 10 pivotally connected at one end to the housing part 3 by a pivot hinge or
flexure 11, and an air valve seat 12 in the form of a sill located at some distance from
the pivot hinge or flexure 11. The arm 10 extends substantially across the whole of
the top of the housing part 3, but is provided with sufficient clearance at its edges to
permit it to pivot within the housing part 3 and to permit passage of air into or out
of the space of the above arm 10 during movement of the gate 9. The restricted
passage for air flow between the space above the arm 10 and the space downstream
of the air control valve 5 restricts the rate of movement of the gate 9 and thus
provides damping so as to prevent oscillation and permit extra fuel supply for
acceleration. Furthermore the gate 9 includes a gate member 14 having the shape of
an arc centered about the pivot point and depending downwardly from the arm 10.
The gate member 14 has a cut-out 15, as may be seen in the detail of the gate
member 14 shown in Figure 10, having a profiled edge 13 which defines with the
straight edge of the sill 12 an air flow orifice 16. It will be appreciated that, as the
gate 9 is pivoted by air pressure acting against gravity and/or an optional spring 17,
as shown in broken lines in Figure 8, the gate member 14 is moved upwardly or
downwardly in the direction of the arrow 18 in Figure 10 relative to the seat 12 in
order to vary the throughflow cross-section of the orifice 16.
A small governor-controlled engine typically has an air flow range of 3 or 4
to 1, and such an air valve gate may be satisfactorily utilised to provide the required
metering to produce a substantially constant air/fuel mixture or more likely an air/fuel
mixture having a ratio which varies with load in order to minimise emissions. In a
governor-controlled engine the air flow rate varies with load, and in such a case the
shape of the profiled edge 13 defining the air flow orifice can be modified to provide
any required variation of air/fuel mixture strength against air flow. The gate profile
can also be modified to accommodate the use of the optional spring 17 so that the
pressure difference across the gate varies with flow.
The fuel valve 6 comprises a fuel valve body 20 incoφorating an axial bore
21 having a constant circular cross-section along its length and a fuel outlet 22 at its
lower end, as well as a transverse passage 23 intersecting the bore 21 and providing
a fuel inlet. The fuel valve 6 also incoφorates a fuel valve member 25 having a
constant circular cross-section along its length substantially matching the cross-section
of the bore 21 into which the valve member 25 extends, but having a slightly smaller
diameter to enable the valve member 25 to move freely up and down within the bore
21. The valve member 25 has an integral extension member 26 having a head 27
which engages the lower surface of the pivotal arm 10 of the air valve gate 9 such
that pivotal movement of the gate 9 causes corresponding movement of the valve
member 25 within the bore 21 so as to vary the length of an annular passage 28
provided between the outside wall of the valve member 25 and the inside wall of the
bore 21 for fuel flowing from the transverse passage 23 along the bore 21 to the fuel
outlet 22. The head 26 of the extension member 27 is maintained in contact with the
air valve gate 9 by a compression spring 26A.
Fuel is supplied to the transverse passage 23 from the float bowl 8 by way of
a fuel supply passage 29, and the passage of fuel along the bore 21 to the fuel outlet
22 is restricted by the presence of the cylindrical valve member 25 by an amount
which depends on the length by which the lower end of the valve member 25 extends
below the transverse bore 23, which may be referred to as the length of overlap.
Since the air pressure at the free surface of the fuel within the float bowl 8 is equal
to the air pressure upstream of the air control valve 5 and since the air pressure at the
location to which the fuel is supplied downstream of the fuel valve 6 is equal to the
air pressure downstream of the air control valve 5, the pressure difference driving the
fuel through the fuel valve 6 corresponds to the pressure difference across the air
control valve 5 required to lift the air valve gate 9 against gravity and/or the spring
17.
The pressure difference across the air control valve 5 will be approximately
proportional to the square of the ratio of the air mass flow to the area of the orifice
16 for air flow through the valve, whereas the fuel flow through the fuel valve 6 will
be proportional to the pressure difference across the valve divided by the length of
overlap (since other geometric factors will remain constant as the length of overlap
varies). If the pressure difference across the fuel valve 6 is constant (that is affected
only by gravity and not by spring pressure), the length of overlap multiplied by the
area of the throughflow orifice through the air control valve 5 will need to be constant
if the air/fuel ratio is to remain constant. Such constancy requires that the width of
the cut-out 15 of the air control valve 5 at the level of the sill formed by the air valve
seat 12 should be proportional to the square of the reciprocal of the length of overlap.
Such a relationship is shown graphically in Figure 12 which plots the width of the
cut-out 15 at the level of the sill against the length of overlap.
The air which passes through the air control valve 5 then passes into the
housing part 4 by way of an air outlet 30 as shown in Figure 9, and from there passes
through an evaporator 31 consisting of a series of parallel plates 32 spaced apart so
as to define narrow passages 33 therebetween and providing evaporation surfaces 34
along the sides of the passages 33. Figure 11 is an exploded view of one of the plates
32 showing that each plate 32 is in fact made up of three parts bonded together (or
possibly formed integrally), namely a manifold portion 33 sandwiched between two
perforated outer portions 34 and 35. The manifold portion 33 has a T-shaped
aperture extending therethrough constituting a manifold chamber 36, and each of the
perforated outer portions 34 and 35 has a number of fine pores 37 extending
therethrough and communicating with the manifold chamber 36. Each of the pores
37 is formed by a laser in the portions 34 and 35, which are preferably metal sheets
or foils, and has a diameter of 20-40 microns, and the pores 37 are spaced about 2
mm apart, about 10 pores being spaced along a line in each portion. Furthermore
each perforated portion 34 or 35 is provided with an aperture 38 extending
therethrough and communicating with the upright portion of the T-shaped manifold
chamber 36. A lip 39 surrounds the aperture 38 in at least one of the portions 34 and
35 so that, when the plates 32 are bonded together, the lips 39 bridge the gaps
between the plates and have the effect of forming a continuous fuel inlet duct
supplying fuel to each of the manifold chambers 36. In addition nipples 40 on at least
one of the portions 34 and 35 of each plate 32 serve to space apart the plates 32 with
the required narrow passages 33 therebetween.
In operation of the evaporator 31 fuel from the outlet 22 of the fuel valve 6
is supplied to the manifold chambers 36 by way of the apertures 38, and at the same
time air passing through the air outlet 30 is caused to enter the narrow passages 33
between the plates 32 by way of the evaporator inlet 42 (see Figure 9). As a result
of the pressure difference across the fuel valve 6, fuel from the manifold chambers
36 is caused to seep through the pores 37 so as to form a thin fuel film on the
evaporation surfaces 34 on the outsides of the plates 32. The air flow along the
narrow passages 33 between the plates 32, which occurs generally in the direction of
the arrow 43 in Figure 11 , causes evaporation of fuel from the evaporation surfaces
34 so that a highly homogenous air/fuel mixture is outputted through the evaporator
oudet 44 towards an exit tube 45 of the system as shown in Figure 9. The small size
of the pores 37 substantially eliminates the production of droplets in the air flow
which would otherwise cause inhomogeneities in the air/fuel mixture. Any fuel from
the fuel films on the evaporation surfaces 34 which passes towards the bottom of the
evaporation surfaces without being evaporated into the air flow may be collected and
conducted to the float bowl 8 for recirculation within the system. The evaporator 31
may be replaced by an evaporator having non-porous, non-reticulated evaporation
surfaces as described above with reference to Figures 1 to 7 if required.
As described in detail in International Published Application No. WO
94/16211, the exit tube 45 incorporates a valve member (not shown) which serves to
change the system between two modes of carburettor operation, namely lean
operation, which is provided up to about three quarters load, and rich operation in
which additional fuel may be supplied by way of a fixed fuel restrictor provided for
starting and full load operation in parallel with the fuel valve 6. In lean operation the
throttle is progressively opened by the governor up to full throttle as the load is
increased. Thereafter, as the load is further increased, change over to rich operation
takes place, and the throttle is closed as additional fuel is introduced in order to
prevent a stepwise increase in torque. Further increase in load leads to progressive
opening of the throttle again, up to full throttle.
Figure 19 shows a variant 1 ' of the carburettor metering system previously
described with reference to Figures 8 to 12, the variant incoφorating an air control
valve 5' and a fuel valve 6', and the parts of this variant being indicated in Figure 19
by the same reference numerals as the corresponding parts in Figure 8 with primes
added thereto. In this case the complete housing part 3' is sealed and contains an
evaporator 31 ' supported by shoulders 150 above an exit tube 45'. A main air inlet
150 is partially covered by the gate member 14' of the air control valve 5' , and the
upper face of the gate 9" is subjected to the housing pressure while the lower face of
the gate 9' is subjected to the outside pressure applied by way of an air restrictor 152
whose function is to damp out oscillations of the gate 9' and to delay movement of
the gate 9' in response to air flow changes, thus providing temporary mixture
enrichment during acceleration and improving the response to transient demands. If
required, the pivoted gate 9' can be replaced by a bellows or piston arrangement.
Figure 20 shows three possible fuel valve arrangements, each of which will require
a corresponding profile of the cut-out in the gate member 14' of the air control valve
5 ' so that the relationship between air flow and air/fuel ratio is appropriate for the
application. In A the fuel valve member 25' has a constant circular cross-section
along its length whereas, in C, part of the fuel valve member 25' is tapered with a
conical angle matching the conical angle of a section of the bore within which the
tapered part is displaceable so as to define therebetween an annular passage having
a length which varies in proportion to the width of the passage (and such that, when
the valve member is in the closed position, the width and length of the passage is
substantially zero. In C a tapered part of the fuel valve member 25' is displaceable
to vary the throughflow cross-section through a restriction 154.
Figure 13 shows an alternative carburettor metering system 101 for supplying
an air/fuel mixture to a governor-controlled single cylinder lawnmower engine, the
system comprising an evaporator 102 for receiving fuel from a fuel reservoir 103 and
air from an air inlet 104 and for supplying air/ fuel mixture to an engine by way of
an outlet 106 in dependence on the position of a throttle 105. The fuel reservoir 103
incoφorates a float 107 for controlling the level 108 of fuel in the reservoir 103 by
means of a valve 109.
The evaporator 102 consists of a flow duct 110 of generally rectangular cross-
section within which a stack of generally parallel metal plates 111 is accommodated.
The plates 111 are spaced apart by spacers (not shown) which define narrow passages
113 for flow of air between the plates 111. Each of the plates 111 has a cross-
sectional shape as shown in Figure 1 having a thickness which is at a maximum close
to the air inlet 104 to the evaporator 102 and which decreases progressively towards
the outlet 106 of the evaporator 102. Thus the evaporation surfaces 114 provided on
both sides of the plates 111 (apart from the outermost plates which have such an
evaporation surface on only one side) are shaped so as to ensure that the air passages
113 have a cross-section which is at a minimum close to the air inlet 104 and which
increases progressively towards the outlet. Each air passage 113 is in the form of a
venturi having a throat 115 in the vicinity of a fuel supply pipe 112 by means of
which fuel is supplied to the plates 111.
In operation of the carburettor metering system, air drawn in through the inlet
104 passes through a gate valve 116 which is in the form of a hinged flap to be lifted
by the air flow against its own weight and/or a light spring and which provides a
substantially constant pressure difference in the air flow. The air then flows along
the narrow passages 113 between the plates 111 of the evaporator 102, and, at the
throat 115 of each venturi, provides a pressure depression which causes fuel to flow
from the fuel supply pipe 112 onto the evaporation surfaces 114, the fuel being
supplied to the fuel supply from the fuel reservoir 103 by way of a restrictor 117.
A fuel film of large surface area is thus provided over the evaporation surfaces 113
of the plates 111, and the passage of the air, which has been warmed prior to entry
into the inlet 104, over the evaporation surfaces 114 results in evaporation of fuel into
the air flow.
The pressure applied to the fuel surface within the float-controlled fuel
reservoir 103 is related to the air pressure at the inlet 104 with a result that the sum
of the pressure difference across the fuel restrictor 117 and the hydrostatic pressure
difference (due to the difference between the level of fuel in the fuel supply pipe 112
and the fuel level 108 in the fuel reservoir 103) is the same as the sum of the air
pressure difference across the gate valve 116 and the pressure drop at the venturi
throats 115. Thus the evaporation of fuel into the air flow is proportional to the air
flow, and a substantially constant air/fuel mixture of highly uniform consistency is
obtained.
Such a carburettor metering system may be used to supply a substantially
constant air/fuel mixture or more likely an air/fuel mixture having a ratio which
varies with load in order to minimise emissions. The provision of the gate valve 116
enables the fuel supply pipe 102 to be arranged at a level higher than the fuel level
108 in the fuel reservoir 103 so as to prevent leakage of fuel in the evaporator 102
in the absence of the required air pressure.
Figures 15 and 16 show sections through a modified carburettor 120 which
may be used in such a system. As will be apparent from Figure 15, showing a
section taken along the line D-D in Figure 16, the plates 121 are of constant thickness
along their lengths. However the narrow passages 122 between the plates 121
nevertheless constitute Venturis by virtue of the fact that, as will be appreciated from
Figure 16 showing a section taken along the line C-C in Figure 15, adjacent plates
121 are spaced apart by spacers 123 providing shaped surfaces 124 on opposite sides
of the intervening passage 122 which define a throat 125 close to the air inlet at which
the passage cross-section is at a minimum. In this case fuel is supplied to the plates
123 in the vicinity of the throats 125 of the Venturis by means of fuel supply pipes
126.
Figure 17 is a sectional view, similar to that of Figure 16, of a further
modified evaporator 130 which may be used in such a system. In this case the plates
of the evaporator are again of substantially constant thickness as shown in Figure 15.
However each plate is separated by a shaped central spacer 132 such that air flows
occur in parallel along passage portions 133 and 134 on the two sides of the spacer
132. It will be appreciated that each passage portion 132 and 133 constitutes a
venturi, and that accordingly the required control of fuel supply may be obtained by
supplying fuel to the evaporator plates in the vicinity of the throat of each venturi.
Figure 18 is a graph showing both the air flow (solid line) and the fuel flow
(broken line) within the evaporator against the applied pressure difference ΔP across
the evaporator. Air flow is initiated at a particular pressure difference sufficient to
overcome the resistance of the gate valve 116, and fuel flow is initiated at a pressure
difference sufficient to overcome the hydrostatic pressure due to the difference in
level between the fuel supply pipe 112 of the evaporator and the fuel level in the fuel
reservoir. It will be appreciated that the fuel flow will be substantially proportional
to the air flow over a substantial pressure range R with the result that the required
substantially constant mixture strength will be obtained over a wide range of load in
a small governor-controlled engine.