CA1213269A - Mixing apparatus - Google Patents
Mixing apparatusInfo
- Publication number
- CA1213269A CA1213269A CA000420805A CA420805A CA1213269A CA 1213269 A CA1213269 A CA 1213269A CA 000420805 A CA000420805 A CA 000420805A CA 420805 A CA420805 A CA 420805A CA 1213269 A CA1213269 A CA 1213269A
- Authority
- CA
- Canada
- Prior art keywords
- rotor
- passages
- inlet
- axis
- passage
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23K—FEEDING FUEL TO COMBUSTION APPARATUS
- F23K5/00—Feeding or distributing other fuel to combustion apparatus
- F23K5/02—Liquid fuel
- F23K5/08—Preparation of fuel
- F23K5/10—Mixing with other fluids
- F23K5/12—Preparing emulsions
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
- B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
- B01F25/60—Pump mixers, i.e. mixing within a pump
- B01F25/64—Pump mixers, i.e. mixing within a pump of the centrifugal-pump type, i.e. turbo-mixers
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Mixers Of The Rotary Stirring Type (AREA)
Abstract
ABSTRACT
" MIXING APPARATUS"
Apparatus for mixing fluids comprises a housing (10) affording a substantially annular mixing chamber (15), and an annular rotor (20) mounted for rotation in the mixing chamber, out-wardly extending individual passages (19) being located in the rotor, the inlets to the passages in the rotor being disposed (55) adjacent its axis of rotation, the passages in the rotor leading from the said inlets to the periphery of the rotor (36) and emerging therethrough, the median line (152) through each passage in a plane perpendicular to the axis of the rotor intersecting the circle around the axis of the rotor on which the inlet to the said passages lies at a point A and making a rearward angle with the radius of the rotor which passes through the said point A for that passage.
An inlet chamber (49, 53) communicates with the inlets in the rotor adjacent the axis of rotation of the rotor, the inlet chamber being provided with inlet means for the fluids to be mixed. The mixing chamber has a circular outer wall (37) extending around a major proportion of its circum-ference with a small clearance with the periphery of the rotor.
" MIXING APPARATUS"
Apparatus for mixing fluids comprises a housing (10) affording a substantially annular mixing chamber (15), and an annular rotor (20) mounted for rotation in the mixing chamber, out-wardly extending individual passages (19) being located in the rotor, the inlets to the passages in the rotor being disposed (55) adjacent its axis of rotation, the passages in the rotor leading from the said inlets to the periphery of the rotor (36) and emerging therethrough, the median line (152) through each passage in a plane perpendicular to the axis of the rotor intersecting the circle around the axis of the rotor on which the inlet to the said passages lies at a point A and making a rearward angle with the radius of the rotor which passes through the said point A for that passage.
An inlet chamber (49, 53) communicates with the inlets in the rotor adjacent the axis of rotation of the rotor, the inlet chamber being provided with inlet means for the fluids to be mixed. The mixing chamber has a circular outer wall (37) extending around a major proportion of its circum-ference with a small clearance with the periphery of the rotor.
Description
i MIXING APPARATUS
', The present invention is concerned with apparatus for mixing two liquids particularly immiscible liquids and especially for introducing water into fuel supplies, especially hydrophobic fuels, in such a manner as to improve the combustion characteristics of the fuel mixture. However it is also effect in mixing light and heavy fuels such as alcohols and petroleum fuels, such as diesel fuels or higher distillates The apparatus, for ease of reference, will be referred to as an emulsifier. The emulsifier has been developed with the particular problems of industrial oil-~ired boilers in mind, but is also applicable to the supply of fuel to diesel engines, to gas turbines and to fuel injection, or carburetor petrol engines.
British Patent No. 1,572,698 DYNATROL
CONSULTANTS US LID published 30 July 1980 discloses an emulsifier by which, by mechanical means alone without the need for surfactants, emulsions of water and oil can be produced.
Investigations since the filing of that application have revealed that it produces micron size water droplets each carrying a coating of the oil with which the water has been mixed.
Subsequent work has corroborated that the device is effective in mixing waxer and a wide range of hydrocarbon fuels and it will be appreciated that blends with alcohols such as methanol or ethanol can also be emul~iied.
The present invention is concerned with an improvement over the emulsifies shown in said British .
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', The present invention is concerned with apparatus for mixing two liquids particularly immiscible liquids and especially for introducing water into fuel supplies, especially hydrophobic fuels, in such a manner as to improve the combustion characteristics of the fuel mixture. However it is also effect in mixing light and heavy fuels such as alcohols and petroleum fuels, such as diesel fuels or higher distillates The apparatus, for ease of reference, will be referred to as an emulsifier. The emulsifier has been developed with the particular problems of industrial oil-~ired boilers in mind, but is also applicable to the supply of fuel to diesel engines, to gas turbines and to fuel injection, or carburetor petrol engines.
British Patent No. 1,572,698 DYNATROL
CONSULTANTS US LID published 30 July 1980 discloses an emulsifier by which, by mechanical means alone without the need for surfactants, emulsions of water and oil can be produced.
Investigations since the filing of that application have revealed that it produces micron size water droplets each carrying a coating of the oil with which the water has been mixed.
Subsequent work has corroborated that the device is effective in mixing waxer and a wide range of hydrocarbon fuels and it will be appreciated that blends with alcohols such as methanol or ethanol can also be emul~iied.
The present invention is concerned with an improvement over the emulsifies shown in said British .
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- 2 -Patent No. 1572698.
According to the present invention apparatus for mixing fluids comprises: a housing affording a substant-I` tally annular mixing chamber; an annular rotor mounted 5 rotatable and drivable for rotation in a first direction in the mixing chamber; radially outwardly extending } individual passages being located in the rotor, the pass-$ ages in the rotor having inlets near the axis of rotation and outlets at the periphery of the rotor and emerging ! lo there through, wherein the passages in the rotor have a first radially inner portion of cross-sectional area decreasing in the radially oared direction, a second radially outer portion of non-decreasing cross sectional area, and a throat between said first and second portions;
15 and wherein said passages have their outlets peripherally ` displaced relative to said inlets in a second direction opposite the said first direction.
The invention may include any one or more of the following features in any combination. The median line 20 for each passage may make a rearward angle with the radius of the rotor at the Passage inlet, which is in the range up to 35 e.g. 1 to 30 or 5 to 30 or 20 to 25 . An inlet chamber disposed at or adjacent the axis of rotation of the rotor may communicate with the inlets in the rotor.
` 25 The inlet chamber may be provided with inlet means for the fluids to be mixed. The mixing chamber may have a circular outer wall extending around preferably a major ` proportion of its circumference preferably with a clear-ante between the said circular wall and the periphery of 30 the rotor, the circular outer wall extending outwardly i` preferably into a spiral shape so as to define a prefer-ably generally crescent shaped outlet region between the ? preferably spiral shaped wall of the mixing chamber and the periphery of the rotor, the outlet ------------------, I
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region communicating with an outlet passage.
The individual passages extending out through the peripheral surface of the rotor may be spaced from each other by solid regions of the peripheral 5. surface, the ratio of the radial distance from the inlet Jo each passage to the outer surface of the rotor to the radius of the rotor preferably being in the range of 0.4:1 to 0.9:1.
The ratio of the radius ox the rotor to the 10. clearance between the periphery of the rotor and the circular portion of the outer wall of the mixing chamber is preferably at least 200:1.
The radial passages preferably have at least one constriction intermediate their ends. In one 15. preferred form of the invention, 4 to 20 radial passages are provided. In one form of the invent lion each radial passage preferably has a convert gent entry portion leading to the constriction and a divergent outlet portion.
20~ The passages may each comprise a V-shaped convergent inlet portion and a V-shaped divergent outlet portion defining a constriction between them the constriction optionally being a parallel sided throat portion interconnecting the V-shaped 25. inlet end and the V-shaped outlet end of each passage.
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The V-shaped inlet end preferably forms an included angle of 40 to 80 and the V-shaped outlet end preferably forms an included angle of 10 to 40~.
, 5. The radial length of each passage is prefer-ably 0.6 times the radius of the rotor.
The passages may be open at one face of the rotor which is closely spaced from a wall of the missing chamber, or the passages may be closed 10. along their length.
The rotor may be,generally~,conical to enable the area of the inlet to a passage to be about equal to the area of the outlet. The invention also extends to the rotor per Sue lZ~3~9 : 5.
, ,.,, I' . The invention may be put into practice in various ways and two specific embodiment swill be described to :$ illustrate the invention with reference to the s accompanying drawings in which, .- 5. Figure 1 is a flow diagram of a fuel supply system appropriate for use with a high spill return ' fuel injection engine;
Figure 2 is a longitudinal cross-section of a preferred embodiment of an emulsifier in accordance 10. with the present invention;
, Figure 3 is a cross-section on the line III-III of ' Figure Al on a reduced scale, showing the mixing ; chamber and, diagrammatically, the outline of the rotor;
Figures 4 and 6 are cross-sections on the line IVY of . 15. Figure 5, on an enlarged scale showing in detail the s shape of the passages in two forms of the rotor; and l Figure 5 is a cross-section of Figures 4 and 6 Jo on the line V-V.
I Referring now to Figure 1 reference 100 denotes I 20. the fuel injection system of the engine, 101 being the inlet line thereto and 102 being the outlet therefrom to the high spill return line 103.
The inlet 101 to the injector 100 is fed by a line 104 and main fuel pump 105~ The main fuel pump 25. 105 draw sin the fuel and water emulsion via a line 107 from an emulsifier 106 of appropriate type such as that described below with reference to Figures 2 to 5.
The emulsifier is fed with fuel from a fuel tank 110 having a filter 111 in its outlet by a lift pump 30. 112 via a further filter 113 and a line 114.
Al .
Jo Jo The emulsifier is fed with water from a water supply 120 via a filter 121 and a line 122. The water supply may be a header tank, an accumulator driven by the engine e.g. by its water pumper may ye a constant 5. displacement pump. The first two options are preferred.
The spill return line passes through a cooler 130 ego provided with forced cooling by a cooling water inlet 131 Ed outlet 132. The cooled spill return then passes via a line 133 Jo thy smoothing means which are 10. shown as a tank 140 having a vent 141 to atmosphere.
The smoothed spill return then-p,àsses by the line 142 to the emulsifier 106.
The structure of a preferred form of emulsifier in accordance with the invention will now be described.
I, 15. The emulsifier shown in Figures 2 to 5 consists of an inlet chamber housing 10 and a seal housing 11 appropriately secured together in leak-proof fashion.
The housings 10 and 11 between them provide a mixing chamber 15 and a seal chamber 35. Located in the mixing 20. chamber 15 for free rotation therein is a rotor 20 having radial passages 19, the rotor being supported on a drive shaft 21 which extends out through a mechanical seal 23 and the seal housing 11 to an external drive motor 24.
25. The seal 23 is located within the seal chamber 35 formed between the seal housing 11 and inlet chamber housing 10. The seal chamber 35 is separated from the mixing chamber 15 by the rotor 2G except for a small clearance C, between the outer edge of the rotor and 30. the inner peripheral wall 37 of the mixing chamber 15.
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i Liquids may be prevented from passing directly through into the chamfer 35 by the provision of a recirculation flow of the emulsion which is intro-duped through an orifice (not shown) into the seal . 5. housing 11 and which provides a cooling effect for the seal and then recombines with the emulsion in the chamber 15. The housing 10 provides an inlet chamber 50 which is fed my three inlet passages, a water inlet passage 51, a fuel inlet passage 52 and . 10. a spill return passage (not shown). Each supply line 114, 122, and 142 to these passages is prefer-ably provided with an on off valve (not shown) I adjacent the emulsifier.
.' The inlet chamber comprises the rounded sided ' 15. disc shaped chamber 53 at the confluence of the passages 51 and 52, plus a cylindrical chamber 49 located between the central end face 54 of the rotor 20, a wall 55 into which the inner ends of the passage 19 open and a race 56 of the chamber 53.
20. The mixing chamber 15 is defined as being bounded by a front wall 60, an-inner wall 61 extent ding from the inside edge of the front wall parallel to the longitudinal axis of the device, an inclined wall 62 joining the inner wall 61 to an outer side 25. wall, of which part, 37, is cylindrical and part, 66, is on a spiral, and a plane 64 extending across the axis of the housing 10 parallel to the front wall 60 from the rear wall 63 of the part 66 of the side wall. The mixing chamber communicates with an 30. outlet passage 65 disposed tangentially to the rotor `
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(see also Figure 3) and transverse to its axis The circular wall extends around the chamber for 240 and the spiral wall 66 extends outwardly from the ' point 70 to the outer edge of the outlet passage 65.
Jo 5. The mixing chamber includes this part crescent shaped region extending from point 70 to the line 72 across the opening 65. The mixing chamber is largely occupied by the rotor 20.
The clearance, C, between the wall 37 and the 10. outer space of the rotor is preferably at least 0.001"
e.g. 0.001" to 0.070'~, e.g. 0.020 to 0.060 and especially 0.045 to 0.055 inches ~1.1 to 1.4 mums s The generally crescent shaped region may have a Jo flat outer wall 66 as shown in Figure 3. However, one 15. convenient way of making this part of the housing is to mill out the cylindrical mixing chamber and drill the circular outlet opening 65 tangentially to the circular chamber down to the point 78. One can then pick out Jo the region 15 with a milling machine from a line 72 down 20. to the point 70 so as to smooth out the transition between the hole 65 and the circular wall 37 of the its mixing chamber to form the curved region extending from the line 72 to the point 70. In this arrangement, the wall fix need not be flat. The maximum clearance, C2, 25. between the wall 66 and the periphery of the rotor at the point 78 is many times that of the clearance. C
between the wall 37 and the rotor and the ratio C2/C
is preferably at least loo and more desirably at least 1 50:1 or 100:1 and particularly in the range 50 1 to 30. 200:1 or 500:1.
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7' Referring now to Figures 4 and 5 which show the rotor 20, the rotor has a base 80 secured to or formed on a rotor shaft 81 sleeved at 82 to suit the drive , shaft of the motor 24, and having a clearance hole 83 j 5. for the end fixing of the drive shaft which may be a bolt 85 and washer 86 (see Figure I The rotor also Jo has a generally conically shaped top portion 87 in which eight outwardly extending passages 19 are formed e.g.
by milling or casting. The top 87 is secured to the I base 8G by four equispaced screws 88 (see Figure 5) passing through holes in the base 88 into lappings in the top 87. In an alternative arrangement the base 80 and the portions 77 are integrally formed and the portion indicated by 87 and cross hatched in Figure 4 is screwed 15. to the base by the screws 88. The periphery of the rotor once the top and base have been secured is given deep gnarling 90 as illustrated diagrammatically in Figure 5 for one vane 77. The gnarling is preferably a cross-cross pattern of two arrays of parallel grooves inclined 20. at 45 to each other each groove having a maximum depth of 0.010 inches (0.25 mums) and a maximum width of 0.015 inches (0.38 mums) and adjacent parallel grooves being at least 0.020 inches (0.51 mums) apart. More broadly the depths of the grooves can vary from 0.01 preferably OWE 0.1 to 0.25 mm, and the widths of the grooves from 0.02 to 0.4 mums erg. 0,2 to 0.35 mums and the separation of adjacent parallel grooves can vary from 0.5 to 2 mums, e.g. 0.5 to 1 mm.
The rotor has a diameter 3 Dl,where the diameter of 30. the circle 150 (which defines the wall 55 on which the inlets to the passages 19 Lucy Do.
The passages 19 each have an inlet axial length (ILL) of A and an outlet axial length (CAL) of about 0.5 A
where A 3 3/8 (Do). The V-shaped inlet region 172 has it J
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a radial length (IRK) of about 0.09 Do, the outlet ; region has a radial length (OWL) of about 0.9 Do, whilst, its length (OWL) along the median line 152 of the passage (see Figure 5) is about Lowe Do.
'I 5. The median line 152 of the passage is constructed , by joining the mid points of the chords 153 and 154 'I drawn across the inlet wish on the circle 150 which defines the inlet wall 55) and the outlet to the passage respectively.
10~ The angle (AM) between the median line and -the radius through the point A, the mid point of the chord 153, is preferably ~r~JS^20 to especial about 22~5.
I ' The rotor also has an inlet collar 155 at its input,,~ lo. end, the radial extent of which is about 3 Dl/20.
The ducts or passages 19 are inclined backwardly Jo in the sense of the direction of rotation of the rotor (arrow 157 in Figure 5). The passages are thus as yummy-tribal and produce a very slight pumping action in 20. addition to their cavitation function. Alight pressure ', head will thus be developed between the inlet and outlet, of the device in use .
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I The ducts I are also converged in the direction of Jo 25. the rotational axis of the rotor on passing from the ! inlet wall 55 to the outlet wall 36. The angle A of i this convergence is about 15; more broadly it may be in the range 10 to 20. Preferably the rotor is arranged so that the ratio ox ILL to CAL lies in the 30. range 0.2:1 to 0.8:1 e.g. 0.3:1 to 0.7:1 especially 0.4:1 Jo 0.6:1.
The ratio of the length of the passages 19 as measured along the median line ].52 to the diameter of . the rotor is preferably in the range 0.6:1 to 1.35:1 Lo 11 .
e.g. 0.75"1 to 102:1 or especially 0.96:1 to 1.11:1.
The axial convergence is designed to ensure that the flow area at the inlet to each passage 19 is closely the same and preferably virtually the same as the flow , 5. area at the outlet to each passage at the circumference to the rotor. Thus the ratio of inlet flow area IF to the outlet flow area OVA it desirably in the range t 0.8:1 to 1.2:1 and especially in the range 0~9:1 to 1.1:1 and particularly in the range 0.95:1 to 1.05:1.
10. The dimension A is preferably related to the diameter Do of the rotor eye, the circle 150 on which the rotor inlets lie, by the equation:
A - 3 + 2 (Do).
15. With a rotor in which Do = 1.5 inches (3.8 ems) the device can deliver a flow, F, of up to 300 gallons Imperial hour of emulsion with a power requirement (PRY) of 1.5 HOP. for the motor; when Do = 2 inches (5.1 cams F = up to 450 and PRY = 2.5; and when Do = 3 20. inches ~7.6 ems), F = up Jo 600 and PRY = 3Ø
Referring now to Figure 5, the rotor 20 in this embodiment has eight outwardly extending passages 19 equally spaced apart through 45 and extending from the inlet wall 55 defined by the circle lS0) to the 25. outer periphery 36 of the rotor 20.
In this form of the invention the inlet end of I
12.
i each passage is a V-shaped slot 172 including an angle, AIR of 65 and the outlet end is a V-shaped slot 73 including an angle, A, of about 25. The two V-shaped slots interact to form a constriction which is located 5. on the circle 156~
In operation the rotor is rotated in the direction : shown by the arrow 157 in Figure 5 i.e. with the passages facing out backwards with regard to the direction of rotation. The liquids to be mixed are 10. drawn from the inlet chamber by the centrifugal force on the liquid in the passages l-9 and thrown out radially through the passages 19 and caused to hit the wall 37.
The outer wall 36 of the rotor is broken up into eight solid portions 77, each of about the same circumferential 15. length as the outlets 73, and the solid portions 77 may be considered to act as vanes, and as mentioned above they preferably have knurled surfaces 90.
They thus have the function both of shearing the fuel and water mixture in the gap between the wall 37 I` 20. and the wall 36 and propelling it around the circumfer-once of the mixing chamber through the part crescent shaped region 78, where turbulent mixing may be expected to occur and is preferably encouraged by leaving the last 30~ of the outlet wall 66 unsoothed and in the 25. rough condition produced by the milling operation, and then ejecting it through the outlet passage 65.
The constriction 71 has the function of impeding the flow of fluid along the passage 19 and thus increasing its velocity outwardly and the diverging 30. outlet slot 73 then causes a pressure drop in the fluid 13.
,, ., Al resulting in vaporization of the fuel in the mixture.
, The rotor shown is very suitable for fuels having viscosities from 35 Redwood seconds up to 3000 Redwood f . seconds with rotor speeds of 2800 to 7000 rum The 5. rotor is thought to work by vaporisakion of the fuel as it goes through the throat of the passages 19 producing cavitation in the fuel/water mixture, the water droplets are thought to be sheared by the wall 37 and the vanes Andy the fuel is thought to condense I on the surface of the water droplets in the turbulent flow region 78 producing droplets having micron part-ale size and thus promoting smooth and more complete , combustion.
Referring now to the rotor shown in Figure 6, 15. to which Figure 5 also applies, the rotor has a base 80 similar to that of Figure 4. The rotor ha a generally conically shaped top edge 160l eight open-topped outwardly extending passages 19 being formed in the base 80 and opening out along the 20. edge 160. The top wall 160 is juxtaposed to the inclined wall 62 of the housing 10 so as to be substantially parallel thereto and the clearance between 160 and 62 is substantially smaller than ; that between 36 and 37 (Figure 3) for example pro-! ` 25. fireball being less than 0.020 inches (0.50 mums and especially less than 0.015 inches ~0.38 mums) e.g. in the range 0.005 to 0.015 inches ~0.12 to 0.38 mums) and particularly about 0.010 inches (0.25 mums).
The periphery of the rotor is given deep gnarling OWE 90 as illustrated diagrammatically in Figure 5.
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'`' In other respects the combustion is similar to that of Figures 4 and 5. The cavitation and pumping action described for that embodiment, occur because of the close proximity of the top edge 160 of the rotor to the wall 62, (Figure 2).
In one less desired embodiment (not illustrated) the constriction 71 is not present, the inclined passages 19 having the same width in the plane of Figure 5 along : their whole length, but apart from that being as described for Figures 4 and 5 In another simpler embodiment (also not illustr-axed) the axial convergence shown in Figure 4 is elimin-axed or is also eliminated so that the passages 19 are either of the same axial length along their whole radial length but have the constriction 71 and are inclined backwards.
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According to the present invention apparatus for mixing fluids comprises: a housing affording a substant-I` tally annular mixing chamber; an annular rotor mounted 5 rotatable and drivable for rotation in a first direction in the mixing chamber; radially outwardly extending } individual passages being located in the rotor, the pass-$ ages in the rotor having inlets near the axis of rotation and outlets at the periphery of the rotor and emerging ! lo there through, wherein the passages in the rotor have a first radially inner portion of cross-sectional area decreasing in the radially oared direction, a second radially outer portion of non-decreasing cross sectional area, and a throat between said first and second portions;
15 and wherein said passages have their outlets peripherally ` displaced relative to said inlets in a second direction opposite the said first direction.
The invention may include any one or more of the following features in any combination. The median line 20 for each passage may make a rearward angle with the radius of the rotor at the Passage inlet, which is in the range up to 35 e.g. 1 to 30 or 5 to 30 or 20 to 25 . An inlet chamber disposed at or adjacent the axis of rotation of the rotor may communicate with the inlets in the rotor.
` 25 The inlet chamber may be provided with inlet means for the fluids to be mixed. The mixing chamber may have a circular outer wall extending around preferably a major ` proportion of its circumference preferably with a clear-ante between the said circular wall and the periphery of 30 the rotor, the circular outer wall extending outwardly i` preferably into a spiral shape so as to define a prefer-ably generally crescent shaped outlet region between the ? preferably spiral shaped wall of the mixing chamber and the periphery of the rotor, the outlet ------------------, I
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region communicating with an outlet passage.
The individual passages extending out through the peripheral surface of the rotor may be spaced from each other by solid regions of the peripheral 5. surface, the ratio of the radial distance from the inlet Jo each passage to the outer surface of the rotor to the radius of the rotor preferably being in the range of 0.4:1 to 0.9:1.
The ratio of the radius ox the rotor to the 10. clearance between the periphery of the rotor and the circular portion of the outer wall of the mixing chamber is preferably at least 200:1.
The radial passages preferably have at least one constriction intermediate their ends. In one 15. preferred form of the invention, 4 to 20 radial passages are provided. In one form of the invent lion each radial passage preferably has a convert gent entry portion leading to the constriction and a divergent outlet portion.
20~ The passages may each comprise a V-shaped convergent inlet portion and a V-shaped divergent outlet portion defining a constriction between them the constriction optionally being a parallel sided throat portion interconnecting the V-shaped 25. inlet end and the V-shaped outlet end of each passage.
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The V-shaped inlet end preferably forms an included angle of 40 to 80 and the V-shaped outlet end preferably forms an included angle of 10 to 40~.
, 5. The radial length of each passage is prefer-ably 0.6 times the radius of the rotor.
The passages may be open at one face of the rotor which is closely spaced from a wall of the missing chamber, or the passages may be closed 10. along their length.
The rotor may be,generally~,conical to enable the area of the inlet to a passage to be about equal to the area of the outlet. The invention also extends to the rotor per Sue lZ~3~9 : 5.
, ,.,, I' . The invention may be put into practice in various ways and two specific embodiment swill be described to :$ illustrate the invention with reference to the s accompanying drawings in which, .- 5. Figure 1 is a flow diagram of a fuel supply system appropriate for use with a high spill return ' fuel injection engine;
Figure 2 is a longitudinal cross-section of a preferred embodiment of an emulsifier in accordance 10. with the present invention;
, Figure 3 is a cross-section on the line III-III of ' Figure Al on a reduced scale, showing the mixing ; chamber and, diagrammatically, the outline of the rotor;
Figures 4 and 6 are cross-sections on the line IVY of . 15. Figure 5, on an enlarged scale showing in detail the s shape of the passages in two forms of the rotor; and l Figure 5 is a cross-section of Figures 4 and 6 Jo on the line V-V.
I Referring now to Figure 1 reference 100 denotes I 20. the fuel injection system of the engine, 101 being the inlet line thereto and 102 being the outlet therefrom to the high spill return line 103.
The inlet 101 to the injector 100 is fed by a line 104 and main fuel pump 105~ The main fuel pump 25. 105 draw sin the fuel and water emulsion via a line 107 from an emulsifier 106 of appropriate type such as that described below with reference to Figures 2 to 5.
The emulsifier is fed with fuel from a fuel tank 110 having a filter 111 in its outlet by a lift pump 30. 112 via a further filter 113 and a line 114.
Al .
Jo Jo The emulsifier is fed with water from a water supply 120 via a filter 121 and a line 122. The water supply may be a header tank, an accumulator driven by the engine e.g. by its water pumper may ye a constant 5. displacement pump. The first two options are preferred.
The spill return line passes through a cooler 130 ego provided with forced cooling by a cooling water inlet 131 Ed outlet 132. The cooled spill return then passes via a line 133 Jo thy smoothing means which are 10. shown as a tank 140 having a vent 141 to atmosphere.
The smoothed spill return then-p,àsses by the line 142 to the emulsifier 106.
The structure of a preferred form of emulsifier in accordance with the invention will now be described.
I, 15. The emulsifier shown in Figures 2 to 5 consists of an inlet chamber housing 10 and a seal housing 11 appropriately secured together in leak-proof fashion.
The housings 10 and 11 between them provide a mixing chamber 15 and a seal chamber 35. Located in the mixing 20. chamber 15 for free rotation therein is a rotor 20 having radial passages 19, the rotor being supported on a drive shaft 21 which extends out through a mechanical seal 23 and the seal housing 11 to an external drive motor 24.
25. The seal 23 is located within the seal chamber 35 formed between the seal housing 11 and inlet chamber housing 10. The seal chamber 35 is separated from the mixing chamber 15 by the rotor 2G except for a small clearance C, between the outer edge of the rotor and 30. the inner peripheral wall 37 of the mixing chamber 15.
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i Liquids may be prevented from passing directly through into the chamfer 35 by the provision of a recirculation flow of the emulsion which is intro-duped through an orifice (not shown) into the seal . 5. housing 11 and which provides a cooling effect for the seal and then recombines with the emulsion in the chamber 15. The housing 10 provides an inlet chamber 50 which is fed my three inlet passages, a water inlet passage 51, a fuel inlet passage 52 and . 10. a spill return passage (not shown). Each supply line 114, 122, and 142 to these passages is prefer-ably provided with an on off valve (not shown) I adjacent the emulsifier.
.' The inlet chamber comprises the rounded sided ' 15. disc shaped chamber 53 at the confluence of the passages 51 and 52, plus a cylindrical chamber 49 located between the central end face 54 of the rotor 20, a wall 55 into which the inner ends of the passage 19 open and a race 56 of the chamber 53.
20. The mixing chamber 15 is defined as being bounded by a front wall 60, an-inner wall 61 extent ding from the inside edge of the front wall parallel to the longitudinal axis of the device, an inclined wall 62 joining the inner wall 61 to an outer side 25. wall, of which part, 37, is cylindrical and part, 66, is on a spiral, and a plane 64 extending across the axis of the housing 10 parallel to the front wall 60 from the rear wall 63 of the part 66 of the side wall. The mixing chamber communicates with an 30. outlet passage 65 disposed tangentially to the rotor `
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(see also Figure 3) and transverse to its axis The circular wall extends around the chamber for 240 and the spiral wall 66 extends outwardly from the ' point 70 to the outer edge of the outlet passage 65.
Jo 5. The mixing chamber includes this part crescent shaped region extending from point 70 to the line 72 across the opening 65. The mixing chamber is largely occupied by the rotor 20.
The clearance, C, between the wall 37 and the 10. outer space of the rotor is preferably at least 0.001"
e.g. 0.001" to 0.070'~, e.g. 0.020 to 0.060 and especially 0.045 to 0.055 inches ~1.1 to 1.4 mums s The generally crescent shaped region may have a Jo flat outer wall 66 as shown in Figure 3. However, one 15. convenient way of making this part of the housing is to mill out the cylindrical mixing chamber and drill the circular outlet opening 65 tangentially to the circular chamber down to the point 78. One can then pick out Jo the region 15 with a milling machine from a line 72 down 20. to the point 70 so as to smooth out the transition between the hole 65 and the circular wall 37 of the its mixing chamber to form the curved region extending from the line 72 to the point 70. In this arrangement, the wall fix need not be flat. The maximum clearance, C2, 25. between the wall 66 and the periphery of the rotor at the point 78 is many times that of the clearance. C
between the wall 37 and the rotor and the ratio C2/C
is preferably at least loo and more desirably at least 1 50:1 or 100:1 and particularly in the range 50 1 to 30. 200:1 or 500:1.
1, .
.
, , ., .
I
7 9.
/
7' Referring now to Figures 4 and 5 which show the rotor 20, the rotor has a base 80 secured to or formed on a rotor shaft 81 sleeved at 82 to suit the drive , shaft of the motor 24, and having a clearance hole 83 j 5. for the end fixing of the drive shaft which may be a bolt 85 and washer 86 (see Figure I The rotor also Jo has a generally conically shaped top portion 87 in which eight outwardly extending passages 19 are formed e.g.
by milling or casting. The top 87 is secured to the I base 8G by four equispaced screws 88 (see Figure 5) passing through holes in the base 88 into lappings in the top 87. In an alternative arrangement the base 80 and the portions 77 are integrally formed and the portion indicated by 87 and cross hatched in Figure 4 is screwed 15. to the base by the screws 88. The periphery of the rotor once the top and base have been secured is given deep gnarling 90 as illustrated diagrammatically in Figure 5 for one vane 77. The gnarling is preferably a cross-cross pattern of two arrays of parallel grooves inclined 20. at 45 to each other each groove having a maximum depth of 0.010 inches (0.25 mums) and a maximum width of 0.015 inches (0.38 mums) and adjacent parallel grooves being at least 0.020 inches (0.51 mums) apart. More broadly the depths of the grooves can vary from 0.01 preferably OWE 0.1 to 0.25 mm, and the widths of the grooves from 0.02 to 0.4 mums erg. 0,2 to 0.35 mums and the separation of adjacent parallel grooves can vary from 0.5 to 2 mums, e.g. 0.5 to 1 mm.
The rotor has a diameter 3 Dl,where the diameter of 30. the circle 150 (which defines the wall 55 on which the inlets to the passages 19 Lucy Do.
The passages 19 each have an inlet axial length (ILL) of A and an outlet axial length (CAL) of about 0.5 A
where A 3 3/8 (Do). The V-shaped inlet region 172 has it J
10 .
a radial length (IRK) of about 0.09 Do, the outlet ; region has a radial length (OWL) of about 0.9 Do, whilst, its length (OWL) along the median line 152 of the passage (see Figure 5) is about Lowe Do.
'I 5. The median line 152 of the passage is constructed , by joining the mid points of the chords 153 and 154 'I drawn across the inlet wish on the circle 150 which defines the inlet wall 55) and the outlet to the passage respectively.
10~ The angle (AM) between the median line and -the radius through the point A, the mid point of the chord 153, is preferably ~r~JS^20 to especial about 22~5.
I ' The rotor also has an inlet collar 155 at its input,,~ lo. end, the radial extent of which is about 3 Dl/20.
The ducts or passages 19 are inclined backwardly Jo in the sense of the direction of rotation of the rotor (arrow 157 in Figure 5). The passages are thus as yummy-tribal and produce a very slight pumping action in 20. addition to their cavitation function. Alight pressure ', head will thus be developed between the inlet and outlet, of the device in use .
' '`
I The ducts I are also converged in the direction of Jo 25. the rotational axis of the rotor on passing from the ! inlet wall 55 to the outlet wall 36. The angle A of i this convergence is about 15; more broadly it may be in the range 10 to 20. Preferably the rotor is arranged so that the ratio ox ILL to CAL lies in the 30. range 0.2:1 to 0.8:1 e.g. 0.3:1 to 0.7:1 especially 0.4:1 Jo 0.6:1.
The ratio of the length of the passages 19 as measured along the median line ].52 to the diameter of . the rotor is preferably in the range 0.6:1 to 1.35:1 Lo 11 .
e.g. 0.75"1 to 102:1 or especially 0.96:1 to 1.11:1.
The axial convergence is designed to ensure that the flow area at the inlet to each passage 19 is closely the same and preferably virtually the same as the flow , 5. area at the outlet to each passage at the circumference to the rotor. Thus the ratio of inlet flow area IF to the outlet flow area OVA it desirably in the range t 0.8:1 to 1.2:1 and especially in the range 0~9:1 to 1.1:1 and particularly in the range 0.95:1 to 1.05:1.
10. The dimension A is preferably related to the diameter Do of the rotor eye, the circle 150 on which the rotor inlets lie, by the equation:
A - 3 + 2 (Do).
15. With a rotor in which Do = 1.5 inches (3.8 ems) the device can deliver a flow, F, of up to 300 gallons Imperial hour of emulsion with a power requirement (PRY) of 1.5 HOP. for the motor; when Do = 2 inches (5.1 cams F = up to 450 and PRY = 2.5; and when Do = 3 20. inches ~7.6 ems), F = up Jo 600 and PRY = 3Ø
Referring now to Figure 5, the rotor 20 in this embodiment has eight outwardly extending passages 19 equally spaced apart through 45 and extending from the inlet wall 55 defined by the circle lS0) to the 25. outer periphery 36 of the rotor 20.
In this form of the invention the inlet end of I
12.
i each passage is a V-shaped slot 172 including an angle, AIR of 65 and the outlet end is a V-shaped slot 73 including an angle, A, of about 25. The two V-shaped slots interact to form a constriction which is located 5. on the circle 156~
In operation the rotor is rotated in the direction : shown by the arrow 157 in Figure 5 i.e. with the passages facing out backwards with regard to the direction of rotation. The liquids to be mixed are 10. drawn from the inlet chamber by the centrifugal force on the liquid in the passages l-9 and thrown out radially through the passages 19 and caused to hit the wall 37.
The outer wall 36 of the rotor is broken up into eight solid portions 77, each of about the same circumferential 15. length as the outlets 73, and the solid portions 77 may be considered to act as vanes, and as mentioned above they preferably have knurled surfaces 90.
They thus have the function both of shearing the fuel and water mixture in the gap between the wall 37 I` 20. and the wall 36 and propelling it around the circumfer-once of the mixing chamber through the part crescent shaped region 78, where turbulent mixing may be expected to occur and is preferably encouraged by leaving the last 30~ of the outlet wall 66 unsoothed and in the 25. rough condition produced by the milling operation, and then ejecting it through the outlet passage 65.
The constriction 71 has the function of impeding the flow of fluid along the passage 19 and thus increasing its velocity outwardly and the diverging 30. outlet slot 73 then causes a pressure drop in the fluid 13.
,, ., Al resulting in vaporization of the fuel in the mixture.
, The rotor shown is very suitable for fuels having viscosities from 35 Redwood seconds up to 3000 Redwood f . seconds with rotor speeds of 2800 to 7000 rum The 5. rotor is thought to work by vaporisakion of the fuel as it goes through the throat of the passages 19 producing cavitation in the fuel/water mixture, the water droplets are thought to be sheared by the wall 37 and the vanes Andy the fuel is thought to condense I on the surface of the water droplets in the turbulent flow region 78 producing droplets having micron part-ale size and thus promoting smooth and more complete , combustion.
Referring now to the rotor shown in Figure 6, 15. to which Figure 5 also applies, the rotor has a base 80 similar to that of Figure 4. The rotor ha a generally conically shaped top edge 160l eight open-topped outwardly extending passages 19 being formed in the base 80 and opening out along the 20. edge 160. The top wall 160 is juxtaposed to the inclined wall 62 of the housing 10 so as to be substantially parallel thereto and the clearance between 160 and 62 is substantially smaller than ; that between 36 and 37 (Figure 3) for example pro-! ` 25. fireball being less than 0.020 inches (0.50 mums and especially less than 0.015 inches ~0.38 mums) e.g. in the range 0.005 to 0.015 inches ~0.12 to 0.38 mums) and particularly about 0.010 inches (0.25 mums).
The periphery of the rotor is given deep gnarling OWE 90 as illustrated diagrammatically in Figure 5.
I
,` .
'`' In other respects the combustion is similar to that of Figures 4 and 5. The cavitation and pumping action described for that embodiment, occur because of the close proximity of the top edge 160 of the rotor to the wall 62, (Figure 2).
In one less desired embodiment (not illustrated) the constriction 71 is not present, the inclined passages 19 having the same width in the plane of Figure 5 along : their whole length, but apart from that being as described for Figures 4 and 5 In another simpler embodiment (also not illustr-axed) the axial convergence shown in Figure 4 is elimin-axed or is also eliminated so that the passages 19 are either of the same axial length along their whole radial length but have the constriction 71 and are inclined backwards.
.
`:
Claims (9)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. Apparatus for mixing fluids comprising: a housing affording a substantially annular mixing chamber;
an annular rotor mounted rotatably and driveable for rotation in a first direction in the mixing chamber;
radially outwardly extending individual passages being located in the rotor, the passages in the rotor having inlets near the axis of rotation and outlets at the periphery of the rotor and emerging therethrough, wherein the passages in the rotor have a first radially inner portion of cross-sectional area decreasing in the radially outward direction, a second radially outer portion of non-decreasing cross-sectional area, and a throat between said first and second portions; and wherein said passages have their outlets peripherally displaced relative to said inlets in a second direction opposite the said first direction.
an annular rotor mounted rotatably and driveable for rotation in a first direction in the mixing chamber;
radially outwardly extending individual passages being located in the rotor, the passages in the rotor having inlets near the axis of rotation and outlets at the periphery of the rotor and emerging therethrough, wherein the passages in the rotor have a first radially inner portion of cross-sectional area decreasing in the radially outward direction, a second radially outer portion of non-decreasing cross-sectional area, and a throat between said first and second portions; and wherein said passages have their outlets peripherally displaced relative to said inlets in a second direction opposite the said first direction.
2. Apparatus as claimed in claim 1 in which the median line through each passage in a plane perpendi-cular to the axis of the rotor makes an angle with the radius of the rotor at the centre of the passage inlet which is in the range 5° to 30° or 20 to 25°.
3. Apparatus as claimed in claim 1 or claim 2 including an inlet chamber communicating with the inlets in the rotor and disposed at the axis of rotation of the rotor, the inlet chamber being provided with inlet means for the fluids to be mixed.
4, Apparatus as claimed in claim 1 or claim 2 in which the mixing chamber has a circular outer wall extending around a major proportion of its circumference with a small clearance between the said circular wall and the periphery of the rotor.
5. Apparatus as claimed in claim 1 or claim 2 in which the individual passages extend out through the peripheral surface of the rotor and are spaced from each other by solid regions of the peripheral surface, prefer-ably with roughened surfaces at the periphery.
6. Apparatus as claimed in claim 1, in which the passages each comprise a said first portion which is V-shaped when viewed in a direction parallel to the axis of rotation of the rotor.
I Apparatus as claimed in claim 1 or 2, wherein said throat is a parallel-sided portion inter-connecting the first and second portions of each passage.
8. Apparatus as claimed in claim 1 or claim 2 in which the rotor is of generally conical form whereby the individual passages have inlets with a cross-sectional area approximately equal to that of their outlets.
9. Apparatus as claimed in claim 1 or claim 2 in which at least one of the rotor faces which are gener-ally perpendicular to the rotor axis is discontinuous so that the passages are open at that face, and that face is closely spaced from the opposed surface of the mixing chamber.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB8203173 | 1982-02-04 | ||
| GB8203172 | 1982-02-04 | ||
| GB8203173 | 1982-02-04 | ||
| GB8203172 | 1982-02-04 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1213269A true CA1213269A (en) | 1986-10-28 |
Family
ID=26281891
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000420805A Expired CA1213269A (en) | 1982-02-04 | 1983-02-03 | Mixing apparatus |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0089109A1 (en) |
| CA (1) | CA1213269A (en) |
| ES (1) | ES8402512A1 (en) |
| WO (1) | WO1983002733A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0982543A1 (en) * | 1998-08-26 | 2000-03-01 | Abb Research Ltd. | Fuel - water emulsifying in gas turbines |
| EP1253178A1 (en) | 2001-04-17 | 2002-10-30 | Vionnet, Jacques | Aqueous composition for the hydrophobisation of substrates |
| US7186018B2 (en) * | 2003-05-07 | 2007-03-06 | Ashland Licensing And Intellectual Property Llc | Fuel processing device having magnetic coupling and method of operating thereof |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE703282C (en) * | 1939-03-10 | 1941-03-05 | Bader & Halbig | Mixing top |
| DE897997C (en) * | 1941-06-24 | 1953-11-26 | Ernst A Itterlein Fa | Rotary agitator |
| AU459032B2 (en) * | 1969-05-07 | 1975-02-26 | William Hooper Robert | Dynamic mixer and centrifuge combination |
| US3606270A (en) * | 1970-05-14 | 1971-09-20 | Ludish Co | Continuous power blender |
| FR2167688A1 (en) * | 1972-01-05 | 1973-08-24 | Hege Advanced Systems Corp | High energy rotary mixer - with recycle of one constituent to mix with other in rotor |
| GB1572698A (en) * | 1975-12-12 | 1980-07-30 | Dynatrol Consultants Ltd | Mixing apparatus |
| US4066382A (en) * | 1976-06-18 | 1978-01-03 | General Signal Corporation | Surface aeration impeller |
-
1983
- 1983-02-03 WO PCT/GB1983/000029 patent/WO1983002733A1/en unknown
- 1983-02-03 CA CA000420805A patent/CA1213269A/en not_active Expired
- 1983-02-03 EP EP83300558A patent/EP0089109A1/en not_active Withdrawn
- 1983-02-04 ES ES519524A patent/ES8402512A1/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| ES519524A0 (en) | 1984-02-01 |
| WO1983002733A1 (en) | 1983-08-18 |
| EP0089109A1 (en) | 1983-09-21 |
| ES8402512A1 (en) | 1984-02-01 |
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| Date | Code | Title | Description |
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| MKEX | Expiry |