US3620651A - Fluid flow apparatus - Google Patents

Fluid flow apparatus Download PDF

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US3620651A
US3620651A US8340A US3620651DA US3620651A US 3620651 A US3620651 A US 3620651A US 8340 A US8340 A US 8340A US 3620651D A US3620651D A US 3620651DA US 3620651 A US3620651 A US 3620651A
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sheet
flexible sheet
thrust
fluid flow
flexible
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Peter Frederick Hufton
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International Combustion Holdings Ltd
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International Combustion Holdings Ltd
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H11/00—Marine propulsion by water jets
    • B63H11/02—Marine propulsion by water jets the propulsive medium being ambient water
    • B63H11/04—Marine propulsion by water jets the propulsive medium being ambient water by means of pumps
    • B63H11/06—Marine propulsion by water jets the propulsive medium being ambient water by means of pumps of reciprocating type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/025—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/12—Machines, pumps, or pumping installations having flexible working members having peristaltic action
    • F04B43/14—Machines, pumps, or pumping installations having flexible working members having peristaltic action having plate-like flexible members

Definitions

  • Fluid flow apparatus operable either as a pump [52] US. Cl. 417/436, or as a motor in which a flexible sheet is constrained by means 115/28 A, 416/81 of connections at spaced points along its length to follow a [51] Int. Cl ..F04b 19/00, traveling wave motion.
  • the flexible sheet forms one bounding B63h l/30, F03d 5/06 surface for a fluid flow path which is also bounded by an op- [50] FieldofSear-ch 417/436, posed sideplate which may be another flexible sheet.
  • the 437, 476, 475, 479, 481; 416/79, 80, 81, 82, 83; traveling wave motion maintains the flexible sheet in traveling 1 15/28 A contact with the sidewall.
  • SHEET 11 [1F 13 H6. Para? [7/1 701v INVENTOR ATTORNEY PATENTEUNUV 1 6 I97
  • This invention relates to fluid flow apparatus, and has particular, but not exclusive reference to fluid flow apparatus for use as fans.
  • the object of the present invention is to provide apparatus in which fluid may be pumped by a nonrotating impeller.
  • apparatus comprising a fluid flow path, at least one side of the fluid flow path being a flexible sheet, a plurality of members disposed along the length of the flexible sheet and connected to the flexible sheet, the members being constrained to have a sequential movement such that movement of the flexible sheet is constrained to the movement of a traveling transverse wave along the sheet.
  • the members may be oscillatable members.
  • the ends of the flexible sheet may be operatively interconnected to form a loop capable, in use, of transferring tension from one end of the flexible sheet to the other end outside the sheet.
  • the flexible sheet may be capable of transmitting tension along itself without substantial increase in the length of sheet.
  • the present invention also provides apparatus which comprises a fluid flow path, at least one side of the fluid flow path being a flexible sheet, a plurality of oscillatable members disposed along the length of the sheet and connected to the flexible sheet, the oscillatable members being constrained to have a sequential movement such that the movement of the flexible sheet is constrained to the movement of a traveling transverse wave along the sheet, the sides of the flexible sheet moving adjacent to, and in the plane of, sideplates.
  • the present invention also provides apparatus comprising a fluid flow path, which fluid flow path includes a pair of noninterconnected opposed sides, one at least of the opposed sides being a flexible sheet, there being a plurality of oscillatable members disposed along the length of the flexible sheet and operatively connected to the flexible sheet, the oscillatable members being constrained to have a sequential movement, such that movement of the flexible sheet is constrained to the movement of a traveling transverse wave along the sheet.
  • the oscillatable members may each comprise a thrust rod connected to the sheet at one end, and operatively connected to an eccentric at the other end.
  • the flexible sheet may have a plurality of weights distributed along the sheet, preferably uniformly along the sheet.
  • the thrust rods may be hollow tubes. The mass of each weight connected to a thrust rod, together with the mass of its associated portion of thrust rod may be substantially equal to the mass of any one of the weights not connected to a thrust rod.
  • the flexible sheet may be of a length equal to one wavelength of the traveling transverse wave, and opposite ends of the flexible sheet may be rigidly interconnected.
  • the thrust rods may be disposed at positions successively one-quarter of a wavelength from each other along the sheet.
  • the end thrust rods may be constrained by the same eccentric.
  • the thrust rods may each include at least one universal joint along their length.
  • the thrust rods may be supported in bearings which can be lubricated under pressure, preferably with a lubricant compatible with the fluid passed through the apparatus.
  • the eccentrics may all be mounted upon a common shaft.
  • bell cranks may be used to transmit motion from the eccentrics to the thrust rods.
  • the bypass may have a nozzle so that, in use, fluid is fed from the exit end directly into the inlet end, in the direction of flow.
  • the bypass may include a fluid flow control valve.
  • the flexible sheet may be of a length greater than one and one-half wavelengths of the traveling transverse wave and may have an operative portion of a length equal to one and one-half wavelengths of the traveling transverse wave and the ends of the sheet may be rigidly interconnected.
  • pairs of flexible sheets may be separated by a rigid plate.
  • pairs of flexible sheets may be arranged in contraflexing relationship and may directly face each other.
  • a compressor which comprises at least one flexible sheet having a length of greater than one wavelength of the traveling transverse wave, and of a tapering width, the flexible sheet being wider at the inlet than at the outlet.
  • a further form of compressor may comprise a flexible sheet having traveling transverse waves of successively reducing wavelength along the sheet in the direction of fluid flow.
  • the present invention further provides a method of inducing flow in a fluid, said method comprising constraining the fluid in a duct having at least one flexible wall and applying cyclic forces to the flexible wall so as to impose thereon a traveling transverse wave motion whereby the fluid is impelled to flow in the duct in the direction of the wave motion, the kinetic energy in the flexible wall being utilized as an energy reservoir, to spread the energy input from the cyclic forces to the wall to minimize fluctuations in energy in ut to the fluid from the wall along the length of the wall in the direction of fluid flow.
  • a method of generating mechanical energy from a fluid at a relatively high pressure which comprises constraining the fluid in a duct having at least one flexible sidewall, the latter being constrained so as to move in a traveling transverse wavelike motion, expanding the fluid at the relatively high pressure to a relatively low pressure by causing a portion of the traveling wave to move in the direction of the relatively low pressure.
  • FIG. 1 is a diagrammatic view of one arrangement of flexible sheets in a fluid flow path.
  • FIG. 2 is a development of a wave along one flexible sheet.
  • FIG. 3 is a graph illustrating thrust point loci on the flexible sheets.
  • FIG. 4 is a graph illustrating the relationship between thrust point displacement, total power, and power per thrust point.
  • FIG. 5 is a block schematic of a multifan unit.
  • FIG. 6 is a section through a bond between a sheet and a thrust rod.
  • FIG. 7 is a section through a bond between a weight and a sheet.
  • FIG. 8 is a section through a compressor pump embodying the invention.
  • FIG. 8a is a section along the line XllA-XlllA of H6. 8.
  • FIG. 9 is a diagrammatic view of an alternative form of compressor.
  • FIG. I0 is a diagrammatic representation of alternative ar rangernents of the flexible sheets.
  • FIG. 11 is an elevation, partly in section of a second embodiment of the invention.
  • FIG. 12 is a sectional view along the lines XXIA, and XXIB of FIG. 11.
  • FIG. 13 is a schematic view of a single flexible sheet
  • FIG. 14 illustrates a section of FIG. 13.
  • FIG. 15 is a seal between a flexible sheet and a sideplate.
  • FIG. 16 is a side elevation, partly in section of a further embodiment of the invention.
  • FIG. 17 is a plan view along the line XVII-XVII of FIG. 16.
  • FIG. 18 is a cross section along the line XVIII-XVIII of FIG. 16.
  • FIG. 19 is a detail of FIG. 16.
  • FIG. 20 is a cross section along the line XX-XX of FIG. 16.
  • FIG. 21 is a part view along the arrow XXI of FIG. 20.
  • FIG. 22 is a detail of a part of the embodiment.
  • FIG. 23 is an enlarged view of a sheet.
  • FIG. 24 is a cross section along the lines XXIVXXIV of FIG. 23.
  • FIG. 25 is a plan view along the arrow XXV of FIG. 24.
  • FIG. 26 is a detail of an end joint of the sheet.
  • FIG. 27 is a cross section along the line XXVII-XXVII of FIG. 24, and
  • FIG. 28 is a graph of sheet displacement.
  • FIG. 1 shows four flexible sheets 1, 2, 3, and 4 between two walls 5 and 6.
  • Each of the flexible sheets is capable of being vibrated to set up a traveling transverse wave, hereinafter referred to as a traveling wave in the sheet, which moves in the direction of the arrow 7. This will cause a fluid flow in the direction of the arrow 8.
  • the length of each sheet, L is equal to one wavelength of the traveling wave, and the distance between thewalls 5 and 6 is equal to By, where y is equal to the amplitude of the traveling wave in one direction.
  • FIG. 2 the advance of the position of maximum amplitude can be followed along the traveling wave.
  • the FIG. shows nine positions of the flexible sheet, from zero to one cycle in steps of one-eighth of a cycle.
  • the positions of maximum amplitude to the left of the flexible sheet (when seen in the drawing) are designated A1
  • the positions of maximum amplitude to the right of the flexible sheet are designated A2.
  • the distance along the convolutions of the flexible sheet is greater than the wavelength of the traveling wave in the sheet and is in fact equal to the surface length of the traveling wave. If the loci of a series of fixed points on a pair of contraflexing sheets are followed as the sheets fluctuate, different parts of the sheet will be seen to follow different loci.
  • the loci of the points E, B, C, D and E, B, C, D (E and E occur twice as they are at the start of one wavelength and at the end of the adjacent wavelength) can be seen to be straight lines in the case of the points E and C, and figures of eight in the case of the points B and D. When the points B, B and D, D are 180 out of phase, their heights Z at any given point of time are the same.
  • the traveling wave is set up in the sheet by a series of thrust rods which are described in more detail below.
  • These thrust rods are connected to the sheet at the points B, C, D, and E and cause the sheets to fluctuate.
  • the points E and C have loci which move in straight lines, and thus a simple thrust rod can be used which can reciprocate in a straight line.
  • the points B and D move in a figure of eight, and this means that the thrust rod must be capable of reciprocation and also of lateral movement.
  • FIG. 4 illustrates the relationship between, in the top graph, time and displacement for each of the points B, C, D, and E; in the lower graph, the power needed to be supplied to each thrust point to maintain fluctuation of the sheet; and in the middle graph the total power applied, being a summation of the power applied to each individual thrust point.
  • the points B, C, D, and E correspond with those illustrated in FIG. 3, and the displacement X is in the direction shown in FIG. 3.
  • the power which has to be applied to the thrust point is proportioned to the square of the velocity, i.e., it is a maximum whenever the graph of displacement crosses the central axis, and is zero whenever the graph of displacement indicates a maxmove in step. Thus only four different displacement actions are required to fluctuate the sheet.
  • the flexible sheet is shown schematically.
  • the sheet 220 is shown with its midpoint 221 about to make contact with a sideplate 222.
  • the sheet will be under tension in both directions, the tensions being T1 and T2.
  • the tension vector Tl can be regarded as composed of two further vectors T3 and T4.
  • the tension vector T2 can be resolved into the two components T5 and T6. It can be seen that the two vectors T3 and T5 cancel each other out, and the result of adding the two vectors T1 and T2 is equivalent to the vectors T4 and T6.
  • a force applied to a thrust rod at the points 221 can be resolved into tensions along the sheet. Along a whole wavelength of the sheet, these tensions will cancel themselves out.
  • the only points of the sheet which are different are the ends of the sheet. However, if the ends are interconnected by a member which is capable of carrying tensions, then the whole sheet will be in balance.
  • the thrust rods are heavier than the sheet, and with a plain sheet, the force required to accelerate the thrust rods is greater than the force available from the decelerating sheet. This problem is overcome by increasing the momentum of the sheet by adding weights to the sheet, and reducing the weight of the thrust rod system as much as possible. The sheet can, therefore, transfer energy from the decelerating thrust rods to the accelerating thrust rods.
  • Such a weighted sheet can also perform the two seemingly contradictory functions referred to above.
  • the sheet can be flexible and yet the inertia forces caused by the weights accelerating and slowing down generate tensions in the belt which enable it to resist pressure forces in the same way that an inflated balloon is able to resist deforming forces when it is under tension as a result of its internal pressure. This resistance stops the belt being pushed to one side by the fluid on the high-pressure side of the sheet when the sheet is being used as a pump.
  • the material should have:
  • the material should have;
  • FIGS. 11 and 12 One form of the invention is shown in FIGS. 11 and 12.
  • the sheets 95 and 96 they are disposed one on each side of a center plate 104 and are anchored at each end between rubber buffers 105, 106; 107, 108; 109,110; 111, and 112.
  • the buffers 106 and 111 define two sides of an entrance duct
  • the buffers 108 and 109 define two sides of an exit duct.
  • the eccentric 99 is in the form of an inner circle 113 which is mounted eccentrically upon a shaft 114 and is prevented from rotating upon the shaft by the key 115.
  • Surrounding the inner circle 113 is an outer circle 116, which is clamped between two collars 117 and 118.
  • the upper of the collars, 118 has a hemispherical socket 119, which cooperates with a hemispherical socket 120 to clamp a ball 121 between and form a universal joint.
  • the ball 121 is joined to a further ball 122 by a thrust rod 123, which ball 122 is a second pair of hemispherical sockets 124, 125, and forms a second universal joint.
  • the second universal joint is connected to a crosshead 126, and the first universal joint has a bearing housing restraint link 127 to counteract the torque developed when the eccentric is operating.
  • the righthand side of FIG. 12 illustrates the method by which the flexible sheets are secured to their sup ports. Extending from the crosshead l26a,is a thrust rod 128 which carries a reinforcing bar 129. The flexible sheet is riveted between the reinforcing bar 129 and a clamping bar on one side, and the flexible sheet 96'is riveted between a clamping bar 131 and a reinforcing bar 132.
  • the flexible sheets are riveted at the top and the bottom to an end frame 133.
  • the flexible sheets 97 and 98 are connected to their respective reinforcing and clamping bars. It can be seen that the flexible sheet is supported by the clamping bar on either side of the plate 104.
  • the shaft 114 is mounted in bearings 134 and 135, and is provided with two sets of balanced weights 136 and 137 each of which comprises a pair of individually variable bobs 138, 139, and 140, 141 which can be adjusted angularly to balance the shaft 1 14.
  • the four flexible sheets are provided with a series of weights 142, 143, 144, and 145, the function of which has been explained above.
  • the unit is operated by rotating the shaft 1 14, which in turn rotates the eccentrics, and causes the thrust rods to reciprocate the crossheads and the flexible sheets.
  • the points 146 and 147, as seen in FIG. 11, will move laterally and this movement is taken up by the universal joints 148, 149. and 150, 151.
  • theflexible sheet is protected by a pair of rubber cushions 153, 154 where it is joined to a thrust rod 155.
  • a pair of plates 156, 157 is held against the cushions 153, 154 by circlips 158, 159.
  • the cushions are bonded to the flexible sheet, and increase the radius of curvature about which the sheet bends, so reducing the tendency of the sheet to kink where it is joined to the thrust rod, and also reducing bending stresses in the sheet.
  • FIG. 15 One form of seal between a flexible sheet 224 and a sideplate 255 is shown in FIG. 15.
  • the seal 226 is substantially I'I-shaped in cross section, with the two upper arms, as seen in FIG. 15 splayed apart by contact with the sideplates. In some cases if leakage is not too great a problem, a very small gap can be left between the sidewalls and the edges of the sheets.
  • FIG. 7 illustrates the arrangement which is used to attach weights to the flexible sheet 152. Again, two annular cushions 160, 161 are bonded to the belt, and a pair of weights I62, 163 are attached to the belt by a rivet 164.
  • FIG. 5 shows five flow paths 176 to 180, each of which has one or more flexible sheets, and a motor 181 to 185 to drive the flexible sheet or sheets in its path.
  • a motor 181 to 185 to drive the flexible sheet or sheets in its path.
  • one or more of the motors is shut down, and a damper is placed in the flow path to prevent the fluid being pumped from seeping back past the stationary sheet.
  • FIGS. 8 and 8a One form of a compressor unit is illustrated diagrammatically in FIGS. 8 and 8a.
  • the compressing action in this unit is obtained by causing the gas to pass at constant velocity along a duct of reducing cross-sectional area.
  • This compressor comprises a tapering duct 186 which has four flexible sheets 187, 188, 189, and 190.
  • the sheets are 12 wavelengths long but of a tapering height, i.e., the width of the sheet reduces.
  • This taper is best seen in FIG. 8, and each of the gaps between the lines, e.g. 191, 192 of FIG. 8 indicate one compressor stage.
  • the ninth stage is shown to have an intermediate takeoff duct 193.
  • Each of the exit ducts, the intermediate duct 193, and the normal outlet duct 194, is equipped with a pair of butterfly closure valves 195, 196, and 197, 198, which can be used to control the output of the compressor.
  • the intermediate duct valves are closed, and the normal outlet duct valves are open, this will give the maximum compression.
  • FIG. 9 An alternative form of compressor is shown in FIG. 9.
  • the compressing action in this unit is obtained by causing gas to pass at reducing velocity along a duct of constant cross-sectional area.
  • This compressor utilizes the flexibility of the flexible sheet.
  • the compressor comprises a fluid flow duct 199, in which there is a flexible sheet 200 which is driven by a series of thrust rods 201 which are reciprocated by the eccentrics 202 on the shaft 203.
  • the shaft is shown to be supported in bearings 204 and 205 at either end.
  • Five chambers can be distinguished, 206, 207, 208, 209, and 210.
  • the two end chambers, 206 and 210 are shown to be open to the inlet and the outlet respectively.
  • the chambers get progressively smaller as they go from the inlet to the outlet.
  • the shape and size of the chambers change continuously as the shaft is rotated, and the chambers appear to move towards the exit and diminish in size. They are able to do this because one of their walls is the flexible sheet which can adopt any required angle and can form a wave which has different wavelengths along its length.
  • FIG. 9 illustrates a flexible sheet, the operational part of which is two wavelengths long, but the invention can be utilized by sheets of other than a multiple of wavelengths.
  • FIG. 10 illustrates two arrangements using flexible sheets of one wavelength each.
  • the upper arrangement shows a pulsing flow with a single flexible sheet 211 which is mounted at each end in the midpoint of a duct 212.
  • the lower arrangement is different from the other units described above giving a smooth flow, instead of having two rigid walls and a single flexible sheet between them the lower arrangement utilizes two flexible sheets 213 and 214 which are separated by a single plate 215.
  • the minimum length of the plate is one wavelength of the traveling wave, this means that at least one point on the flexible sheet is always in contact with the single plate, and there is no abnormal back passage of the fluid being pumped.
  • FIGS. 16 to 27 An alternative embodiment of the invention is shown in FIGS. 16 to 27.
  • this shows eight flexible sheets 200A to 200H.
  • the four sheets 200A, C, E, and G are connected to move in unison, as are the four sheets 2003, D, F, and H.
  • the sheets are mounted in a duct 201 which is defined by walls 202, 203, 204, and 205.
  • Flanges 206 and 207 are fitted to the ends of the duct to facilitate its positioning in fluid-ducting arrangement.
  • Connected to the sheets 200A, C, E, and G are five pairs of thrust rods 208, 209, 210, and 211.
  • the two end rods 211 move in unison and are designated with the same reference numeral.
  • the thrust rods of each pair are connected to a crosshead 216, 217, 218, 219, 220, 221, 222, 223, 224, and 225.
  • the crossheads are connected by linkages to an eccentric shaft 226.
  • six eccentrics 227, 228, 229, 230, 231, and 232 Connected to the shaft are six eccentrics 227, 228, 229, 230, 231, and 232, which in turn are connected to six shafts 227A 232A by means of bearings 227B 2328.
  • bearings 228 and 231 are larger than the other four bearings. This is because there are four motions needed altogether, two of them are supplied by the large bearings, and the other two are each supplied by the other two bearings.
  • bearings 227 and 229 act in unison, as do bearings 230 and 232.
  • the bearings 227 and 229 balance the bearing 228, and the bearings 230 and 232 balance the hearing 231
  • Connected to the shaft 227A are two cross-shafts 223B and 218B. The remainder of the shafts are connected in the following manner (for the sake of completeness, the first shaft has been included again).
  • the cross-shafts are each supported at both ends by means of bearings. Only one set of these, 219C and 219D is illustrated for reasons of clarity, although each of the cross-shafts is sosupported.
  • Each of the cross-shafts forms a pivot bar for a bellcrank arrangement, one arm of the crank 216A 225A being connected through a shackle link 216E 225E to the crossheads 216 225, and the other arm of the crank 216F 225F being connected to shafts 227A 232A.
  • the shafts and eccentrics are housed within the walls 240, which are joined to the main duct 201 through a felt antivibration washer 241, which is mounted between the bottom of the duct 202 and a flange 242 surrounding the walls 240.
  • the flexible sheet is shown in greater detail in FIGS. 23, 24, 25, 26, and 27.
  • the flexible sheet 250 is almost entirely covered with a series of slats 251.
  • Each of these slats is in two pieces 251A and 25113, the two pieces each being hollow metal and being riveted together through the flexible sheet. The edges of the pieces are cut back as at 252 to prevent them fouling each other during flexure of the sheet.
  • the stiffening bar type 253 used at the quarter wavelength positions is different to the slats 251.
  • the bar comprising two troughshaped channels 254, 255 between which are sandwiched two layers of packing material 256, 257.
  • the bar is reinforced by a pair of plates 258, 259 and 260, 261 which are riveted to the bar.
  • the thrust rods 208 pass through holes 262 in the bar 253.
  • the belt is joined to the end thrust rods 215 by being passed around a rod 263, which is slotted into a hole 264 in a terminating block 265. Tension on the sheet results in the rod being pulled against the inner walls 266 of the block and being jammed into the block by a cleat action.
  • a tie-link is used, as is shown most clearly in FIG. 26.
  • An anchor block 267 is secured to the frame in any suitable manner, and holds one end of a flexible tie 268.
  • the other end of the tie is secured to the terminating block.
  • the tie is made up of several layers of belt material wrapped around shaped ends 269, 270, the ends being trapped in the blocks by a wedging cleat action.
  • the mouth 271 of the block 265 and the mouth 272 of the block 267 is shaped so as to keep the radius of bending of the tie at the point of contact with the blocks high.
  • the termination of the sides of the sheets at the side of the duct is shown most clearly in FIGS. 17 and 18.
  • the sheets 200A 20011 are trapped along their length between truncated triangular prisms 275, and can move between the sloping faces of the two adjacent prisms.
  • the sheet 200G can move between the faces 276 and 277.
  • the sheets are thus held along their length, and are able to form a sea] at the edges when two sheets are adjacent to each other at any point, as for example, the sheets 200E and 200F.
  • FIG. 17 A form of control of the fan is illustrated in FIG. 17.
  • a pair of channels 280, 281 which extend from the exit 282 to the inlet 283 to the fan.
  • a valve plate 284 At one end of each of the channels there is a valve plate 284, which can be moved from a shut position, as shown in the drawing, to an open position by rotating the handle 285.
  • the handle rotates a screw-threaded spindle 286, which in turn moves bosses 287, the latter pull moving arms 288 inwards, and thus pivot the plates 284 open about the pivot points 289.
  • a deflector plate 290 is provided at the one end of each of the channels, and a deflector plate 291 is provided at the other end of each of the channels.
  • Streamlined fairings 292, 293, 294 and 295 are provided to smooth the passage of fluid through the duct. If the fan is operated with the plate valves as shown in FIG. 17, the channels 280, 281 are inoperative, however, if the valves are then gradually opened, fluid flows back along the channels and is diverted back again into the duct and fed directly into the fan under pressure. This fluid operates the fan, so very little effective work is lost by the recirculation arrangement.
  • the materials from which the unit is made would depend upon the function, for example pumping cold air would not present many problems as to the erosion of the belt, and a simple Terylene belt which is similar n manufacture to a con veyor belt would suffice Under higher temperature conditions a glass fiber belt is envisaged which could be impregnated with silicone rubber. Such a belt should enable operating temperatures of up to 230 C to be considered. For still higher temperatures carbon fibers could be utilized The self-lubricating properties of the fibers should enable a dense weave to be used, having a high resistance to gas leakage through the sheet so avoiding the problem of finding a flexible filler suitable for high temperatures
  • the other parts would be made from rigid materials such as metals or reinforced plastics, having a stiffness and corrosion resistance suitable for the environment being considered.
  • the loss coefficient C is a function of the Reynolds number of the leakage flow in the gap.
  • Re p a LI F-
  • Variation of fan speed is a satisfactory method of obtaining control. and so is amplitude variation provided means are used to ensure that the leakage gap is kept constant.
  • both would be relatively expensive and a cheap way can be obtained by allowing unwanted air to recirculate outside the main flow and to be returned into the stream through a variable nozzle. discharging in the flow direction.
  • the upstream pressure energy is then converted into velocity energy at the nonle and as the air jet is caused to diffuse by the resistance of the impellers it does work on the system.
  • the only losses in the recirculating flow are frictional and form drag losses in the duct and nozzle and losses associated with the diffusion process. By proper attention to detail it is anticipated that these losses will be quite small.
  • the losses will be expressed as two components. one associated with the duct which will be a function of the duct velocity head. and the other associated with the nozzle flow which will be a function of the nozzle velocity head.
  • APRFCRBUM lm V28 l nv nn(Pa nn 8 Applying the Bernolli equation to the recirculating flow at the point of entry and the point of nozzle discharge.
  • the system aerodynamic efficiency is defined as Useful work on gas Useful work on gas-l-aerodynamic energy losses
  • the overall fan efficiency can then be determined by multiplying by the mechanical efficiency.
  • Equation 27 could be broken down further, but it becomes ponderous and it is better to evaluate the components of the equation as they stand.
  • the frictional pressure loss can be determined by using the equation for the losses in pipes, using an equivalent hydraulic diameter for the sheets.
  • Power Consumption and Rate of Working Work is done on the gas by the impeller at a constant rate. This energy comes from the kinetic energy of the impeller weights. and the resulting deficit of energy is made up as work is done on the weights by the thrust frames.
  • the sheet can therefore be regarded as an energy reservoir into which energy is fed by the thrust frames. and from which energy is extracted by the gas.
  • This concept can be used to establish a criterion for the belt mass. in that if the ratio of energy extracted by the gas to the ratio of energy present in the impeller is small, then sheet distortions will be minimized. Tests carried out at different energy ratios should indicate at what value the ratio becomes critical.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US8340A 1969-02-07 1970-02-03 Fluid flow apparatus Expired - Lifetime US3620651A (en)

Applications Claiming Priority (1)

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GB673769 1969-02-07

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BE (1) BE745423A (enrdf_load_stackoverflow)
BR (1) BR7016634D0 (enrdf_load_stackoverflow)
DE (1) DE2004870A1 (enrdf_load_stackoverflow)
ES (1) ES376358A1 (enrdf_load_stackoverflow)
FR (1) FR2033309A1 (enrdf_load_stackoverflow)
GB (1) GB1302541A (enrdf_load_stackoverflow)
IL (1) IL33824A (enrdf_load_stackoverflow)
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Cited By (26)

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US4595338A (en) * 1983-11-17 1986-06-17 Piezo Electric Products, Inc. Non-vibrational oscillating blade piezoelectric blower
US5611666A (en) * 1996-04-02 1997-03-18 Au; Ching Y. Fluid forcing device
US5820342A (en) * 1996-12-16 1998-10-13 Au; Ching Yin Fluid forcing device with a fluted roller drive
WO2000004858A1 (en) 1998-07-23 2000-02-03 Saringer John H Mechanism for generating wave motion
ES2170004A1 (es) * 2000-07-31 2002-07-16 Univ De A Coruna Sistema de impulsion ondulante.
US20020146333A1 (en) * 1998-08-11 2002-10-10 Jean-Baptiste Drevet Vibrating membrane fluid circulator
US6463911B1 (en) * 2002-01-14 2002-10-15 Visteon Global Technologies, Inc. Fuel pressure damper
WO2003013412A1 (en) * 2001-08-07 2003-02-20 Saringer Research Inc. Mechanism for generating wave motion
US20050031474A1 (en) * 2001-10-23 2005-02-10 Wilhelm Zackl Valveless pump
WO2007139408A2 (en) 2006-05-29 2007-12-06 Samek Andrzej Method for generating wave motion for propulsion of watercraft
ES2325236A1 (es) * 2005-02-21 2009-08-28 Universidade Da Coruña, Sistema de impulsion ondulante.
WO2012040775A1 (en) 2010-09-27 2012-04-05 Techtonic Pty Ltd Undulatory structures
WO2014089433A1 (en) * 2012-12-07 2014-06-12 Flsmidth A/S Flow channel self-mixing flocculator for a thickener or settling tank
CN104849021A (zh) * 2015-05-28 2015-08-19 山东科技大学 桥梁抗风浪风洞试验模拟波浪装置及其模拟方法
US20180038754A1 (en) * 2016-08-05 2018-02-08 Encite Llc Micro Pressure Sensor
US9968720B2 (en) 2016-04-11 2018-05-15 CorWave SA Implantable pump system having an undulating membrane
US10166319B2 (en) 2016-04-11 2019-01-01 CorWave SA Implantable pump system having a coaxial ventricular cannula
US10188779B1 (en) 2017-11-29 2019-01-29 CorWave SA Implantable pump system having an undulating membrane with improved hydraulic performance
CN111241636A (zh) * 2020-01-09 2020-06-05 浙江理工大学 一种推力杆球铰的优化设计方法
US10799625B2 (en) 2019-03-15 2020-10-13 CorWave SA Systems and methods for controlling an implantable blood pump
US10933181B2 (en) 2017-03-31 2021-03-02 CorWave SA Implantable pump system having a rectangular membrane
US11191946B2 (en) 2020-03-06 2021-12-07 CorWave SA Implantable blood pumps comprising a linear bearing
US11512689B2 (en) 2017-11-10 2022-11-29 CorWave SA Undulating-membrane fluid circulator
US12017059B2 (en) 2022-11-15 2024-06-25 CorWave SA Implantable heart pump systems including an improved apical connector and/or graft connector
US12251550B2 (en) 2022-04-26 2025-03-18 CorWave SA Blood pumps having an encapsulated actuator
US12257427B2 (en) 2022-11-15 2025-03-25 CorWave SA Implantable heart pump systems including an improved apical connector and/or graft connector

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* Cited by examiner, † Cited by third party
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JPS6315480B2 (enrdf_load_stackoverflow) * 1979-05-07 1988-04-05 Piezo Erekutoritsuku Purodakutsu Inc
ES2384684B1 (es) * 2008-10-27 2013-07-05 Universidade Da Coruña Superficie ondulante.
FR2942451B1 (fr) * 2009-02-26 2011-05-06 Andre Schaer Procede et dispositif de propulsion sous-marine basee sur la trainee et la portance d'un element deformable destines a des missions discretes

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DE836006C (de) * 1950-04-04 1952-04-07 Dr Rudolf Blunck Antriebsvorrichtung, insbesondere fuer Wasser- und Luftfahrzeuge
US3294031A (en) * 1965-07-28 1966-12-27 Stephen H Latawic Fluid motor system

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
DE836006C (de) * 1950-04-04 1952-04-07 Dr Rudolf Blunck Antriebsvorrichtung, insbesondere fuer Wasser- und Luftfahrzeuge
US3294031A (en) * 1965-07-28 1966-12-27 Stephen H Latawic Fluid motor system

Cited By (44)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4595338A (en) * 1983-11-17 1986-06-17 Piezo Electric Products, Inc. Non-vibrational oscillating blade piezoelectric blower
US5611666A (en) * 1996-04-02 1997-03-18 Au; Ching Y. Fluid forcing device
US5820342A (en) * 1996-12-16 1998-10-13 Au; Ching Yin Fluid forcing device with a fluted roller drive
WO2000004858A1 (en) 1998-07-23 2000-02-03 Saringer John H Mechanism for generating wave motion
US6029294A (en) * 1998-07-23 2000-02-29 Saringer Research Inc. Mechanism for generating wave motion
US6269500B1 (en) * 1998-07-23 2001-08-07 Saringer Research Inc. Mechanism for generating wave motion
US6689076B2 (en) 1998-07-23 2004-02-10 Saringer Research Inc. Mechanism for generating wave motion
US6659740B2 (en) * 1998-08-11 2003-12-09 Jean-Baptiste Drevet Vibrating membrane fluid circulator
US20020146333A1 (en) * 1998-08-11 2002-10-10 Jean-Baptiste Drevet Vibrating membrane fluid circulator
ES2170004A1 (es) * 2000-07-31 2002-07-16 Univ De A Coruna Sistema de impulsion ondulante.
WO2003013412A1 (en) * 2001-08-07 2003-02-20 Saringer Research Inc. Mechanism for generating wave motion
US20050031474A1 (en) * 2001-10-23 2005-02-10 Wilhelm Zackl Valveless pump
US7101159B2 (en) * 2001-10-23 2006-09-05 Wilhelm Zackl Valveless pump
US6463911B1 (en) * 2002-01-14 2002-10-15 Visteon Global Technologies, Inc. Fuel pressure damper
ES2325236B1 (es) * 2005-02-21 2010-03-11 Universidade Da Coruña, Sistema de impulsion ondulante.
ES2325236A1 (es) * 2005-02-21 2009-08-28 Universidade Da Coruña, Sistema de impulsion ondulante.
WO2007139408A2 (en) 2006-05-29 2007-12-06 Samek Andrzej Method for generating wave motion for propulsion of watercraft
WO2012040775A1 (en) 2010-09-27 2012-04-05 Techtonic Pty Ltd Undulatory structures
EP2622219A4 (en) * 2010-09-27 2017-05-31 Techtonic Pty Ltd Undulatory structures
WO2014089433A1 (en) * 2012-12-07 2014-06-12 Flsmidth A/S Flow channel self-mixing flocculator for a thickener or settling tank
CN104849021A (zh) * 2015-05-28 2015-08-19 山东科技大学 桥梁抗风浪风洞试验模拟波浪装置及其模拟方法
CN104849021B (zh) * 2015-05-28 2018-05-22 山东科技大学 桥梁抗风浪风洞试验模拟波浪装置及其模拟方法
US9968720B2 (en) 2016-04-11 2018-05-15 CorWave SA Implantable pump system having an undulating membrane
US10166319B2 (en) 2016-04-11 2019-01-01 CorWave SA Implantable pump system having a coaxial ventricular cannula
US12005245B2 (en) 2016-04-11 2024-06-11 CorWave SA Implantable pump system having an undulating membrane
US10398821B2 (en) 2016-04-11 2019-09-03 CorWave SA Implantable pump system having an undulating membrane
US11712554B2 (en) 2016-04-11 2023-08-01 CorWave SA Implantable pump system having a coaxial ventricular cannula
US11097091B2 (en) 2016-04-11 2021-08-24 CorWave SA Implantable pump system having a coaxial ventricular cannula
US11298522B2 (en) 2016-04-11 2022-04-12 CorWave SA Implantable pump system having an undulating membrane
US11454563B2 (en) * 2016-08-05 2022-09-27 Encite Llc Micro pressure sensor
US20180038754A1 (en) * 2016-08-05 2018-02-08 Encite Llc Micro Pressure Sensor
US11623077B2 (en) 2017-03-31 2023-04-11 CorWave SA Implantable pump system having a rectangular membrane
US10933181B2 (en) 2017-03-31 2021-03-02 CorWave SA Implantable pump system having a rectangular membrane
US11512689B2 (en) 2017-11-10 2022-11-29 CorWave SA Undulating-membrane fluid circulator
US11446480B2 (en) 2017-11-29 2022-09-20 CorWave SA Implantable pump system having an undulating membrane with improved hydraulic performance
US10188779B1 (en) 2017-11-29 2019-01-29 CorWave SA Implantable pump system having an undulating membrane with improved hydraulic performance
US12214182B2 (en) 2017-11-29 2025-02-04 CorWave SA Implantable pump system having an undulating membrane with improved hydraulic performance
US10799625B2 (en) 2019-03-15 2020-10-13 CorWave SA Systems and methods for controlling an implantable blood pump
CN111241636B (zh) * 2020-01-09 2023-04-25 浙江理工大学 一种推力杆球铰的优化设计方法
CN111241636A (zh) * 2020-01-09 2020-06-05 浙江理工大学 一种推力杆球铰的优化设计方法
US11191946B2 (en) 2020-03-06 2021-12-07 CorWave SA Implantable blood pumps comprising a linear bearing
US12251550B2 (en) 2022-04-26 2025-03-18 CorWave SA Blood pumps having an encapsulated actuator
US12017059B2 (en) 2022-11-15 2024-06-25 CorWave SA Implantable heart pump systems including an improved apical connector and/or graft connector
US12257427B2 (en) 2022-11-15 2025-03-25 CorWave SA Implantable heart pump systems including an improved apical connector and/or graft connector

Also Published As

Publication number Publication date
GB1302541A (enrdf_load_stackoverflow) 1973-01-10
ES376358A1 (es) 1972-07-01
BR7016634D0 (pt) 1973-02-08
DE2004870A1 (de) 1970-09-17
IL33824A0 (en) 1970-04-20
FR2033309A1 (enrdf_load_stackoverflow) 1970-12-04
IL33824A (en) 1973-05-31
NL7001594A (enrdf_load_stackoverflow) 1970-08-11
BE745423A (fr) 1970-07-16

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