EP0224527A1 - Dispositif de transformation de l'ecoulement d'un fluide - Google Patents

Dispositif de transformation de l'ecoulement d'un fluide

Info

Publication number
EP0224527A1
EP0224527A1 EP86903364A EP86903364A EP0224527A1 EP 0224527 A1 EP0224527 A1 EP 0224527A1 EP 86903364 A EP86903364 A EP 86903364A EP 86903364 A EP86903364 A EP 86903364A EP 0224527 A1 EP0224527 A1 EP 0224527A1
Authority
EP
European Patent Office
Prior art keywords
chamber
core
flow
fluid
spiral
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.)
Withdrawn
Application number
EP86903364A
Other languages
German (de)
English (en)
Inventor
Istvan Majoros
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Majoros Istvan
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0224527A1 publication Critical patent/EP0224527A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G53/00—Conveying materials in bulk through troughs, pipes or tubes by floating the materials or by flow of gas, liquid or foam
    • B65G53/34—Details
    • B65G53/58—Devices for accelerating or decelerating flow of the materials; Use of pressure generators
    • 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
    • B01F25/10—Mixing by creating a vortex flow, e.g. by tangential introduction of flow components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F15D1/0015—Whirl chambers, e.g. vortex valves

Definitions

  • the invention relates to a device for converting a fluid flow of a first type into a fluid flow of a second type according to the preamble of claim 1.
  • Such devices are known from various fields of technology.
  • There are cyclone dust separators which are constructed in such a way that a dust-containing gas flows in through the flow channel which opens tangentially into the chamber at a relatively high pressure, a vortex flow occurring inside the chamber and the dust collecting on the peripheral wall of the chamber due to the centrifugal force.
  • the gas which has now been cleaned, can leave the cyclone separator through an axially arranged passage opening.
  • the side wall of the chamber which has the axial passage opening, generally does not run perpendicular to the chamber axis, but rather at a relatively acute angle to it, in order to keep flow losses low.
  • the invention has for its object to develop a device according to the preamble of claim 1 such that the most favorable flow conditions are obtained.
  • the basic idea of the invention is to generate such a fluid flow within the chamber that it has the shape of a spiral potential vortex. It is thus very effectively possible to convert a fluid which is under a high pressure but has a low flow rate to one which has a high flow rate and a very low pressure.
  • rxw const.
  • r is the distance of a point from the vortex axis
  • w is the flow velocity of the fluid at this point.
  • the indices 1 and 2 refer to two different points and n is a constant, where 0 ⁇ n ⁇ . If n is 1, the conditions are the same as for a potential vortex with closed flow paths.
  • FIGS. 1A and 1B show sectional views of a chamber, which is bounded by a peripheral wall 1, which extends over a spiral arch, and side walls 11 and 12.
  • the peripheral wall 1 runs as shown over an angle that is greater than 360 °, so that there is an overlap area ⁇ .
  • the angle ⁇ can be up to about 30 °.
  • a flow channel opens tangentially into the chamber at the periphery of the chamber.
  • the side walls 11 and 12 are even.
  • the peripheral wall 1 is a spiral, flat surface. It is assumed here that the side walls of the tangential flow channel are flat with the side walls 11 and 12 of the chamber.
  • the upper wall 4 and the lower wall 5 of the tangential flow channel 3 are also flat and each extend perpendicular to the side walls, so that the tangential flow channel 3 has a rectangular cross section, which decreases towards the chamber.
  • the tangential flow channel 3 merges into the overlap area of the peripheral wall 1 and at the inner end of the peripheral wall 1 there is then a passage area 6 which has a rectangular cross-sectional area A 1 .
  • a spiral-shaped guide surface 2 is arranged concentrically to the peripheral wall 1 within the peripheral wall 1. This guide surface 2 extends over an angle which is at least 360 °, but is greater than 360 ° in the illustration according to FIG. 1A. At the inner end of the spiral guide surface 2, a passage area 7 is thus formed which has the cross-sectional area A 2 .
  • FIGS. 1A and 1B which serve to explain the basic principle, a spiral guide surface is arranged within the peripheral wall 1. However, this is not necessary if an opening is provided in at least one of the side walls 11, 12 through which the fluid flowing in a vortex shape can escape in the axial direction while maintaining its vortex flow.
  • an elongated core with a circular cross-section is arranged in the chamber, which extends through an opening with the formation of an annular gap in one of the side walls, then the flow circulating near the circumference of the elongated core can escape through the annular gap, whereby its vortex movement in the essentially bites.
  • a cylindrical flow channel adjoins the passage opening and has the same diameter as the passage opening, the fluid flows through this flow channel over a long distance while maintaining its vortex movement. Over time, the fluid velocity of the fluid flow decreases due to the friction and a normal axial fluid flow arises. If the flow channel then widens to the passage opening in the side wall, it acts Extension as a diffuser, so that an increasing pressure increase of the fluid takes place in the axial direction of the diffuser.
  • the elongated core can advantageously also have a continuous, inner flow channel which runs in the axial direction and which opens out at the end remote from the annular gap to the outside of the chamber.
  • a negative pressure is generated at the opening of the inner flow channel of the core, so that a fluid can be sucked in through the inner flow channel.
  • the fluid entering the chamber and exiting in a spiral through the annular gap would be a propellant fluid. Because of the spiral flow of the propellant fluid passing through the annular gap, the propellant jet flows continuously without fluttering, so that this arrangement is highly efficient.
  • the chamber which extends transversely to the axis of the chamber Actuator provided, which at least comes close to the inner surface of the peripheral wall.
  • the peripheral surface of the actuator can also be in contact with the inner wall of the peripheral wall or sealing means can be provided between the peripheral wall of the actuator and the inner surface of the peripheral wall of the chamber.
  • This actuator can preferably be moved along the chamber axis, so that the chamber can be divided into two rooms. Assume that the actuator is located in the median plane of the chamber. If fluid flows into the chamber, a spiral flow can only arise in the region of the chamber which is delimited by the actuator and the side wall having the passage opening, since only here can fluid escape through the annular gap. Fluid is also in the other part of the chamber, since fluid from the tangential flow region can continue to enter this part of the chamber through the passage area. However, this fluid remains "stationary" and has a pressure as it is in the passage area.
  • Actuator is very close to the side wall through which the elongated core extends to form an annular gap, the friction losses on the side wall and the surface of the actuator can be so great that the formation of a spiral eddy flow of the Fluids is severely hindered or even prevented.
  • flow conditions would exist, as is the case with the known, for example poppet valves, in which uncontrollable vortices form in the passage gap.
  • the friction forces mentioned do not prevent the formation of a spiral flow, a uniform flow is maintained, and since no uncontrollable eddies are formed, no disturbing noises occur.
  • the elongated core can be arranged in a stationary manner and the actuator can be displaceable relative to the core. But it is also possible to firmly connect the actuator to the core and to arrange the elongate core slidably. These two possibilities can also be used in the context of the invention if the elongate core has a continuous, inner flow channel. Care must be taken, however, that when the actuator is fixedly connected to the elongated core, the core is sufficiently long that it extends through the chamber from one side wall to the opposite regardless of its position of displacement. This prevents fluid in the chamber from entering the inner flow channel of the elongated core.
  • the elongated core can also be designed as a hollow cylinder which extends through the passage opening and with its outer surface touches the inner peripheral surface of the passage opening.
  • the end of the hollow cylindrical core protruding beyond the passage opening is closed.
  • a cone preferably adjoins, which tapers away from the elongated core.
  • the hollow cylindrical core is open to the chamber, fluid which flows in the shape of a vortex can enter the core while maintaining its vortex flow and can exit the core through the regions of the slots which are located outside the passage opening.
  • the longitudinal surfaces of the slots through which the fluid flows should be designed in such a way that the lowest possible flow losses occur.
  • these inflow surfaces of the slots can be flat and beveled, or they can also be provided with a streamlined profile.
  • the elongated core has a conically tapering end section at its downstream end in order to achieve favorable flow conditions.
  • the invention also encompasses that the entire elongated core tapers toward its downstream end. This has the consequence that when the elongate core is displaced in the direction of its longitudinal axis, the passage area of the annular gap can be changed as a function of the displacement position of the elongate core.
  • the invention it is also possible to connect at least two of the devices according to the invention to one another in terms of flow.
  • One possibility is to provide two chambers, the lateral passage openings of which are connected to one another via a circular cylindrical piece of pipe.
  • a common core extends through the two chambers and the connecting tube.
  • the device acts as a diffuser and the outflow device acts as a confuser.
  • fluid with low flow rate and high pressure is converted into fluid with high flow rate and low pressure and then into fluid with low flow rate and high pressure.
  • an axial, elongated core can be rotatably arranged, on which guide elements extending in the radial direction are attached, which extend as close as possible to the spiral guide surface 2 (FIG. 1A).
  • An axial opening through which a fluid can enter is provided in at least one of the side walls.
  • the guide elements extending in the radial direction from the elongated core can be designed such that their radial extent depends on the angle of rotation of the rotatable, elongated core. It can thereby be achieved according to the invention that the guide elements with their ends remote from the axis are as close as possible or preferably in contact with the inner surface of the spiral guide surface over the largest angular range of their circumferential rotation. In this way, an effective fluid movement or fluid delivery is achieved.
  • the scope of the invention strived to obtain a spiral potential vortex within the respective chamber. Because of the validity of the continuity equation, the amount of fluid flowing into the chamber per unit of time is equal to that per unit of time. the amount of fluid flowing out of the fluid chamber. Furthermore, the flow velocity of the fluid in the various layers of the spiral potential vortex depends on the shape of the side walls. If, for example, the side walls of the chamber approach each other towards the chamber axis, the area of a fictitious passage gap is reduced if its height remains unchanged in the radial direction. As a result, there is also a change in the fluid flow rate.
  • an actuator is provided in the chamber, it can also be designed in accordance with an inclined side wall.
  • 1A and 1B is a schematic representation of a device according to the invention for explaining the basic idea of the invention
  • 2A is a longitudinal sectional view of a first embodiment according to the invention
  • Figure 2B. 3 shows a sectional illustration along the line II-II in FIG. 2A
  • FIG. 3A shows a second embodiment of a device according to the invention
  • FIG. 3B is a sectional view taken along the line III-III in Fig. 3A,
  • FIG. 6A shows a fifth embodiment according to the invention
  • FIG. 6B is a sectional view taken along the line VI-VI in Fig. 6A,
  • FIG. 7B is a sectional view taken along the line VII-VII in Fig. 7A,
  • a chamber 10 is defined by the inner peripheral wall 1, which runs along a spiral arch, and by side walls 11 and 12, which are perpendicular to the
  • An inlet channel 3 opens tangentially into the chamber 10 and is delimited by walls 4 and 5 running parallel to the chamber axis and by side walls (not shown).
  • the tangential inlet channel 3 opens into the chamber 10 at a first passage area 6.
  • the passage area 6 has a surface A 1 and has a rectangular cross section.
  • the side walls 4 and 5 of the inlet duct 3 merge tangentially into the end sections of the peripheral wall 1.
  • the side wall 12 is formed with a circular passage opening 8.
  • An elongated core 13 is arranged concentrically to the chamber axis in the chamber 10 and extends through the side wall 12 of the chamber 10 to form an annular gap with the cross-sectional area A 2 .
  • the core 13 has a circular cylindrical section 14 and an adjoining, conically tapering section 15.
  • a plate-shaped actuator is attached, which extends perpendicular to the chamber axis and is located with its peripheral surface in the immediate vicinity of the inner surface of the peripheral wall 1.
  • the peripheral surface of the actuator 16 can also touch the inner surface of the peripheral wall 1 or sealing means can also be provided between the peripheral surface of the actuator 16 and the peripheral wall 1.
  • peripheral wall 1 extends along a spiral arc and the peripheral surface of the actuator 16 is in the immediate vicinity of the peripheral wall 1 or touches it, means should be provided to prevent the core 13 from rotating. If such means are not provided, there is a risk that when the core 13 rotates, the peripheral surface of the actuator 16 is jammed with the peripheral wall 1.
  • an opening 18 through which a rod 17 extends, which is attached at one end to the actuator 16 or to the core 13 itself.
  • An unspecified sealing device such as an O-ring, is between the
  • the rod 17 serves to enable an axial displacement of the core 13 and of the actuator 16 attached to it.
  • a flow channel 19 adjoins the passage opening 8, which has a conically widening section 12 which adjoins the side wall 12 and which is adjoined by a cylindrical tube 21 with a constant cross section.
  • the width of the inlet-side passage area extends essentially over the entire width of the chamber, but space is provided on both sides of the inlet-side passage area for receiving the actuator 16 in its respective end positions.
  • the plate-shaped actuator 16 In the position of the core 13 and the actuator 16 shown in FIG. 2A, the plate-shaped actuator 16 has a position in which the actuator 16 divides the passage region 6 on the inlet side into two sections.
  • a fluid now flows through the tangential inlet channel 3, it reaches the part of the chamber 10 delimited by the actuator 16 and the side wall 11 on the one hand and the part of the chamber 10 delimited by the actuator 16 and the side wall 12 on the other hand 2A, the chamber 10 is divided into a small partial space and a large partial space on the side of the passage opening 8.
  • both subspaces of the chamber fill. Since fluid can escape through the annular gap between the cylindrical section 14 of the core 13 and the inner wall of the passage opening 8, a vortex-shaped flow in the form of a spiral fluid potential vortex is created in the larger part of the chamber.
  • Chamber 10 has no flow since there is no outlet opening. After formation of the spiral fluid potential vortex, a corresponding spiral fluid flow arises in the larger subspace of the chamber 10, the flow speed of which at the circumferential area of the cylindrical portion 14 is largest.
  • the fluid flow circulating in the immediate vicinity of the circumferential surface of the cylindrical section 14 of the core 13 emerges from the chamber while maintaining its rotational movement through the annular gap and reaches the conically widening tube section 20 as an axially shifting rotational flow. Since the elongated core 13 has a conically tapering end section 15, no uncontrolled vortices occur, but the fluid flows along a spiral in the axial direction. Because the pipe section
  • the cross-sectional area of the inlet-side passage area can be changed, that is to say, the inlet-side passage area into the part of the chamber 10 which is delimited by the side wall 12 and the actuator 16. If the area of this inlet-side passage area is reduced, only a smaller amount of fluid can enter the chamber 10 per unit of time. By moving the core 13, the amount of fluid passage can thus be changed. This also changes the pressure difference between the inlet-side fluid pressure and the outlet-side fluid pressure when it has been rebuilt by converting the kinetic energy of the fluid.
  • the characteristic curve which indicates the relationship between the flow rate per unit of time and the pressure difference between the inlet side and the outlet side, depends on the respective cross-sectional ratio between the area of the inlet-side passage area and the outlet-side passage area, i.e. the area of the annular gap.
  • the course of the characteristic curve mentioned can be influenced by changing this ratio.
  • a conical section which tapers in the direction of the passage opening 8 and to which the conical section 15 adjoins, or the entire section, can be used
  • Core 13 can be designed to taper conically. If such a configuration of the core 13 is present, the area of the annular gap changes as a function of the displacement position of the core 13. The smaller the distance between the actuator 16 and the side wall 12, the smaller the cross-sectional area of the annular gap.
  • Fig. 3A shows a second embodiment in partial longitudinal section
  • Fig. 3B shows a cross section along the line III-III in Fig. 3A.
  • the elongated core 13 has a cylindrical section and is formed with an inner flow channel 25 which extends in the longitudinal direction of the elongated core 13.
  • the core 13 also extends through an axial opening 26 formed in the side wall 11.
  • the core is by means of a sealing device, such as an O-ring 13 sealingly guided in this opening 26.
  • a cylindrical tube piece 19 adjoins the side wall 12 of the chamber 10 and has the same inner diameter as the passage opening 8 in the side wall 12.
  • the core 13 can be moved axially, whereby the length of the end section with which the
  • Core 13 extends into the tube 19, an annular gap always being formed between the outer surface of the end section of the core 13 and the inner wall of the passage opening 8.
  • An actuator 16 is also provided here, which is designed in the same way as in the first embodiment and has the same function.
  • a spiral potential flow is formed, as in the first embodiment, the flow layer close to the core of which has a high flow velocity.
  • This flow layer can flow in the axial direction while maintaining its rotational movement through the annular gap into the tube 19.
  • a vacuum is created in the tube 19, so that a vacuum is present at the opening of the inner flow channel 25, which is not shown, which is remote from the chamber, so that it is remote from the chamber
  • Opening the inner flow channel 25 a fluid can be sucked. This gives the effect of a jet pump.
  • the third embodiment according to the invention shown in FIG. 4 differs from that in FIG. 3A in that a further elongate core 30 is provided, which has a central cylindrical section
  • the cylindrical portion 31 has and has a circular cross-sectional area
  • the further elongated core 30 extends with its one end section 32 and a section of its cylindrical section 31 into the inner one.
  • the volume flow ratio between the driving jet and the suction jet can be influenced by selecting the size of the annular gap area.
  • the difference between the mode of operation of the second embodiment according to FIGS. 3A and 3B and the third embodiment according to FIG. 4 essentially consists in the fact that due to the rotary movement of the fluid passing through the annular gap, the fluid entering through the inner flow channel 25 also has an opening area Rotational movement is imposed, in which the further elongated core 30 extends. 4, the flow course of the fluid flowing through the chamber 10 is shown by a solid, spiral line. The spiral, broken line is intended to indicate the flow pattern of the fluid entering through the inner flow channel 25. It is advantageously achieved that the fluid flowing out of the annular gap and the fluid flowing out of the inner flow channel 25 into the tube 19 mix quickly with one another due to the common rotational movement.
  • FIG. 5 shows a fourth embodiment, which differs from the third embodiment according to FIG. 4 essentially in that the core 13 is stationary and cannot be displaced, that a conically widening tube section 35 connects to the cylindrical tube 19, and that the downstream end section 33 of the further elongated core 30 is formed with guide elements 36.
  • the mode of operation is the same as in the third embodiment.
  • the flared tube section 35 which connects to the cylindrical tube 19, acts as a diffuser, thereby reducing the flow rate of the fluid flow.
  • the guide elements 36 which the cone-shaped end section 33 has, serve to deflect the rotational flow movement of the fluid in such a way that an exclusive as quickly as possible axial flow is achieved. As a result, considerable pressure build-up is obtained even at a short distance from the conically widening tube section 35, and there is therefore only a slight or no rotational movement of the flow.
  • the embodiment shown in FIG. 5 can, for example, be used as a mixing device for two fluids.
  • FIG. 6A and 6B show a fifth embodiment of the invention.
  • This fifth embodiment differs from the fourth embodiment according to FIG. 5 in that, instead of a conically widening tube section 35, a device 40 is connected to the cylindrical tube 19, which also has a chamber 10, which has side walls 11 and 12 and a spiral peripheral wall 1 is limited. An outlet channel 3 also opens tangentially into this chamber 10.
  • the downstream end of the tube 19 is connected directly to the chamber 10, ie a corresponding passage opening is provided in the side wall 11.
  • a hollow cylinder 40 is arranged axially concentrically in the chamber 10. Passage slots 41 extending parallel to the cylinder axis are formed in the jacket of the hollow cylinder 40. 6A, the downstream end portion of the further elongated core 30 does not taper, but retains its cylindrical shape like the cylindrical portion 31.
  • a fluid flowing through the left chamber in FIG. 6A undergoes a spiral flow movement in this chamber 10 and occurs while being maintained the rotational movement through the annular gap into the tube 19.
  • Through the inner flow Fluid 25 drawn through channel 25 also flows spirally through tube 19, namely both fluids flow together spirally around cylindrical portion 31 and move axially to the right in FIG.
  • the axially extending surfaces of the passage slots 41 are shaped so that the lowest possible flow resistance occurs for the passage of the fluid.
  • FIG. 7A and 7B show a longitudinal sectional view and cross-sectional view of a sixth embodiment according to the invention.
  • a chamber 10 is also provided here, which is delimited by a peripheral wall 1 and side walls 11, 12 running along a spiral arch.
  • An opening 8 is formed in the side wall 12.
  • Connected to the side wall 12 in the region of the opening 8 is a pipe section 19 which has a larger diameter than that Has opening 8.
  • a core 13 has a hollow cylindrical section 44, to which a preferably conically tapering section 46 connects downstream. At the connection point between the hollow cylindrical section 44 and the conical section 46, the hollow cylindrical section 44 is closed.
  • a rod 17 is attached centrally, which extends through the hollow cylindrical section 44 and through an opening (not shown) in the side wall 11 to the outside of the chamber 10.
  • the rod 17 is sealingly guided in the opening of the side wall 12, not shown.
  • the outer diameter of the hollow cylindrical section 44 is chosen to be so large that the peripheral surface of the hollow cylindrical section 44 lies essentially sealingly on the inner surface of the opening 8.
  • a sealing device can also be provided in order to achieve a reliable seal.
  • Passage slots 45 extending in the axial direction are formed in the jacket of the hollow cylindrical section 44.
  • the conical section 46 of the core 13 supports a uniform flow, so that the occurrence of undesirable turbulence is hindered. Since the fluid enters the tube 19 with a rotational movement component, it continues to flow in a spiral in this tube until the rotational flow component becomes smaller and smaller over time, so that an axial fluid flow finally occurs.
  • the axially extending surfaces of the passage slots 45 are preferably shaped so that no losses occur, i.e. these surfaces are adapted to the fluid flow.
  • the seventh embodiment shown in FIG. 8 is an example of how various of the previously discussed embodiments combine with each other can be renated.
  • An elongated core 13 extends from the chamber 10 into the pipe section 19 '. This core 13 can be moved in the axial direction by means of the rod 17 protruding from the chamber 10.
  • the core 13 is formed with an inner flow channel 25, the axial opening of which is located in the chamber 10 is closed.
  • the end portion of the core 13 facing the chamber 10 is formed with axial through slots 47.
  • an actuator 16 which extends from the circumferential surface of the core 13 to the circumferential wall 1' of the chamber 10 'and is designed in a manner corresponding to the actuators 16 already described in connection with the other embodiments.
  • This actuator 16 in the chamber 10 ' also has the same function as the actuators already described.
  • the core 13 is sealingly guided in the side wall 11 'of the chamber 10' and a seal 49 is provided for sealing.
  • the inside diameter of the pipe section 19 is only slightly larger than the outside diameter of the elongated core 13.
  • the inside diameter of the pipe section 19 ' is somewhat larger than the outside diameter of the core 13, which overall has the shape of a hollow cylinder, so that in the area of the pipe section 19' Ring channel is formed. If a fluid flows through the chamber 1, which enters the chamber 10 through the associated tangential flow channel 3, a spiral fluid flow arises which also at least partially flows around the end section of the core 13 projecting into the chamber 10 and thereby through the the area of the passage slots 47 located in the chamber 1 reaches the inner flow channel 25 of the elongated core 13. The fluid flow is spiral-shaped inside the flow channel 25, as is indicated by the broken lines. Through the open, conically widening end at 27, the fluid flow arrives from the interior of the flow channel 25 into the pipe section 19 '.
  • the embodiment according to FIG. 8 can be used for mixing two fluids or as a jet pump.
  • the fluids flow into the chambers 10 and 10 'each under the action of a positive pressure.
  • the fluid flows into the chamber 10 'under a positive pressure and in the region of the pipe section 19' a negative pressure is created which propagates through the inner flow channel 25, the through-slots 47, the chamber 10 up to the tangential flow channel 3.
  • a fluid can be sucked in through the tangential flow channel 3, which reaches the pipe section 19 ′ at the open end of the inner flow channel 25.
  • both fluids have a spiral flow in the tube section 19 '.
  • the toroidally widening tube section 48 acts as a diffuser, so that the rotational component of the flow becomes smaller, and an axial flow is established over time.
  • the length of the passage slits 47 is chosen such that the Dur ⁇ h ' slits 47 extend in the longitudinal direction substantially over the entire width of the chamber 10 when the elongated core 13 is shifted all the way to the left in FIG. 8.
  • Fig. 9 shows an eighth embodiment in which two "basic forms" of the invention are interconnected. As can be seen from FIG. 9, the two chambers 10 and 10 ′ are connected to one another via a cylindrical tube section 19. Along the longitudinal axis of the two
  • Chambers extends a core 13 slidably arranged in the longitudinal direction, which has an actuator 16 at the end located in the chamber 10.
  • the actuator 16 is followed by a rod 17, which is fixedly connected to the elongated core 13 and protrudes outwards through the chamber 10 through an opening in the side wall 11, which opening is not specified.
  • the core 13 extends with the end section opposite the actuator 16 in a circular, closed continuation of the side wall 12 '. This continuation and the unspecified opening in the side wall 11 of the chamber 10 serve to guide the core 13 . and its shift.
  • the rod 17 is sealed off from the side wall 11.
  • the inside diameter of the pipe section 19 is considerably larger than the outer diameter of the cylindrical core 13.
  • a fluid flowing into the chamber 10 through the tangential flow channel 3 forms a spiral flow vortex in this chamber 10, the fluid flowing around the outer surface of the elongated core 13 several times.
  • the fluid flow circulating around the core 13 moves in the axial direction through the pipe section
  • FIG. 9 can be compared with the mode of operation of a Venturi nozzle, because fluid entering the chamber 10 under higher pressure at low speed reaches a high flow rate at low pressure within the pipe section 19, and this becomes a high fluid flow rate reduced in the chamber 10 ', again, a pressure is built up in the tangential flow channel 3'.
  • the flow rate through the entire device can be set due to the mode of operation of the actuator 16, as has already been discussed above. If the chambers 10 and 10 'are identical, the same conditions as with a Venturi nozzle are obtained without the actuator 16 but with the core 13, or with the chamber 10 fully open.
  • the use of a fluid potential vortex according to the invention in connection with devices has been described in which the elongated core was stationary or movable.
  • the invention also encompasses devices in which a rotatably arranged core is provided which is arranged in a chamber with a peripheral wall which extends along an arc or spiral arc.
  • the choice of the type of curvature of the peripheral wall depends on the flow conditions in the transition region between the peripheral wall and the flow channel opening tangentially into the chamber. In this regard, it is important how much the flow velocity has changed after one revolution along the peripheral wall. In other words, it has to be taken into account whether or not two flow layers that come into contact with one another in the transition region between the tangential flow channel and the chamber have a greater speed difference.
  • FIG. 10 shows a schematic representation of a cross section of a device according to the invention with a rotatably arranged core 60.
  • a peripheral wall 1 delimiting the chamber 10 runs along a spiral arch.
  • a flow channel 3 connects tangentially to this peripheral wall 1.
  • the transition area between the interior of the chamber 10 and the connection end of the flow channel 3 is designated by 6.
  • a spiral-shaped guide surface 2 is arranged in a stationary manner within the peripheral wall 1, so that the chamber 10 is divided into an interior and an annular space, the latter being delimited by the peripheral wall 1 and the spiral-shaped guide surface 2.
  • Side walls which cannot be seen in FIG. 10 are provided, so that a housing is formed overall.
  • An elongated core 60 is rotatably mounted in the interior of the chamber 10. From the core 60 extend radially outward.
  • the radial extension of the guide elements 61 is selected so that a free rotation of the core 60 about its longitudinal axis is possible.
  • the rotatable core 60 is rotatably mounted in a bearing device which is fastened to at least one of the side walls, not shown. Furthermore, there is a passage opening in at least one of the side walls, so that the interior space of the chamber 10 located within the spiral guide surface 2 has a flow connection to the outside of the device.
  • the device according to FIG. 10 is filled with a liquid. Furthermore, the passage opening in at least one of the side walls is to be connected in terms of flow to a liquid supply, and the rotatable core 60 is to be connected in terms of drive to a drive device, such as a motor (not shown).
  • a drive device such as a motor (not shown).
  • the liquid located in the interior of the chamber 10 is set in rotation and passes through the passage area 7, which is delimited in the radial direction by the end sections of the spiral guide surface 2, into the annular space of the chamber 10 already mentioned, forming in this annular space a spiral-shaped liquid flow arises, and the liquid layer flowing along the peripheral wall 1 passes through the passage area 6 into the tangential flow channel 3 and from there to the outside. Since liquid is conveyed into the annular space from the interior, a negative pressure is created in the interior, so that liquid is sucked out of the liquid supply through the passage opening which is in flow communication with the interior in at least one of the side walls.
  • the size of the pressure built up in the tangential flow channel 3 depends, inter alia. on the speed of the core 60 and thus on the rate of entry of the liquid into the passage area 7, and on the radial dimension of the peripheral wall 1. Furthermore, the cross-sectional area of the passage area 6 also plays a role, because because of the continuity equation, the amount of liquid flowing through the passage areas 6 and 7 per unit of time must be the same. The passage amount in turn depends on the respective flow velocity in these areas.
  • the guide elements 61 can also be designed within the scope of the invention in such a way that their radial extension depends on the rotational position of the core 60 changes.
  • the device according to the invention with a rotatable core according to FIG. 10 has very low losses during its operation, since favorable flow conditions result.
  • a rotatable core 50 is arranged in a chamber 10 delimited by an arcuate or spiral arcuate peripheral wall 1.
  • a flow channel 3 opens tangentially into the chamber 10, the passage area from the flow channel 3 into the chamber 10 being designated by 6. 11, which cannot be seen from a radial section, are provided which, together with the peripheral wall 1, form a housing.
  • a rotatable core, generally indicated at 56 Arranged in chamber 10 is a rotatable core, generally indicated at 56, which has a rotating shaft 50 which extends through at least one of the side walls. 11, the core 56 has two curved guide elements 57 and 57 '.
  • the two guide elements 57 and 57 ' have concave outer cylindrical surfaces 54 and 54', the geometric location of the generatrix of these cylindrical surfaces 54 and 54 'being a spiral arc.
  • the ends 51 and 52 of the outer surface 54 and the inner surface 58 of the guide element 57 are connected to one another via an inflow surface 53, which is curved into the space delimited by the outer surface 54 and the inner surface 58.
  • the inflow surface 53 is also a cylindrical surface. In this example, the geometrical location of the generatrix of this inflow surface 53 is a semicircle.
  • the outer surface 54 and the inner surface 58 are connected to one another via an arcuate cylindrical surface.
  • the guide element 57 ' is designed in the same way as the guide element 57, so that the preceding description also applies to the outer surface 54', the inner surface 58 ', the ends 51' and 52 'of these surfaces, the inflow surface 53' and the end region 55 '. of the guide element 57 'applies.
  • the core 56 having the guide elements 57 and 57 ' is rotatably mounted.
  • a passage opening preferably a passage opening concentric with the axis of rotation of the core 56, is provided in the side walls (not shown).
  • the operation of the device according to the invention will now be described in the case where the fluid is a liquid.
  • chamber 10 is filled with a liquid.
  • Further liquid should now flow into the chamber through the tangential flow channel 3.
  • This inflowing liquid passes through the passage area 6 into the interior of the chamber 10, and a spiral flow is formed in the chamber 10 which, as provided in the context of the invention, has the shape of a spiral liquid potential vortex.
  • the spiral fluid potential vortex rotates in the clockwise direction.
  • the reference numeral 60 denotes a section of a spiral flow path which is already very close to the rotatable core 56.
  • this flow path 60 is divided at the radially outer connecting edge between the inflow surface 53 and the outer surface 54 of the guide element 57 into a proportion which is between the connecting edge 51 of the inflow surface 53 and the outer surface 54 and the end region 55 'of the guide element 57' and is deflected towards the interior of the core 56 by the inflow surface 53.
  • the other portion of the flow path 60 continues to flow on the outer surface 54 of the guide element 57 and finally reaches the passage area which is delimited by the connecting edge 51 'between the outer surface 54' and the inflow surface 53 'of the guide element 57' and the end region 55 of the guide element 57 is.
  • the liquid flowing through this area strikes the inflow surface 53 ′ and is deflected by this toward the interior of the core 56.
  • the liquid deflected into the interior of the core 56 can reach the outside of the chamber 10 through the passage opening already mentioned into one of the side walls.
  • the outer surfaces 54 and 54 'of the guide elements 57 and 57' are curved such that the curvature has essentially the same course as that of the flow paths adjacent to the outer surfaces 54 and 54 '.
  • the passage areas through which the liquid enters the interior of the core 56 are to be dimensioned in this way. that their cross-sectional areas are adapted to the cross-sectional area of the passage area between the tangential flow channel 3 and the interior of the chamber 10.
  • the flow velocity of the liquid plays a role in the respective passage area, because the liquid volume flowing through the passage area 6 is equal to the amount of liquid flowing through the passage areas between the ends of the guide elements 57 and 57 '.
  • two guide elements 57 and 57 ' are provided, the respective inflow surfaces 53 and 53' of which are acted upon by liquid, so that the core 56 is set in rotation.
  • more than two guide elements can also be provided, the passage areas between the respective ends of the. Guiding elements with regard to their cross-sectional areas and the existing ones
  • Flow velocities should be designed in such a way that the conditions resulting from the continuity equation are fulfilled as well as possible.
  • the fact that a spiral liquid potential vortex is provided with a plurality of revolutions and the outer surfaces of the guide elements are designed in accordance with the spiral flow paths ensures that the inflow surfaces are continuously exposed to the fluid. As a result, there are extremely low vibrations and losses and the risk of cavitation is extremely low.
  • the device according to the invention described above can also be operated so that the rotatable Core 56 is driven by a drive device, wherein the direction of rotation is then reversed, ie the rotatable core 56 then rotates counterclockwise.
  • the device acts like a conveying device for a fluid which axially enters the interior of the core through the passage opening provided in at least one of the side walls and is conveyed through the contact surfaces of the guide elements into the chamber surrounding the core, in which then results in a spiral fluid potential vortex.
  • the fluid or the liquid enters the tangential flow channel at the periphery of the chamber.
  • a rotating, spiral-shaped fluid potential vortex is generated in a chamber with a circular-arc-shaped or spiral-arc-shaped circumferential wall, such that the fluid rotates several times around the axis of the chamber as it flows through the chamber.
  • Flow velocity of the fluid and n mean a constant, for which 0 ⁇ n ⁇ gilt applies.
  • n is greater than or equal to 1. The value for n depends on the intended purpose for which a device according to the invention is to be used.
  • the devices according to the invention can be operated or used with liquid, gaseous and vaporous fluids. It is also noted that with the invention Devices, the pipe flow resistance in the pipe adjoining a device according to the invention, in which the fluid moves in a spiral, can be reduced. In other words, this means that, compared to a purely axial flow, a flow spiraling in the axial direction has less friction loss, so that along the pipe section in which the flow still has a rotating component, less energy, which the fluid contains, of the fluid is released.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Cyclones (AREA)

Abstract

Un dispositif de transformation de l'écoulement d'un fluide comprend une chambre avec deux parois latérales et une paroi périphérique circulaire ou en spirale s'étendant entre les parois latérales. Un canal d'écoulement s'ouvre dans la chambre tangentiellement à la paroi périphérique. Un noyau allongé à section transversale circulaire est agencé axialement dans la chambre et s'étend dans une ouverture d'une paroi latérale en formant une fente annulaire. Pour n'importe quels deux points de l'écoulement du fluide à l'intérieur de la chambre, la condition w1r1n = w2r2n doit être essentiellement remplie, ri étant l'écart radial entre le point P1 de l'arc de cercle ou de spirale décrit par la paroi périphérique, wi étant la vitesse d'écoulement du fluide au point P1 et n une constante définie par 0 < n < . Ce dispositif permet de transformer un écoulement axial de fluide en un écoulement de fluide se déplaçant en spirale dans le sens axial, ou vice-versa. L'invention décrit diverses possibilités d'application de ce dispositif.
EP86903364A 1985-06-04 1986-06-04 Dispositif de transformation de l'ecoulement d'un fluide Withdrawn EP0224527A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853520032 DE3520032A1 (de) 1985-06-04 1985-06-04 Vorrichtung zum umwandeln einer fluidstroemung
DE3520032 1985-06-04

Publications (1)

Publication Number Publication Date
EP0224527A1 true EP0224527A1 (fr) 1987-06-10

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EP86903364A Withdrawn EP0224527A1 (fr) 1985-06-04 1986-06-04 Dispositif de transformation de l'ecoulement d'un fluide

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Country Link
US (1) US4824449A (fr)
EP (1) EP0224527A1 (fr)
DE (1) DE3520032A1 (fr)
WO (1) WO1986007417A1 (fr)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2055429C (fr) * 1989-05-12 1993-07-20 John T. Tang Reacteur a effet vortex a etages multiples
DK7291D0 (da) * 1990-09-11 1991-01-15 Joergen Mosbaek Johannesen Stroemningsregulator
US5207805A (en) * 1991-01-11 1993-05-04 Emtrol Corporation Cyclone separator system
KR100308432B1 (ko) * 1992-12-23 2002-07-06 데이비드 에스. 호이리스 휴대용실내공기정화기
DE4335595A1 (de) * 1993-10-19 1995-04-20 Robert Dipl Ing Freimann Verfahren und Vorrichtung für eine unter Druck stehende, umzulenkende oder zu verzweigende Rohrströmung
DE59502286D1 (de) * 1994-12-21 1998-06-25 Siemens Ag Vorrichtung zur begrenzung des volumenstroms eines unter druck stehenden fluides
US6024874A (en) * 1998-11-03 2000-02-15 Lott; W. Gerald Hydrocyclone separator
JP4710420B2 (ja) * 2005-05-31 2011-06-29 セイコーエプソン株式会社 液体流通装置及び液体噴射装置
WO2011130259A1 (fr) 2010-04-12 2011-10-20 Saudi Arabian Oil Company Appareil de séparation de mélanges gaz-liquide et favorisant coalescence de liquides
US8757667B2 (en) 2010-07-16 2014-06-24 Ipex Technologies Inc. Adapters and connector assemblies for flow managing apparatuses
CA2714675C (fr) 2010-07-16 2017-05-09 Ipex Technologies Inc. Ensembles de connecteurs pour dispositifs limiteurs de debit
US8876961B2 (en) 2012-02-21 2014-11-04 Mann+Hummel Gmbh Particle separator with deflector and lateral opening and air filter system
KR102071655B1 (ko) 2012-03-20 2020-01-30 사우디 아라비안 오일 컴퍼니 통합적인 증기-액체 분리가 있는 스팀 촉매 크래킹 방법 및 시스템
US11446660B2 (en) 2012-06-18 2022-09-20 Scanlogx, Inc Organism evaluation system and method of use
EP2861753B1 (fr) * 2012-06-18 2021-11-03 SoBru Solutions, Inc. Système d'évaluation de microorganisme
US10748278B2 (en) 2012-06-18 2020-08-18 Sobru Solutions, Inc. Organism evaluation system and method of use
CN107237396B (zh) * 2017-06-03 2022-10-04 水利部产品质量标准研究所 带有空气储存区的蜗形滞流器
CN107162101B (zh) * 2017-07-14 2023-06-30 核工业理化工程研究院 一种基于文丘里管的大通量水力空化发生器以及空化方法
ES2939761T3 (es) * 2018-12-21 2023-04-26 Nat Univ Ireland Galway Aparato generador de vórtice

Family Cites Families (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US450372A (en) * 1891-04-14 Orville m
US658832A (en) * 1899-03-13 1900-10-02 Roger Danvin Dust-collector.
US837705A (en) * 1906-03-06 1906-12-04 Orville M Morse Separator.
US1045532A (en) * 1911-06-08 1912-11-26 Julius A Dyblie Dust-catcher.
US1915678A (en) * 1930-07-25 1933-06-27 Bour Harry E La Pump
BE406007A (fr) * 1933-08-10
US2187646A (en) * 1935-08-16 1940-01-16 Bbc Brown Boveri & Cie Separator
GB555908A (en) * 1942-02-09 1943-09-13 Davidson & Co Ltd Dust collector and separator
FR1005450A (fr) * 1947-07-22 1952-04-10 Procédé et dispositif pour la pulvérisation de tous liquides et le fibrage de matières thermoplastiques
FR1069071A (fr) * 1952-10-27 1954-07-05 Airmeca Perfectionnements aux capteurs de particules contenues dans des fluides
US2888096A (en) * 1955-06-22 1959-05-26 Shell Dev Horizontal centrifugal separator
DE1128808B (de) * 1957-11-21 1962-04-26 Simon Ltd Henry Pneumatische Foerderanlage
US3064411A (en) * 1959-08-14 1962-11-20 Jr Joseph Breslove Separator
NL285619A (fr) * 1961-11-30
DE1248388B (de) * 1963-05-17 1967-08-24 R I V Anstalt Zur Verwaltung V Wirbelkammerstroemungsdrossel
DE1241207B (de) * 1963-03-26 1967-05-24 R I V Anstalt Zur Verwaltung V Wirbelkammer-Stroemungsdrossel
US3215165A (en) * 1963-05-27 1965-11-02 Cons Paper Bahamas Ltd Method and device for the control of fluid flow
US3282030A (en) * 1963-09-25 1966-11-01 Rotron Mfg Co Apparatus for fluid treatment
DE1279538B (de) * 1963-10-15 1968-10-03 Imp Tobacco Co Ltd Zentrifugalabscheider
US3426513A (en) * 1967-11-13 1969-02-11 Kurt Bauer Vehicular vortex cyclone type air and gas purifying device
DE2137128C3 (de) * 1971-07-24 1978-10-05 Siemens Ag, 1000 Berlin Und 8000 Muenchen Vorrichtung zur Drallerzeugung in einem Drehströmungswirbler
CH580442A5 (fr) * 1974-08-09 1976-10-15 Sulzer Ag
US3953184A (en) * 1974-09-18 1976-04-27 Stockford William F Cyclone-type dust separator
SU543427A2 (ru) * 1975-07-23 1977-01-25 Тюменский государственный научно-исследовательский и проектный институт природных газов Сепаратор
SU556839A2 (ru) * 1975-12-16 1977-05-05 Тюменское Специализированное Проектно-Конструкторское И Технологическое Бюро Объединения "Сибкомплектмонтаж" Сепаратор
DE2606673C2 (de) * 1976-02-19 1983-12-08 Klöckner-Humboldt-Deutz AG, 5000 Köln Vorrichtung zum Ausscheiden von Gasen aus Flüssigkeiten
DE2610031C3 (de) * 1976-03-10 1980-07-03 Messerschmitt-Boelkow-Blohm Gmbh, 8000 Muenchen Stofftrennung mittels auf das betreffende Medium einwirkender Fliehkräfte
DE2625422C3 (de) * 1976-06-05 1979-03-01 Messerschmitt-Boelkow-Blohm Gmbh, 8000 Muenchen Einrichtung zur Rückverwandlung von Drallströmungsenergie in Druckenergie
CA1082427A (fr) * 1977-09-01 1980-07-29 Hassan A. Hamza Appareil servant a melanger une poudre a un liquide, et methode connexe
DE2741243A1 (de) * 1977-09-14 1979-03-22 Werner Anliker Verfahren und vorrichtung zur durchmischung zweier medien
DE2743391A1 (de) * 1977-09-27 1979-03-29 Maschf Augsburg Nuernberg Ag Wirbelkammer zur trennung von gasgemischen
GB2055634B (en) * 1979-08-16 1983-01-26 Ishikawajima Harima Heavy Ind Gas-liquid separators
US4464314A (en) * 1980-01-02 1984-08-07 Surovikin Vitaly F Aerodynamic apparatus for mixing components of a fuel mixture
US4333499A (en) * 1980-04-15 1982-06-08 Conoco Inc. Pressure dissipation apparatus
DE3039510A1 (de) * 1980-10-20 1982-06-03 Hoechst Ag, 6000 Frankfurt Vorrichtung und verfahren zum dispergieren und loesen von polymerpulvern

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8607417A1 *

Also Published As

Publication number Publication date
US4824449A (en) 1989-04-25
DE3520032A1 (de) 1986-12-04
WO1986007417A1 (fr) 1986-12-18

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