EP0224527A1

EP0224527A1 - Device for transforming a fluid flow

Info

Publication number: EP0224527A1
Application number: EP86903364A
Authority: EP
Inventors: Istvan Majoros
Original assignee: Individual
Current assignee: Majoros Istvan
Priority date: 1985-06-04
Filing date: 1986-06-04
Publication date: 1987-06-10
Also published as: DE3520032A1; WO1986007417A1; US4824449A

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.A device for transforming the flow of a fluid comprises a chamber with two side walls and a circular or spiral peripheral wall extending between the side walls. A flow channel opens into the chamber tangentially to the peripheral wall. An elongated core of circular cross section is arranged axially in the chamber and extends into an opening in a side wall forming an annular slot. For any two points of the fluid flow inside the chamber, the condition w1r1n = w2r2n must be essentially fulfilled, ri being the radial deviation between the point P1 of the arc of a circle or of a spiral described by the peripheral wall, wi being the flow velocity of the fluid at point P1 and n a constant defined by 0 <n <. This device makes it possible to transform an axial flow of fluid into a flow of fluid moving in a spiral in the axial direction, or vice versa. The invention describes various possibilities of application of this device.

Description

Fluid flow converting device

Description

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.

This object is achieved by the in the Kenn Character of claim 1 specified features solved.

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.

The basic principle of the potential vortex will be explained using the schematic illustration in FIGS. 1A and 1B. In the case of a vortex with closed flow paths, rxw = const. is. Here r is the distance of a point from the vortex axis and w is the flow velocity of the fluid at this point. A spiral-shaped potential vortex is one in which essentially the condition r ₁ ⁿ xw ₁ = r ₂ ⁿ xw _{2 is} fulfilled. 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.

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 α. The angle α 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. Furthermore, it is assumed that 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 .

It is assumed that a fluid, in particular a liquid, enters the tangential flow channel and has the average speed w ₁ at the passage area 6. In the chamber forms between the spiral peripheral wall 1 and the spiral

Guide surface 2 from a spiral vortex flow which exits through the passage area 7 into the space which is limited by the inner surface of the spiral guide surface 2 and the two side walls 11 and 12 of the chamber. Of course, this space must have an outlet opening for the fluid. In the illustration according to FIG. 1A, the peripheral wall 1 runs along a spiral arch. It is thereby achieved that the fluid flow layer adjoining the peripheral wall 1 has, after a revolution of 360 °, essentially the same speed as the fluid flow layer which opens into the chamber at the inner end of the spiral peripheral wall 1. This results in no or almost no relative speed between the two fluid flow layers, so that no secondary vortex losses occur. When a fluid flows continuously through the chamber from the passage area 6 to the passage area 7, there is a spiral "wound" fluid flow band. There is essentially no relative speed between the individual layers of the flow band, so that essentially the friction between the fluid and the side walls 11 and 12 is the greatest loss factor.

In FIG. 1B, the distance of the upper edge of the passage area 6 from the axis of the spiral with R ₀ , the distance of the lower edge of the passage area 6 with R ₁ , the distance of the outer end of the spiral guide surface 2 with R ₂ and the distance of the designated R ' _{2 on the} inner end of the spiral guide surface,

In 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.

It should be noted that if the height of the passage area 6, which is equal to R ₀ minus R ₁ , has a relatively small value, a fluid flow in the form of a spiral potential vortex can be obtained if the circumferential wall 1 along an arc runs. Then there may be conditions such that the relative speed between the fluid flowing through the passage area 6 and the fluid which has essentially carried out a first, full circulation is relatively small, so that only slight flow or friction losses occur .

If 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. If 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. At the end of the elongated core, which extends into a flow channel adjoining the annular gap, 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. In this case, 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.

If according to an advantageous development of the invention in the inner flow channel of the elongated core, another elongated core, the end sections of which taper, preferably taper conically, so that one of the tapering end sections extends into the inner flow channel, this is experienced by the inner one Fluid flowing in the flow channel, at least in the end region of the inner flow channel, also has a spiral rotation, so that the propellant fluid and the fluid flowing out of the inner flow channel mix well with one another without additional energy-consuming vortex formation.

According to another development of the invention, there is one in 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.

Since there is still a spiral fluid flow in the part of the chamber connected to the annular gap, the fluid flows evenly through this part of the chamber.

It should be noted that if the

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. In this case flow conditions would exist, as is the case with the known, for example poppet valves, in which uncontrollable vortices form in the passage gap. However, if 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.

In the context of the invention, 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.

In the context of the invention, 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. There are elongated through slots in the cylinder jacket formed, which preferably extend parallel to the longitudinal axis of the elongated, hollow cylindrical core. At the closed end of the elongated core, a cone preferably adjoins, which tapers away from the elongated core.

Since in this embodiment according to the invention 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. In order to have favorable flow conditions, 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. For example, these inflow surfaces of the slots can be flat and beveled, or they can also be provided with a streamlined profile.

According to an advantageous development, 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.

If it is desired to have an essentially exclusively axial flow even at a short distance from the chamber, then in the flow chamber nal, in which the core extends, or at the downstream end of the core, preferably in its tapering section, guide elements are provided which deflect the vortex flow in the direction of an axial flow. Furthermore, if a pressure increase downstream of the chamber is to be obtained as quickly as possible, a diffuser can be provided.

In previous discussions, it was generally assumed that a fluid enters through the flow channel arranged tangentially to the chamber and exits through the annular gap. But it is also possible to reverse the direction of flow and a vortex-shaped

Feed the flow in the opposite direction from outside the chamber. This reverses the flow conditions previously discussed, i.e. In the chamber, a spiral vortex revolving in the opposite direction is then generated, the fluid then reducing its flow velocity to the peripheral wall of the chamber and finally exiting through the tangential flow channel under pressure build-up.

The extent to which the flow conditions are reversible depends of course on the goal sought.

According to 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. When a fluid enters the chamber through the tangential flow channel, it flows in it along a spiral potential vortex and exits in a spiral around the elongated core through the annular gap of the chamber. The fluid moves in the longitudinal direction of the core while maintaining its vortex flow and enters the other chamber through the annular gap. In this it flows along a spiral vortex of potential from the elongated core outwards to the peripheral wall of this other chamber and finally exits the chamber through the tangential flow channel. Of course, the tangential flow channel through which the fluid exits must be oriented in accordance with the vortex rotation in the chamber connected to it. With this described arrangement of two devices according to the invention, flow conditions are obtained which are comparable to a Venturi nozzle. The inflow side

The device acts as a diffuser and the outflow device acts as a confuser. In other words, 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.

According to an advantageous development, in an embodiment according to FIG. 1, which is used to explain the

The basic principle of the invention has already been discussed, in addition, 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. When the elongated core is rotated by a drive means such as a motor, fluid enclosed by the spiral baffle is also rotated and exits into the space through the passage area between the ends of the baffle is limited by the outer surface of the spiral guide surface and the peripheral wall. A vacuum is created at the opening provided on the axial side, so that further fluid can be drawn in there. A spiral fluid potential vortex is created in the space delimited by the spiral guide surface and the peripheral wall, and the fluid finally passes through the passage area delimited by the peripheral wall in the radial direction and flows out via the tangential flow channel. The flow conditions are therefore reversed to those indicated in FIG. 1A by the arrows designated w ₁ and w ₂ . Advantageously, 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 following is also pointed out:

As has already been discussed, 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.

These considerations must be taken into account when dimensioning the chamber, the elongated core and the flow passage areas.

If an actuator is provided in the chamber, it can also be designed in accordance with an inclined side wall.

The invention will now be explained in more detail using exemplary embodiments with reference to the drawing. It shows:

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,

3A shows a second embodiment of a device according to the invention,

3B is a sectional view taken along the line III-III in Fig. 3A,

4 shows a third embodiment according to the invention,

5 shows a fourth embodiment according to the invention,

6A shows a fifth embodiment according to the invention,

6B is a sectional view taken along the line VI-VI in Fig. 6A,

7A shows a sixth embodiment according to the invention,

7B is a sectional view taken along the line VII-VII in Fig. 7A,

8 shows a seventh embodiment according to the invention,

9 shows an eighth embodiment according to the invention,

10 shows a ninth embodiment according to the invention,

11 shows a tenth embodiment according to the invention, In the following description of the embodiments, the same parts are denoted by the same reference numerals.

2A and 2B show a first embodiment according to the invention. 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

Axis of the spiral peripheral wall 1 are limited. 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 . As shown in FIG. 2A, the core 13 has a circular cylindrical section 14 and an adjoining, conically tapering section 15. At the end of the cylindrical section 14 remote from the annular gap, 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. Since the 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.

In the side wall 11 there is 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

Inner surface of the opening 18 and the rod 17 are provided. The rod 17 serves to enable an axial displacement of the core 13 and of the actuator 16 attached to it.

Outside the chamber 10, 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 annular gap formed between the cylindrical section 14 and the passage opening 8 can be clearly seen in FIG. 2B.

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.

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.

If 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. When fluid flows into the chamber through the inlet-side flow channel 3, 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. In the smaller part of the

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

20 conically expanded, the rotational speed of the fluid flow changes accordingly. The flow then continues into the cylindrical tube section

21 while maintaining their rotational movement, which reduces the axial pipe flow resistance and whose speed decreases over time due to the pipe friction, so that an axial flow finally occurs.

By axially displacing the core 13 by means of the rod 17 from outside the chamber 10, 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. Thus, according to the invention, instead of a cylindrical section 14 of the core 13, a preferably 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, while Fig. 3B shows a cross section along the line III-III in Fig. 3A.

2A and 2B essentially differ in that 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. In this embodiment, 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.

If a fluid flows into the chamber 10 through the tangential flow channel 3, 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. As a result, 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.

By axially shifting the core 13 is also Actuator also moved so that, just as in the first embodiment, the amount of fluid flowing through the chamber 13 can be changed. This also changes the negative pressure at the opening of the inner flow channel 25 opening into the tube 19, with the result that the pumping speed is also changed. If one considers the fluid flowing through the chamber 10 as a driving fluid, the suction effect of the device can be changed by changing the amount of driving fluid flow.

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

31 and at these tapered end sections

32 and 33. The cylindrical portion 31 has and has a circular cross-sectional area

Diameter that the peripheral surface of the cylindrical portion 31 is spaced from the inner wall of the inner flow channel 25. As shown in FIG. 4, the further elongated core 30 extends with its one end section 32 and a section of its cylindrical section 31 into the inner one. Flow channel 25, and defines an annular gap for the suction jet. 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.

Apart from the fact that no actuator is provided in this fourth embodiment, and thus the amount of fluid flow through the chamber 10 cannot be changed, the mode of operation is the same as in the third embodiment. One difference, however, is that 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. Furthermore, 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.

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. 6A. The fluid flowing around the cylindrical section 31 passes. inside the hollow cylinder 40 while maintaining its rotational movement. Since the hollow cylinder 40 is formed with through-slots 41 running in the axial direction, the fluid can pass through these slots and into the chamber 10 on the right in FIG. 6A. In this chamber there is also a spiral fluid potential vortex, the outermost flow layer of which can pass through the passage area 6 from the chamber 10 into the tangential flow channel 3. Thus, since the flow velocity decreases with increasing radius, a pressure build-up results in the tangential flow channel 3.

Advantageously, 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.

7A and 7B show a longitudinal sectional view and cross-sectional view of a sixth embodiment according to the invention. As with the other embodiments, 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. At the end of section 44, which is closed by the base of section 46, 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.

7A and 7B are only those

Described parts that have not yet been mentioned in connection with the previous embodiments.

If a fluid flows through the chamber 10, which enters the chamber 10 through the tangential flow channel 3, a spiral circulation flow also arises here, the speed of which is greatest within the chamber 10 near the rod 17. This circulating flow settles in the interior of the hollow cylindrical Ab Section 44, which is open to the chamber 10, continues. The fluid flow circulating in the hollow cylindrical section 44 can exit through the through slots 45 in the region of these slots which extends essentially within the tube section 19. Since the flow within the hollow cylindrical section 44 is a circumferential or vortex-shaped flow, the fluid flows out through the mentioned areas of the passage slots 45 and reaches the space between the section of the hollow cylindrical section 44, which extends into the tube 19, and the inner wall of the tube 19. 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.

By moving the elongated core 13, which is possible from the outside through the rod 17, the amount of fluid flowing through the chamber 10 and entering the tube 19 can be changed.

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. Two chambers 10, 10 'with side walls 11, 12 and 11', 12 'are connected to one another in terms of flow via a pipe section 19. A pipe section 19 'adjoins the side wall 12' of the chamber 10 ', which is adjoined by a pipe section 48 which widens in a toroidal shape. 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. In the chamber 10 'there is 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 part of the embodiment according to FIG. 8, which comprises the tangential flow channel 3 'and the chamber 10', essentially corresponds to the second embodiment according to FIGS. 3A and 3B.

The embodiment according to FIG. 8 can be used for mixing two fluids or as a jet pump. In the former case, the fluids flow into the chambers 10 and 10 'each under the action of a positive pressure. In the latter case, 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. As a result, 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. egg In this embodiment, 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 Durσh ^' 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. Here, too, 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

19 into chamber 10 ', both of which the fluid flow is also in the form of a spiral potential vortex. The flow exits the chamber 10 'through the tangential flow channel 3'. The orientation of the tangential flow channels 3 and 3 'is adapted to the direction of rotation of the respective fluid potential vortices.

The embodiment shown in 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'. By axially displacing the core 13, 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.

In the previously described embodiments, 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. However, 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. As has already been mentioned, 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.

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. Guide elements 61. 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.

It is now assumed that 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). When the core 60 is rotated by the drive device, the guide elements 61 attached to the core 60 also rotate. As a result, 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.

It is advantageously possible with a device according to FIG. 10 to build up a relatively high liquid pressure in the tangential flow channel 3. 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.

If the radial extension of the guide elements 61 is independent of the rotational position of the core 60, the space between the ends of the guide elements 61 and the inner surface of the spiral-shaped guide surface 2 changes during one revolution depending on the rotational position. In order to achieve good conveyance of the fluid by the guide elements 61, which was assumed to be a liquid in this example, 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.

Within the scope of the invention it is also possible to use the fluid vortices generated in a chamber with a circular-arc-shaped or spiral-arc-shaped peripheral wall to set a rotatable core in rotation. An example of this according to the invention is shown in FIG. 11.

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. 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 inner surfaces 58 and 58 'are curved cylinder surfaces in the direction of the core axis. 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. In the end region 55 of the guide element 57 opposite the inflow surface 53, 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.

As already mentioned, the core 56 having the guide elements 57 and 57 'is rotatably mounted. In at least one. 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, which is shown by way of example in FIG. 11, will now be described in the case where the fluid is a liquid. Assume that 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. In the presentation according to 11, 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. If one follows this flow path 60 in a clockwise direction, it can be seen that this flow path 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. Here, too, 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 '.

In the embodiment shown in FIG. 11, 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. However, 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.

Advantageously, 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. In this case, 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.

In summary, it follows that, according to the basic idea of the invention, 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. The spiral fluid potential vortex is constructed in such a way that essentially for any two points P ₁ and P _{2 of} the spiral fluid potential vortex, w ₁ r ₁ ⁿ = w ₁ r ₂ ⁿ , where r _{i is} the radial distance from the vortex axis, w _{i is} the present one Flow velocity of the fluid and n mean a constant, for which 0 <n <gilt applies. Preferably 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.

It is also pointed out that 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.

Claims

Patent claims

1. A device for converting a fluidity of a first type into a fluid flow of a second type, having a chamber which is delimited by two side walls and a concave peripheral wall extending between the side walls, with a substantially arranged tangentially to the peripheral wall, to form a Passage area flowing into the chamber and a passage Step opening in a side wall, characterized in that the peripheral wall (1) runs along a circular arc or a spiral arc, that in the chamber (10) an elongated core (13) is arranged, which has a circular cross-section and its central longitudinal axis with the axis of the circular arc or spiral arc and which extends through the passage opening (8) to form an annular gap, and that for any two points (P ₁ , P ₂ ) the fluid flow between the first passage area (6) and the outer surface of the axial core ( 13) essentially the condition w ₁ r ₁ ⁿ = w ₂ r ₂ ^{n is} met, with r _i the radial distance of the point P _i from the center (0) of the circular arc or the spiral arc, w _i the flow velocity of the fluid on Point P _i and n of a constant with 0 <n <∞.

2. Device according to claim 1, characterized in that a flow channel (19) adjoins the passage opening (8) in one side wall (12), into which the elongate core (13) extends and the inner wall of which extends from the peripheral surface of the elongate Core (13) is spaced.

3. Apparatus according to claim 1 or 2, characterized in that the elongated core (13) has a continuous, in the longitudinal direction of the elongated core (13) extending, inner flow channel (25) and up to the opposite of the annular gap, others Side wall (11) extends, and that the inner flow channel (25) on the side of these other side wall (11) opens outside the chamber (10).

4. The device according to claim 3, characterized in that in the inner flow channel (25) of the elongated core (13), a further elongated core (30) is arranged, the peripheral surface of which is spaced from the inner wall of the inner flow channel (25), and that the further elongated core (30) over the annular gap end. of the elongated core (13) extends.

5. Device according to one of claims 1 to 4, characterized in that in the chamber (10) between its side walls (11, 12) movable actuator (16) is provided, the

The peripheral surface is in close proximity to the inner surface of the peripheral wall (1) of the chamber (10).

6. The device according to claim 5, characterized g e k e n n z e i c h n e t that the

Actuator (16) is plate-shaped and extends from the elongated core (13) towards the peripheral wall (1) of the chamber (10).

7. The device according to claim 5 or 6, characterized in that the actuator (16) extends perpendicular to the longitudinal axis of the elongated core (13).

8. The device according to claim 1 or 2 and one of claims 5 to 7, characterized in that the elongated core (13) is movable along its longitudinal axis and the actuator (16) is attached to it.

9. Device according to one of claims 1 to 4 and one of claims 5 to 7, characterized in that the elongated core (13) is displaceable along its longitudinal axis and extends through an opening. (26) in the other side wall (11) regardless of its displacement position, and that the actuator (16) is attached to the elongated core (13).

10. The device according to claim 1 or 2, characterized in that the elongated core (13) has at least one portion (35) tapering in the direction of its annular gap end.

11. The device according to claim 4, characterized in that the further elongated core (30) has at least one portion (32, 33) tapering towards one of its ends.

12. The apparatus according to claim 10, characterized in that the extending beyond the one side wall (12) section of the core (13) has at least one guide element through which at least part of the fluid vortex flow can be deflected in the direction of an axial flow.

13. The apparatus according to claim 11, characterized in that the extending beyond the elongated core (13) portion of the further elongated core (30) has at least one guide element (36) through which at least part of the fluid vortex flow in the direction of an axial flow is deflectable.

14. The apparatus according to claim 2, characterized in that the cross-sectional area of the flow channel (19) adjoining the passage opening (8) in one side wall (12) is constant or widens,

15. The apparatus according to claim 1 or 2, characterized in that the elongated core (13) has the shape of a hollow cylinder (44), the end extending beyond the one side wall (12) is completed that in the outer surface of the hollow cylinder ( 44) at least one passage slot (45) extending parallel to the cylinder axis is formed such that the elongated core (13) is displaceable in the direction of the cylinder axis and is sealingly guided in the passage opening (8) in one side wall (12).

16. The apparatus according to claim 1 or 2, characterized in that in the chamber (10) between the elongate core (60) and the peripheral wall (1) a spiral guide surface (2) is arranged stationary, which is between the side walls and over a Angle of essentially Chen extends 360 ° and is oriented in the same direction to the tangentially into the chamber (10) opening flow channel (3) that a passage opening is formed in one of the side walls, which opens within the spiral guide surface (2) in the chamber (10) that the elongate core (60) is arranged so as to be rotatable about its longitudinal axis and has guide elements (61) extending radially to very close to the core-side surface of the spiral-shaped guide surface (2).

17. Device according to one of claims 1 to 16, characterized in that the passage area (6) of the flow channel (3) opening tangentially into the chamber (10) extends essentially across the width of the peripheral wall (1).

18. The apparatus according to claim 17, characterized in that the passage area (6) has a rectangular cross section.

19. The apparatus according to claim 17, characterized in that the passage area (6) has a substantially trapezoidal cross section that tapers towards one of the side walls (11, 12).

20. Device according to one of claims 17 to 19, characterized in that means are provided through which the cross-sectional area of the passage area (6) can be changed.

21. The apparatus according to claim 8, characterized g e k e n n z e i c h n e t that a to the outside of the chamber (10) extending, movable actuator (17) is provided, which is fixedly connected within the chamber (10) with the elongated core (13).

22. Apparatus for converting a fluid flow of a first type into a fluid flow of a second type, having a chamber which is delimited by two side walls and a concave peripheral wall extending between the side walls, with a substantially tangential to the peripheral wall, forming a Passage area in the flow channel opening into the chamber and a passage opening in a side wall, characterized in that the peripheral wall (1) runs along a circular arc or a spiral arch, that in the chamber (10) an elongated core (13) is rotatably arranged, which has a circular cross-section and the central longitudinal axis of which coincides with the axis of the circular arc or spiral arc, that the core (56) has at least two guide elements (57, 57 '), each with a first cylindrical surface (57, 57') facing the peripheral wall (1) and one to the first cylinder surface (57, 57 ') and approximately in the Direction to the longitudinal axis of the core (56) extending second cylinder surface (53, 53 '), that the geometric location of the respective generatrix of the first cylinder surface (57, 57') is a spiral arc section adapted to the course of the fluid flow, that the geometric location of the respective generatrix of the second cylinder surface (53, 53 ') is a portion of a curve that the two generators parallel to the longitudinal axis of the

Core (56) run that the tangent to the spiral arc section and that at the curve section form an acute angle at their common point, that between two respectively adjacent guide elements (57, 57 ') a passage gap is provided towards the center of the core (56) that the core-side opening areas of the passage gaps are in fluid communication with the passage opening in a side wall, and that for any two

Points (P ₁ , P ₂ ) of the fluid flow between the first passage area (6) and the outer surface of the guide elements of the core (56) essentially satisfy the condition w ₁ r ₁ ⁿ = w ₂ r ₂ ⁿ , with r _i the radial Distance of the point P _i from the center of the circular arc or of the spiral arc, w _i the flow velocity of the fluid at the point P _i and n a constant with 0 <n <oo.