DE19806507A1 - Design elements to improve working and power machines - Google Patents

Abstract

The design elements are based on the principle that the potential spiral flow of a fluid is the most efficient form of fluid motion. Various elements are described to create this flow in the most efficient manner for use to be made of it. The principle can be applied to reciprocating and rotary pistons. For example, a rotor may be placed in a funnel-shaped inlet region in a jacket with sectors, some of which are straight and some curved. Such a rotor would have scoops shaped so that the fluid between them is accelerated axially.

Description

1. Introduction 1.1. Problem

The known technique of turbomachines, for. T. extraordinarily high efficiency, which is hardly considered to be capable of improvement. However, this primarily concerns the machine components, which is the direct conversion of the kinetic energy of the fluid into kinetic energy mechanical Type, that is, the movement of a rotor or vice versa. By contrast, they are usually lossy Machine components, which the supply of the fluid to the turbomachine, the deflection of the Relate fluid flow within the machine or discharge of the fluid from the turbomachine. The same applies to reciprocating piston machines, where only the known mechanics of the lifting movements are used is an inadequate solution. In this respect, both flow and reciprocating machines offer great potential to improve the efficiency with regard to the fluid flow such as the mechanics.

1.2. Base

The basis of this patent application here is the invention "Constructional elements for improving the fluid flow in pipes ", which is hereinafter called" pipe invention ". There were based on a new model potential molecular movement developed an ideal flow form of the fluid flows in pipes. These be standing from rolling layer, main and core current and was called "potential swirl flow". Were there Various new construction elements designed to generate this potential swirl current and are suitable for use. The construction elements there are only fixed parts.

1.3. Goal setting

The aim of this patent application here is to increase the efficiency of labor and strength machines through a systematic, novel design of these machines and associated components. The physical principles discussed in the pipe invention are explained here continued speaking. The resulting knowledge becomes a basic construction principles for turbo machines such as for reciprocating piston machines and their components. This are implemented here in appropriate constructions of a new kind. In contrast to pipe inventions the moving parts of turbomachines are in the foreground of this patent application.

Further consequences of these findings and inventions in other areas of application are presented in further patent applications, for example with regard to the upward and forward propulsion of Air and water vehicles.  

2. Physical basics 2.1. Potential swirl flow

A model of potential molecular motions was developed in pipe invention. The basis for this was the movements of the molecules of a fluid that point equally in all spatial directions. For example, eight of these potential movements for a molecule can be represented in the drawing plane (A in Figure 1; hereinafter referred to as "A-1"). Representing these directions of movement, the two perpendicular ones could be considered (B-1). A movement component in the general direction of a streamline (SL) can be impressed on these potential directions of movement (C-1). Of the resulting directions of movement (D-1), two of these potential movements (E-1) can be considered representative. The greater the speed in the current direction, the farther forward (F-1) these potential, representative directions of movement of a molecule will point.

In the pipe invention it was shown that these potential movements due to friction on the pipe wall an additional movement in the direction of the pipe center (G-1) is impressed, which is considered perpendicular to Tube wall can be considered effective. Because of this, in the pipe invention "cross flow" (QS) mentioned, component inevitably results in turbulent flow with its disadvantages in terms of Fluid flow rate of conventional type. This cross flow, however, has a positive effect, if as a general direction a circular path (H-1) is desired for the streamlines. However, the circular path must not only be radial Direction to the general current direction, but must also point in the axial current direction.

In the pipe invention it was shown that molecules of neighboring, parallel streamlines always point in the direction of the faster river. It was derived from this that the rotational movement is not in the Frame of a rigid vortex, but a potential vortex should take place. The ideal form of fluid flow in pipes, the "potential swirl flow" was developed from this in pipe invention. Also at Working machines and power machines will make sense to generate or use them. The following is a Potential vortex with additional movement in the axial direction referred to as "potential swirl current" (ie the "Rolling layer" ignored the pipe invention).

2.2. Hurricanes

The strongest potential swirl flow is in the form of tornadoes. Their emergence in general explained by the coincidence of air masses of different temperatures, which then reach the ground training reaching vertebrae.

Smaller wind pants can be seen, however, that they can develop from the ground. A somewhat stronger air flow (compared to the general air flow or relatively calm air) on the surface of the earth is sufficient; it is more obvious if two opposite air flows meet each other offset, as shown schematically in Figure 1 (I-1). This initially causes the currents to roll into a vortex in one plane (J-1). The resulting local overpressure then leads to this flow escaping upwards (K-1). The air parts moving in this way border on stationary or slower flowing air parts. There is a diffraction of the streamlines towards the faster flowing parts, the cross flow described above in the direction of the vortex axis as parallel to this, that is to say a potential swirl flow.

Instead of this initial local overpressure, a local underpressure can also be assumed this must be connected to an upward flow. Even then the surrounding one Air does not continue to flow concentrically to the center of the negative pressure, but instead (starting from random asymmetry) very quickly to form a curling and upward vortex. Due to the cross flow, a potential swirl current develops from this.

The above large air masses have different general directions of movement and different heat great kinetic energy. The (coincidentally) opposite and something staggered air meets Currents of local wind trousers, on the other hand, have only a slightly higher kinetic energy than that of general air movement in their environment. A relatively small one can also be the triggering moment Negative pressure can be viewed, e.g. B. due to an upward movement of a relatively low air mass local but above average warming. The energy of the resulting potential swirl flow appears in any case to be a multiple of this originally existing kinetic energy or the relatively low energy of the triggering moment.

2.3. Water vortex

An analogous sequence of movements is given in water eddies. A current causes (or two moves) opposite currents cause) a rolling, initially flat vortex, the flow then evades down. Likewise, a current at depth (or again two currents) result in a potential vortex that affects the water surface. Or one from deep down rising currents can cause this. Or a downward drain creates this sequence of movements (like in every bathtub).

The triggering moment can in turn be a small one. The training of the potential swirl is fed flow due to the pressure of the surrounding, relatively calm medium, or due to the friction a wall (as shown in the pipe invention). There is a pressure drop from the outside in.

The cause of this is shown schematically in Figure 1 using the above model of potential molecular movements. A relatively dormant molecule (LI) has potential movements in all spatial directions, which in total can be viewed as radial to the axis of rotation (RA, right in the picture). A molecule (M-1) moving about the axis of rotation (RA) on a circular streamline (SL) also has molecular movements in any direction according to the general fluid temperature. This tangential direction of movement is also impressed on them (corresponding to D-1). After a collision with a relatively stationary molecule (L-1), it is braked in the tangential direction and gains movement in the radial direction (analogous to G-1), i.e. in the direction of the axis of rotation. A molecule on an adjacent inner streamline of a potential vortex (N-1) still has these properties, only it has a higher velocity in the tangential direction.

All these molecules (L-1, M-1 and N-1) have the same energy component in the radial direction general molecular motion. As is known, there is a higher one outside in a potential vortex Pressure than inside. This phenomenon results from the relatively greater frequency of those outside Molecules (L-1 versus M-1, M-1 versus N-1) to perform movements in the direction of the axis of rotation. The larger amount of potential movements of internal molecules (N-1 versus M-1, M-1 versus L-1), on the other hand, point forward in the direction of rotation or inward, and are therefore also relatively rare move outwards.

A molecule on the innermost streamline (N-1) points not only outwards, but also inwards relative little potential molecular movements. So it produces a relatively small amount both externally and internally Pressure. In a water potential swirl flow of sufficient strength, this pressure will be so low in the middle that it now only corresponds to air pressure (O-1, as an example of a molecule of air). That is why in water whirl even at a depth of a few meters an air column can be recognized as the axis of rotation. This Vortex core will have decreasing speed from outside to inside, so it will be a rigid vortex.

The pressure difference of the potential vortex can also be equated with the above-mentioned cross flow. This can be seen particularly clearly in the known experiments with water vortex tubes, in which Suspended matter (also heavier than water) can be introduced. The cross flow drives them in the direction Axis of rotation. When this "buoyancy" has brought the suspended solids to the innermost streamline, they protrude (relatively large parts compared to the molecules of the fluid) in the vortex core. Be within this they braked due to the lower inner speed, "fall" into an orbit accordingly smaller radius or ultimately collect on the axis of rotation.

2.4. Vortex energy

In addition to the movements, pressures or currents described above, there are some essential properties added. The potential directions of movement of a molecule in the potential swirl current (M-1 and N-1) point predominantly to the front, to a much lesser extent to the rear. These molecules don't move the same way either quickly because "heat" is only the average of a bell-shaped distribution of different speeds of the corresponding molecular movement is. In this respect, molecules in a streamline can collide. In each In the event these collisions become the general fluid flow within a relatively rectified flow  less serious impairment than with turbulent flow. The "throughput" in a potential swirl Flow will be much higher in the sense of the (curved) streamlines.

Another important property of the potential swirl flow is that the collisions also cross to the respective Streamline the less or less disadvantageous, the faster the speed in the direction Streamline is in relation to the speed of general molecular motion. The movements on the Streamlines of a potential swirl vortex are maximally free of collisions or at least minimal negative in the sense of the general current direction. There can be more molecules in the same space move relatively collision-free than with turbulent molecular movements or turbulent flow.

Above it was assumed that a relatively dormant representative of all potential movements Molecule (L-1) the movements can be viewed radially to the axis of rotation. This gives the positive Effect of diffraction of the streamline to the circular shape. If you look at the other potential movements Considering this molecule, the following effects result:

If a relatively dormant molecule (L-1) (randomly) on a path parallel or at least in the direction of the Streamline of a molecule of an outer streamline of the potential swirl vortex (M-1), it will there can move relatively long without collision or can be fully integrated as part of this streamline become. If this molecule (L-1) is (accidentally) pushed against the direction of the outer streamline, then it initially brakes the corresponding molecule (M-1) in the event of a collision, but the negative occurs Acceleration of the molecule (M-1) only with the energy of the general molecular movement. The molecule (L-1) takes over the energy (including the rotational energy) of the decelerated molecule (M-1) approximately tangential direction. In the case of a subsequent collision (now total again perpendicular to Axis of rotation) then also deflected onto a circular path. Ultimately, a very fast (compared to general heat) molecule (L-1) are (randomly) on a path on which it is from behind a molecule (M-1) of the potential swirl collides. In this case it brings its energy and direction in a positive sense of rotation, while it itself is only slightly reflected in a negative sense.

In this way it follows that the boundary layer of the potential swirl flow continues to outward shifted, practically ever larger amounts of fluid are integrated into this vortex. The potential twist flow seems to have more energy than is originally available. Common interpretation is that heat is removed from the fluid. Or a special "vortex force" is postulated. This will especially adopted for swirl rings. However, this is only a special form of potential swirl flow. Instead of evading the flow of an air vortex upwards or a water vortex downwards this evasion takes place in a circular shape in the swirl ring. The axis of rotation forms a circle. It is not additional space required for the flow to evade. A swirl ring is therefore a special one stable form of the potential swirl flow.  

From the considerations and explanations given in the pipe invention it follows that all Explain the appearance of the potential vortices with a simple model of potential molecular movements are. There is no greater amount of kinetic energy in a potential swirl flow than originally is available. There is no energy conversion in the potential swirl flow. It takes place there is also no energy absorption by the surrounding, relatively still fluid. It only finds one more orderly alignment of the directions of movement instead.

Each fluid has far more kinetic energy than molecular macroscopic energy Is visible or usable. The imprinted movement through a general current direction is only a fraction of the general molecular movement. This applies e.g. B. also for all triggering currents a hurricane, a wind trousers like a water vortex. However, as soon as the requirements for Aus Formation of these potential swirl currents are given by the structure of the movements described above These relatively low output currents are impressed with a constant direction and into this directional flow other fluid quantities integrated. These bring their energy to the molecular movement. With this in mind one says that the originally existing flow now also has the velocity component directional molecular movement (instead of impressing the flow on an directed molecular movement).

The apparently higher energy of a potential swirl flow does not consist of a transformation or introduction another form of energy, but only in the larger order of the directions of movement The object of this invention here is to achieve this greater order of flow in machines to organize. Before doing so, however, a few more theoretical aspects need to be clarified.

2.5. Pressure between fluid flows

The transfer of forces from one solid body to another solid body via pressure is no problem. The mass of solid bodies can even be thought of as united in one point. In the case of a fluid, on the other hand, particles or each molecule have to be considered as independent bodies.

If the pressure of one fluid is to be transferred to another, the pressure gradient is compensated. If turbulent flow or turbulent molecular movement is a sufficient result, do so this sense. However, if directional movement and speed are to be achieved, then must the pressure of one fluid flow can be used so that the potential swirl flow of the other is increased becomes. The technical implementation of this is in the pipe invention for the construction element "Introduction or Rejection ". On the other hand, this tangential introduction of fluid particles also takes place at the top described expansion of the radius of a potential swirl current. This kind of merging of fluid streaming will make sense to also be used with turbomachines.  

2.6. Suction between fluid flows

Suction between solid bodies is practically irrelevant or not given (because of the participation relatively small amount of a fluid is required). The suction effect between fluid flows, however, is significant, e.g. B. in a simple water jet pump.

The individual molecules of a fluid have no "inertia" insofar as it can be assumed that at a collision of each molecule instantaneously detects the kinetic energy and direction of the other molecule takes over. So every molecule is always ready to be pushed in any direction. How far it goes this path comes forward depends solely on when another collision occurs. Mostly The molecules of a fluid therefore always flow into areas of local negative pressure, i.e. H. lower density. On the other hand, collisions are also relatively rare if the majority of the molecules in a fluid are in one another move in the same direction. In this respect, a potential swirl flow also represents a "pull". Molecules can move in the direction of rotation of this flow over a relatively long way without (or with only slightly negative effective) collision. This movement can even lead to an area of greater density. This movement is triggered by normal molecular movement, so it does not require any additional movement external energy. This type of "suction effect" is therefore also useful for flow be able to use and use machines.

2.7. Suction effect of fluid on solid bodies

Fluid can flow in the direction of a suction (in the broad sense above), but never a solid. A suction or vacuum is z. B. generated at the top of a wing. However, this alone is completely ineffective. The pressure on the underside is effective in terms of buoyancy. The Fluid flow on the top only causes a lower pressure on the wing from above is exercised.

Figure 2 shows what is causing this "pull". Relative to the resting wing (A-2), the fluid flow on the top is faster than on the bottom due to the profiling. With a molecule (B-2) on the underside, the normal molecular movement has a relatively small movement to the rear, a molecule (C-2 and D-2) with a larger movement. The molecule (B-2) exerts pressure by impacting the underside of the wing. A molecule (C-2) impacts the upper side of the wing with less frequency or with a flatter angle. By withdrawing the rear wing surface against a molecule (D-2), the frequency will be even less frequent or the angles will be even flatter. The resulting "pressure difference" gives the buoyancy.

In turbomachines, you should never attempt to pull a solid body by fluid suction alone want to move. The suction side must always be opposite a pressure side, with the remaining pressure the Suction side is to be as low as possible, ideally reduced to zero.  

The situation is to be seen differently if a solid body that is moving due to another cause has minimal possible resistance should be moved by a fluid. Then it is useful that in the direction of movement to remove any fluid in front of the solid by suction. However, this aspect is in one another context or another patent application to be considered.

2.8. Solid body suction effect on fluid

The suction effect of solid bodies in liquids is problematic with regard to the risk of cavitation. Also in In compressible fluids, the suction effect of solid bodies is often considered unsuitable. The back soft solid body creates a local area of lower fluid density. They flow into these Molecules of a fluid with normal molecular speed. However, it is important to ensure that no turbulent flow occurs but a directed, continuous flow can develop. Therefore z. B. this retraction of the solid body does not take place too quickly. For this purpose, e.g. B. a relative large space required to form a potential swirl flow. Under these conditions the The suction effect of solid bodies on a fluid can be quite useful in turbo machines.

2.9. Solid body pressure on fluid

The generation of pressure in fluids by moving solid bodies is due to the compression stroke in Piston machines solved as best as possible. Even in turbomachines, solid bodies can move against a fluid pressure. The generation of pressure in the fluid should not be in the Stand in the foreground. Rather, the objective should (almost exclusively) be the generation of directed Movement should be as fast as possible, d. H. a strong potential swirl flow. Of the Efficiency in converting mechanical energy into fluid movement depends on the design of the Rotors. However, the type of supply of the fluid to this machine component is just as important as that Removal of this machine part or its forwarding.

Under these circumstances, it makes little sense to supply relatively static fluid to a pump or even to do so immediately afterwards to set up any swirl by tail units. It makes a lot more sense at first only want to generate rotational speed with swirl and only shortly before using the kinetic energy of the fluid flow to bring it into the appropriate form of movement. Construction elements for this are mentioned in the pipe invention. Flow machines are presented in this patent application here, which realize an optimal flow through the entire machine.

2.10. Pressure effect of fluid on solid bodies

In the pipe invention, the flow conditions in pipes were treated. In a tube, the Reflection of movements towards the pipe wall is considered to be in principle perpendicular to the pipe wall become. The shear forces (SK) in the fixed pipe wall could be neglected. With regard to the moving fixed parts here, however, these are essential.  

A moving machine part is generally referred to below as a "rotor" (RO) (in later chapters the respective design of this machine part is also defined). This force parallel to the surface of the In the following, the rotor is called "thrust" (SK).

This thrust is dependent on the angle of the impact: with a steep angle (E-2) it is less than with a flatter angle (F-2). With a very flat angle (G-2), however, a "total reflection "occur, i.e. the thrust is very low with a very smooth surface of the rotor a rough or appropriately shaped surface (H-2), however, can in turn be enlarged. Last but not least, the thrust is dependent on the speed of the impacting molecule in relation to the Speed of the rotor (I-2). If the speed difference is zero, the thrust is also zero.

When the kinetic energy of a fluid flow in a turbomachine is caused by pressure on a rotor mechanical energy is to be converted, on the one hand comes the impact angle as well as the shape but also the surface design of the rotor. It is generally assumed that the amount of energy that can be converted depends only on what mass and at what speed Machine component is fed. However, this view requires a more detailed look.

A molecule (I-2) impacts the rotor (RO) due to its impact on the rotor surface (to simplify all movements perpendicular to the rotor surface are considered). The rotor then deviates accordingly (to the right in Figure 2). The molecule is reflected (to the left in Figure 2) and moves back towards the rotor after another collision. The second impact of the molecule (now shown as K-2) on the rotor surface will in turn cause an impulse on the rotor. However, this will be less than the previous impulse due to the rotor now moving in the same direction. With a correspondingly reduced energy, the reflection of the molecule also takes place. If this process continues, less impulses will be given.

A molecule of the fluid is thus its kinetic energy on the pressure side of a rotor by repeated Deliver impacts, however the first impact is the most effective, while the subsequent one have less effect. It would be disadvantageous if the reflection of the molecule (now called L-2) by other molecules (e.g. M-2) would take place indirectly through a suction side of another rotor (which is usually taken into account by a correspondingly small number of rotor blades).

After the fluid has given up its energy to the rotor, it must be able to drain off. The one shown here therefore only vertical impact of the fluid molecules on the rotor surface is not feasible. A molecule (N-2) will therefore hit the rotor surface (RO) at a shallower angle while this is already in a receding movement (to the right in the picture). After that impact, it will Molecule with a correspondingly lower energy reflected. One molecule (O-2) was previously in the corresponding  Way reflected on the rotor surface. The next molecule (N-2) is therefore from the previous molecule (O-2) can hardly be reflected so that there is another, effective impact on the rotor surface could come. Of course, the molecule (O-2) will eventually become a molecule again (P-2) reflected. Ultimately, however, this molecule (P-2) will only have the normal energy of the environment and therefore no further impulse can be exerted on the rotor.

The speed of the molecular movement is usually many times higher than that of a rotor. However, previous theoretical statements are by no means meaningless. The logical consequence is rather, that as much as possible each fluid molecule should deliver its energy directly to the rotor, d. H. a The thinnest possible jet of the fluid should be able to strike the largest possible surface of the rotor.

Another impact of a molecule (Q-2) on the receding surface of the rotor (RO) is only achieved essential effect if the reflection occurs on a housing part which is generally used as a strator (ST) referred to as. The distance between the rotor and strator should be as small as possible, so that in one relatively thin fluid jet as little unproductive fluid flows can arise. Important is ensuring that these targeted and continued collisions continue to be harmonious guided flow, ideally again in the form of potential swirl.

2.11. Essential starting points

There is almost no straight line in nature. The exception to this are crystals, which are also the body greatest strength. Fluids, on the other hand, move in a variety of rotary movements. It is not arbitrary like that, but obviously the path of least resistance. The aim of this patent application is to implement these harmonious movements, as well as technically feasible, in machines.

In principle, turbomachines have to be designed in such a way that a throughput of as large a mass as possible speed is as high as possible. The generation or use of pressure may only be a consequence of this.

This means that turbomachines the fluid in an optimal flow form, the potential swirl flow to be supplied. When implementing the form of energy, this directional flow must be so long and so well preserved as possible, significantly strengthened with pumps.

This energy conversion cannot take place without redirecting fluid flows. Again, it is valuable that relatively directional flows around an axis of rotation with a relatively low resistance around a allow another axis to pivot. However, when redirecting it must also be considered which form of Power transmission makes sense, suction or pressure, between fluid flows or between fluid and solid body.

The following constructions have been developed based on these aspects and the principles outlined above.  

3. Construction elements 3.1. Pre-swirl generator function

This construction element is used to generate a fluid flow with swirl, consisting of a Main stream (including core stream) and a secondary stream.

Construction principle

This construction element corresponds to the construction element shown in the pipe invention "Container outlet or pipe inlet". The construction element there consists exclusively of solid parts, while a rotor is an essential part here.

A rotor rotates in a relatively large inlet area with a tapering diameter. This represents basically a tube, the diameter of which increases from the back to the front, but with an ever smaller one Diameter than that of the inlet area. (The "rear" is always the direction or machine side from which the flow comes, "front" always means the direction or machine side, in which the current flows). Fluid is sucked or pressed into the rotor through openings in the rotor, which flows through the rotor as the main flow. By the suction effect of the rotor as by friction Its outer surface causes the fluid to move radially and parallel to the axis in the entire inlet area transferred. The outer areas of this flow flow between the inlet wall and the rotor wall Sidestream. From the inlet to the outlet, the movements of all fluid parts represent a total Potential swirl flow.

Constructional execution

Figure 3, left, shows a schematic and exemplary longitudinal section of this construction element. The inlet pipe (A-3) is fixed in the housing (GE) of the machine. The walls of the inlet pipe have a round cross section, which decreases from the back to the. The dimensioning of this inlet area in relation to the rotor (RO) can or should be chosen to be larger than shown in the drawing. If the fluid is removed from a container, the hyperbolic design of the inlet area shown in the above-mentioned structural element of the tube invention should be used.

The rotor (RO) can be rotated about its axis of rotation (RA) on the same axis as that of the inlet pipe stored. The rotor is represented by a tube, the diameter of which is always smaller than that of the Inlet pipe. The diameter of the rotor widens from the back to the front. He is in the back not designed as a full surface as a tube, but is especially formed from one or preferably several blades The longitudinal axis of these blades run parallel to the smallest to the largest diameter of the rotor Pipe axis, can alternatively also have an angle to the pipe axis, can be straight or have a curved course.  

Figure 3, right, shows an example of a cross-section of this area (on an enlarged scale compared to the illustration on the left). The rotor turns (here clockwise) around the axis of rotation (RA). Figure 3, top right, shows a rotor with two blades. In principle, the blades (I-3) are shaped analogously to the representation of the above-mentioned construction element of the pipe invention. Starting from an outer radius, they are curved inwards to an inner radius. To stabilize this shape and to control the fluid flow, baffles (H-3) should be installed between these ravens and between the blades (I-3). Figure 3, in the middle, shows schematically how these guide plates (H-3) should be positioned with respect to the axis of rotation (RA): from back to front with an increasing angle of attack. In principle, therefore, a baffle plate could be installed that is spirally wound from the back to the front, continuously having larger radii and continuously larger angles of attack. The blades with their respective curvature from the outer edge to the inner edge of the guide plate are then approximately perpendicular to its surfaces. In Figure 3, bottom right, a rotor consisting of four profiled blades (I-3) is shown as a further example; baffles (H-3) are in turn arranged between the blades.

Baffles at the rear (E-3) and at the front can be between the wall of the inlet area (A-3) and the rotor (G-3) installed. These can be used on the one hand to support the rotor or to drive the rotor Convey rotors. Storage and drive can be done with known technology and are therefore not shown. The angle of attack of these baffles should in turn correspond to the desired current direction correspond. Rear baffles (E-3) should be twisted to give a stronger swirl inside and outside to produce less swirl. Front baffles (G-3) should have the relatively largest angle of attack of all baffles.

The rear end (F-3) of the rotor can be solid or a relatively small tube represent knife. In this tube the core flow could be triggered as a rigid vortex if in the tube appropriate baffles are attached. These should only be on the inner wall of this pipe section attached and should be only a small height.

Special properties

This construction fulfills all the theoretically described prerequisites for triggering a potential swirl flow, such as the criteria set out above for the sensible use of suction or pressure between fluid and solid bodies:
The fluid (B-3) at the inlet is already swirling through the baffles (E-3), but the mass of the fluid in the (larger) outer area is only very small, but in the (smaller) inner area is stronger. An interface of the nuclear current with a rigid angle can already be introduced in the middle.

The relatively turbulent flow at the rear (unless the above-mentioned construction element of the pipe invention can be used) parallel to the tube axis is already there by the baffle (H-3) in radial Guided movement. This baffle initially only covers a relatively small inner area relatively flat angle of attack, but forms a continuous surface up to the front with a relatively strong end Employment, so successively records all partial flows with a continuous course.

The outer walls of the blades give way due to the increasing diameter from the back to the front of the rotor only very gently. They create a uniform suction, which fluid in the direction Causes pipe axis (RA) to flow. Fluid also flows into the interior of the rotor, where its retreating inner walls (seen from the inside to the front) continue this pull. This suction inside favors that Whirling the fluid flow. Less suction and at the same time more pressure is exerted there when the blades (I-3) are profiled without creating resistance as with wing-shaped blades. The fluid inside the rotor is accelerated radially by friction on the inner wall and thus experiences Centrifugal force, which has an axial force component on the inclined inner rotor walls. Through suction, pressure and centrifugal force, a movement occurs parallel to the rotation axis.

Inside there is always a suction, while the inlet area narrows, so that from its walls (A-3) there is always an external pressure, i.e. the desired pressure difference is given. This pressure from externally, as theoretically presented above, the curling of the potential swirl flow is strengthened.

In addition, the rotation of the rotor and the associated friction on the outside of the rotor Potential vortex generated (analogously e.g. how a potential vortex is generated in the water glass when in the middle Wooden stick is turned). As more and more fluid flows into the interior of the rotor, it gets it outer potential vortices also movement parallel to the rotation axis (analogue e.g. as by gravitation of the Drainage of water from the bathtub causes this).

The angle of attack of the guide plates (H-3) and the curvature of the blades (I-3) cause pressure on the fluid for generating movement in radial and axial directions. However, these forces never set in abruptly, but only in a gentle and continuous manner. In relation to the cross section of the draining Main current (C-3), these effective areas are extremely large. The disadvantage of large areas in the form of However, friction becomes an advantage here: it essentially causes the formation of the potential swirl flow in the entire fluid range. The secondary flow (D-3) is also achieved without any special effort.

The above printed pages work without disadvantageous suction pages. All suction from solid bodies to the fluid as from Fluid flows from one area to other areas are smooth and continuous. All currents this machine can run absolutely laminar, but never linear, but always turning.  

The energy consumption of this machine is only partly used to meet the requirements for To create an extensive potential swirl flow. This type of movement Living dynamics can thus be used. Due to the fluid-compatible movements in the the entire machine, the energy requirement will be relatively low, the efficiency will be correspondingly high.

This construction element generates a potential swirl flow with main and secondary flow. This can are further reinforced if a pump is connected downstream of this pre-swirl generator on the same axis.

3.2. Tube pump function

This construction element serves to generate a potential swirl flow.

Construction principle

The design principle is analogous to the pre-swirl generator shown above. Unlike this, here However, no main and secondary flow is generated, but the entire fluid flow is discharged into a tube.

Constructional execution

This tube pump is shown schematically and exemplarily in Figure 4 with a longitudinal section. The flow is shown from left to right. All designs with regard to the rotor, guide plates and blade from the pre-swirl generator shown above apply analogously. Other than there is the following:
The walls of the inlet area (A-4) taper to the rear to the diameter of the tube that receives the fluid flow. Through the openings of the rotor between the blades, the entire incoming amount of fluid (B-4) flows into the rotor (RO), ie the main flow (C-4) and the above secondary flow (D-3 or D-4) flow together . Therefore, no baffles between the wall of the inlet area and the rotor are required at the rear. Instead, the bearing (G-4) in the housing (GE) is shown schematically at the rear. There z. B. also the drive of the rotor, for example by externally attached to the rotor components of an electric motor.

Special properties and application

This machine has all the positive properties of the pre-swirl generator shown above in a corresponding way Way on. However, a potential swirl flow is immediately generated in a pipe here. This means low volume and a very compact design.

This means that this tube pump can be used directly for many purposes, but could also be used on the other hand subsequent centrifugal pump can be coupled.  

3.3. centrifugal pump function

This construction element serves to generate a potential swirl flow.

Construction principle

In this pump, fluid is drawn in in the axial direction in a large inlet area. A rotor is equipped with baffles in the radial direction, the angle of attack of which is large at the rear with respect to the axis of rotation is, but is almost zero in front. The fluid is accelerated parallel to the axis of rotation and at the same time in radial direction. The fluid flows in a radial direction, at the same time as the greatest path speed, tangentially out of the rotor and tangentially into a worm housing. There is an extraordinarily strong potential swirl flow generated.

Constructional execution

In Figure 5, top left, a centrifugal pump is shown schematically and as an example in longitudinal section. A rotor (RO) with its axis of rotation (RA) is rotatably mounted in a housing (GE). The rotor has an outer wall (A-5), the diameter of which is as large as possible at the rear, smaller in the middle, and larger again at the front. The rotor has an inner wall (B-5) which is identical to the rotor axis up to approximately the smallest diameter of the outer wall of the rotor, but becomes larger towards the front. At the very front is the outlet (C-5) of the rotor between the outer wall and the inner wall. Between the outer wall and inner wall of the rotor guide plates (D-5) are attached in a preferably radial direction. The angle of attack in relation to the axis of rotation (RA) is steep at the back, becomes increasingly flatter and is almost zero at the front, ie almost parallel to the axis of rotation.

Figure 5, right, schematically shows these angles of attack of the guide plates (D-5) in relation to the axis of rotation (RA). Preferably, several such baffles are installed, which are spirally wound around the rotor axis with continuously increasing inclination with respect to the rotor axis.

Two cross sections of such chambers are shown schematically in Figure 5, below. At the rear (pointing to the left in the picture), the cross section is almost a circular section ( 6-5 ), which is formed by the outer rotor wall (A-5), the guide plates (D-5) and the axis of rotation (RA). The cross-section of such a chamber is smaller at the front (pointing to the right in the picture), because instead of the rotor axis, this chamber is now represented on the inside by the inner wall of the rotor (B-5). The area of these cross sections should be designed from the back to the front by appropriate shaping of the rotor outer and inner walls in such a way that they correspond to the desired fluid velocity in the chambers in the respective area.

The outlet (C-5) of the rotor opens into a transfer duct (E-5) of the housing and this opens tangentially into a housing screw (F-5). This screw has a minimal diameter at the beginning (e.g. how in the picture on the left), in the direction of rotation it becomes larger (e.g. as in the picture on the right) after a full rotation  it has its maximum diameter (e.g. as shown in dashed lines in the image on the left). The transfer channel (E-5) should preferably introduce the fluid flow into the screw housing (F-5) so that the stronger fluid flow (in the rotor on the outer wall) flows into the worm housing (F-5) inside, the weaker Fluid flow (in the rotor on the inner wall) outside. The fluid flow in the screw housing can ultimately be discharged tangentially into an outlet pipe (not shown in the picture).

Special properties and application

Conventional centrifugal pumps generally have the following disadvantages with regard to fluid flow: the inlet area near the rotor axis represents a circular or circular area of relatively small cross-section The outlet area on the outer edge of the rotor, however, represents a relatively large tubular casing section The geometry of the chambers changes from the inside to the outside. The inlet of the fluid usually takes place in the axial direction without swirl. The fluid is abruptly pushed in by the blades accelerated tangential direction. Due to the increasing tangential distance from the inside to the outside there is a strong suction between the blades. So it already happens within the chambers turbulent, d. H. unproductive currents. By largely tangential adjustment of the blades on The outer edge of the rotor flows largely in the radial direction. The high web speed it cannot be transferred to the fluid on the outside of the rotor.

In contrast, the centrifugal pump shown here has the following basic advantages: large inlet area available. The fluid becomes gentle and gentle by the adjustment of the guide vanes initially accelerated mainly in the axial direction. The cross section available to the fluid becomes continuously reduced according to the acceleration, initially from the outside (as long as the centrifugal force is not yet too large), then from the inside. The acceleration continues to increase Acceleration in the direction of rotation. The cross section of the chambers is only reduced from the inside forth, while the outer boundary of the chambers remains almost constant. So there is hardly any pressure drop in given the chambers in the tangential direction. Rather, the pressure is always from the inside out growing. Due to the increasing diameter of the rotor outer wall, the Centrifugal force accelerating on the general fluid flow. Move from the inlet to the outlet all fluid parts in spiral paths, so as best as possible in stationary or laminar flow. The baffles always point in the radial direction. The fluid emerges from the rotor at the front at the highest path speed out. Practically only a rigid vortex is generated in the rotor, although the fluid flow is optimal is ordered and points in the appropriate direction. Due to the tangential flow into the screw This is where the potential swirl flow first arises, but of extraordinary strength.

A centrifugal pump of the type described above will have the highest efficiency and for many Purposes.  

3.4. Pressure lock function

This construction element serves to flow a fluid from a first area into a second area to leave, with no effect on the first area from the second area, even if in the in the second area there is a higher static pressure than in the first area.

Construction principle

With this construction element, fluid is fed tangentially to a housing screw analogous to the above shown centrifugal pump. However, the fluid flow is not passed to a drain pipe. The housing Rather, snail is continued on an approximately circular path with an almost constant radius. The cross section, for example, remains the same size for a third of an arc. After that it tapers the cross section to zero within a full circular arc and has openings in this area through which the fluid can flow tangentially into a second area, analogous to the inflow, usually also in pointing in the same direction as this.

Constructional execution

Figure 6, left, shows schematically and exemplarily a pressure lock in a cross-section to the axis (RA). Instead of a housing screw running over a full circular arc, three such housing screws are shown here, for example. A shell screw describes a third of an arc, with its diameter increasing from its smallest to its largest diameter. In this area (A-6) fluid is fed tangentially to the housing screw analogous to the above housing screw (F-5) through a transfer channel analogous to the above (E-5, not shown in Figure 6 on the left). The housing screw is continued in the same direction of rotation on approximately the same radius with approximately the same cross section for a second third of the arc. In this area (B-6) the housing screw has no openings. The cross-section then tapers to zero during the last third of an arc. In this area (C-6) there is again an overflow channel similar to the one above (not shown in Figure 6 on the left).

Figure 6, right, shows a cross-section along the axis. The inlet area (A-6) of this housing screw is arranged on the inside, the outlet area (C-6) on the outside. The arrangement of all areas of the housing screw is shown here by way of example in one plane; these could also be offset from one another. The transfer channels, which bring the fluid flow (D-6) into the screw housing, are shown schematically here. The transfer channels to the smallest and largest diameter of the screw are spatially close together. They are only shown schematically here as two transfer channels, in practice you will choose a more aerodynamic arrangement. In Figure 6, left, the corresponding positions are identified by circles. The outlet area (C-6) of this housing screw is in principle laid out analogously to the inlet area with a corresponding transfer channel for the outflow (E-6) of the fluid. Instead of these three housing screws, a different number could also cover a full circular arc.

Special properties and application

As already shown with the above centrifugal pump, a tangential supply of a fluid into a Casing screw generates a potential swirl current of extraordinary strength. Its continuation in the same Direction of rotation causes only minimal resistance. Through the rectified movements throughout The fluid can be streamed tangentially from the housing screw with an equally insignificant loss divert. Typically, when a fluid is transferred from one container to another Instant pressure equalization tank. However, the pressure in this system mainly consists of back pressure due to the high speeds both radially and axially in the tube. The outlet area practically forms one Elongated cross-section nozzle over a full circular arc. The speed of the fluid in this Nozzle is so high that even a higher static pressure in the fluid-receiving container has no return can have an effect on the flow and pressure conditions of the container which releases the fluid.

With this construction element, an almost absolute blockage is achieved with optimal flow conditions guaranteed a pressure against the current direction. An application example is shown below.

3.5. Potential swirl pump function

This construction element serves to produce a bundle of strong potential swirl currents.

Construction principle

On the one hand, this structural element represents a centrifugal pump. The chambers between the Buckets have a constant or decreasing cross-sectional area from the inside to the outside. The wall The chambers are not completely imaged by the rotor, but partly by the housing or also from a body rotating faster than the rotor. In the following "acceleration rotor" called. The flow in the chambers takes place from the inside out as with a centrifugal pump. In addition, however, the fluid in the chambers becomes increasingly stronger rotation from the inside out offset around the longitudinal axis of the chambers. As a result, fluid is drawn out of the inlet area with strong suction sucked in. On the other hand, this creates extremely strong potential swirl currents on the outlet side each chamber, with this entire bundle of vertebrae additionally showing strong rotation.

These design principles are shown schematically in Figure 7, above. A section of a rotor (RO) of a centrifugal pump is shown on the left, which is to be regarded as rotating clockwise on its axis of rotation (RA). Inside, the entry takes place with a relatively small radius. The fluid flow (A-7) flows through a chamber (B-7) from the inside out to the outlet with a relatively large radius. Instead of curved blades, segments are drawn here which form the walls of the chambers. The chamber (B-7) thus has the same cross-section from the inside to the outside.

Figure 7, top center, shows a longitudinal section (only one half of the symmetrical machine). The walls of the housing (GE) represent the inlet area in which the fluid flow (A-7) enters. The rear part of the rotor (RO) is shown conically in the area of the axis of rotation (RA), so that the fluid flow is deflected in the radial direction. It flows through the chamber (B-7), which is part of the rotor. But only three wall sides of the chamber are represented by the rotor, the fourth wall side is represented by the housing (GE). Figure 7, top right, shows a top view that illustrates this: The rotor (RO) moves relative to the housing (GE). The fluid in the chamber (B-7) rotates about the axis of rotation at the speed of the rotor. However, it is braked on the housing wall and thus also experiences a rotation about the longitudinal axis of the chamber (B-7). The difference in relative speeds between the rotor and the housing increases in proportion to the radius. The rotation of the fluid around the longitudinal axis of the chamber is therefore relatively small on the inside and becomes increasingly stronger on the outside.

Figure 7, middle line on the left, shows another section of a top view. The housing (GE) is fixed, the rotor (RO) rotates (here in the picture from bottom to top). A chamber (C-7) is now shown in the rotor with round walls of the rotor. Part of the chamber wall is in turn formed by the housing. An acceleration rotor (D-7) also rotates about the axis of rotation, but at a higher speed, preferably twice as fast as the rotor. It also forms part of the chamber wall. Due to its higher speed, it accelerates the rotation of the fluid in the chamber about its longitudinal axis. This body is therefore called the "acceleration rotor".

With this concept it is practically achieved that the walls (or parts thereof) of a pipe (or the elongated chamber with a basically round cross section) twist increasingly faster, analogous to Movement of the potential swirl flow. This conception is therefore a representation of a tornado by solid parts.

In an axial plane to the longitudinal axis of the chamber, fluid can rotate at any speed without consequences outward. The situation is completely different if the fluid additionally moves in the direction of the chamber runs along the longitudinal axis. This movement radial to the axis of rotation (RO) is already given due to the Centrifugal force. In addition, baffles could be on the wall of the chamber (B-7) formed by the rotor be attached or grooves, practically cut a thread, but with from the inside to the outside with a larger incline. On the other hand, the wall parts of the rotor should be as smooth as possible so as not to slow down the rotation in the chamber. Especially the pressure side of the rotor walls should be as smooth as possible. Baffles or grooves should only be on the suction side of the rotor wall (G-7) to be appropriate. The walls of the housing and especially the acceleration rotor can get out relatively to promote rotation in the chamber. Due to housing like acceleration rotor whose flat walls exerted pressure on the fluid vortex. This means that all the requirements for Formation of a potential swirl flow in the chambers of the rotor about the longitudinal axis of the chamber.  

Instead of the turbulent flows of conventional centrifugal pumps caused by pressure and suction directional movements occur. This has enormous consequences. If there is a potential swirl can form flow and the cross-sectional area of the chambers from the inside to the outside accordingly is reduced, this results in a high velocity of the fluid as it exits the Chamber. If this cross-sectional area is kept relatively the same, then this results in a very strong one Suction in the inlet area. In any case, the throughput of this machine will be much higher than that of conventional centrifugal pumps.

A disadvantage may appear that the fluid is not uniform over the entire outer circumference of the rotor emerges, but in the form of individual pegs. A relative negative pressure develops between these. This could be used to achieve a strong curl of the fluid flow overall. Or its Suction can be used as outlined below.

Constructional execution

Figure 7, middle line on the right, shows a longitudinal section as an example for this potential swirl pump. In the inlet area (on the left in the picture) there is a flow, which expediently already has a corresponding swirl. The outer wall of the fluid flow is always represented by the housing (GE). The rotor (RO) initially has a conical shape in the region of the axis of rotation (FA) in order to deflect the fluid flow in the radial direction. The channels (C-7) are located in the rotor, with only two wall sides being imaged by the rotor. The inner or front wall of the chambers is represented by the accelerator (D-7). The fluid flow leaves the machine (to the right in the picture) here in the axial direction and at the same time rotating around the axis of rotation due to the rotation of the rotor. In addition, each fluid flow from each chamber forms a potential swirl flow around its longitudinal axis.

A further example of this potential swirl pump is shown in Figure 7, lower line of the illustration, on the right a schematic longitudinal section analogous to the previous one. In the inlet area there is a flow with main and secondary flow, such as z. B. is delivered by the vortex generator shown above. The outer wall of the fluid flow as a whole is still imaged by the housing (GE). Inside this is the main flow pipe (F-7). The main and secondary flows are still separated in the rotor (RO). That is why a round wall is installed there, which has a diameter at the back corresponding to the main pipe, which widens towards the front. The main flow is passed through chambers (C-7), with three sides of the wall being imaged by the rotor and one by the acceleration rotor (D-7). The sidestream is passed through chambers (E-7), with three sides of the wall being imaged by the rotor and one by the housing. Figure 7, lower line on the left, shows a corresponding cross-section of the outlet area. The chambers of the main flow (C-7) are offset from the chambers of the secondary flow (E-7), both are separated by the main tube wall (F-7) of the rotor. Potential swirl flow will develop in the same direction of rotation in all chambers. Many other designs according to the above principles are feasible.

Special properties and application

This potential swirl pump combines the advantages of a conventional centrifugal pump with the Advantages of the potential swirl flow. The pressure generated by the rotor is applied to the fluid in the rotor transfer chambers optimally in rotational movement of the fluid. By being larger from the back to the front As the radius of the rotor increases, the fluid experiences centrifugal force and flows off tangentially. By the rotation of the fluid around the longitudinal axis of the chambers forms potential swirl flow with them Momentum. This potential swirl pump is therefore very efficient. It is suitable for Applications of various kinds. B. also in the form of the vortex container described later be used.

3.6. Suction pump function

This construction element serves to create a bundle of potential swirl flows solely due to To generate suction and thus low energy consumption.

Construction principle

An essential feature of this suction pump is that channels are provided on the inner wall of the housing, which have a spiral course from back to front. The channels have an asymmetrical cross section with a tear-off edge. The rotor, on the other hand, always has a round cross-section and its surface should be relatively rough be so that the fluid "adheres". By rotating the rotor, the fluid is also rotating Moves. The radii of the rotor increase from the back to the front, which means that the "liability" of the fluid whose rotation from the back to the increasing speed reached. The fluid strokes over the tear edges of the above channels and causes an additional rotation of the fluid in the channels, whereby potential swirl flow will form. The channels have a relatively steep angle to the rear Rotation axis up, in the middle part a much flatter angle and a little steeper towards the front Angle on. The potential swirl vortex braids leave the machine in axial and tangential directions.

Constructional execution

In Figure 8, above, a longitudinal section through this suction pump is shown schematically and as an example. The fluid flow runs from left to right. The rotor (RO) rotates around the axis of rotation (RA). The rotor always has a round cross-section with a radius that increases from the back to the front. Part of the housing (GE) is the inner wall (A-8), which in principle is also round in cross-section. Its radius is relatively large in the inlet area, decreases towards the center and increases again towards the front. Channels (B-8) are formed on the inner wall (A-8) from back to front. They run in a spiral shape, with the position at the back being relatively steep with respect to the axis of rotation, then becoming flatter towards the center and steeper again at the back. The channels have a small height at the rear compared to the inner wall, which increases towards the center and at the front occupies the entire height of the cross section available for the fluid.

In figure 8, some sections of the cross-section of the rotor (RO), the inner wall (A-8) and the channels (B-8) are shown schematically in the lower display line. The rotation of the rotor is assumed to be clockwise. The tear-off edges of the channels point in this direction of rotation. On the one hand, the channels have the function of baffles, so they could also assume the entire height of the cross-section available to the fluid from the back to the front. On the other hand, an additional potential swirl flow should be able to develop in the channels. In this respect it makes sense that these channels initially form practically only one groove in the inlet area (left in Figure 8), then take on an increasingly greater height in relation to the cross section available to the fluid. Due to the rotation of the fluid (assumed to the right here), it sweeps over the tear-off edges and creates a suction in the channel, which forms a rotational movement of the fluid within the channel (here then directed counterclockwise). As more and more fluid fractions flow into it at an ever increasing rotational speed (in the middle or right in Figure 8), the desired potential swirl flow is formed with the inherent characteristics.

Special properties and application

This suction pump can be operated with minimal energy consumption. There is only friction losses in the bearings of the rotor and by the friction of the fluid on the surfaces of the rotor. The Effect of this suction pump is achieved in that only the requirements for training the Potential swirl current are created and its own dynamic is used. The fluid must Training this flow form will be given enough time and space. That is why this machine build relatively large. However, the efficiency will be correspondingly high. This suction pump will can not build up a lot of pressure, but result in a very gentle delivery of the fluid.

3.7. Vortex container function

With this construction element, gentle swirling becomes a mixture of different components achieved in a fluid or an intensive swirling of a fluid with low energy consumption.

Construction principle

This vortex tank is based on the construction principle of the suction pump described above, the here Fluid delivery takes place in a closed cycle. Alternatively, the design principle Potential swirl pump described above are used, in which case the fluid delivery in one closed cycle takes place.

Constructional execution

A longitudinal section through this vortex container is shown schematically and as an example in Figure 9, right. The desired flow circuit is shown schematically therein. A potential swirl flow is formed in a hyperbolic middle part with narrowing streamlines. At the bottom, the flow flows apart in a spiral on increasing radii and thus returns to the inlet area at the top. This continuous rotational movement in turn consists of vortex braids, thus representing an ideal shape of the vortex flow.

Figure 9, left, schematically shows a longitudinal section through a vortex tank, only half of this symmetrical machine. The rotor (RO) rotates on the axis of rotation (RA). The rotor is represented in the middle by a relatively thin axis, its radius increases at the bottom and its wall runs back upwards on the outside. At the top, the outer wall of the container is represented by the housing (GE). Part of the housing there are baffles (D-9), via which a body (E-9) is firmly connected to the housing. The outer walls of this body represent the inner walls (A-9) of the container. The shape of the rotor walls, the housing walls and the walls (A-9) of the inner body (E-9) are designed so that there is a hyperbolic inlet area , which merges into a return area of decreasing cross-section. On the walls (A-9) there are channels (B-9), the cross sections of which are in principle analogous to those of the suction pump described above. The positioning of these channels in relation to the axis of rotation must be aligned according to the desired basic current directions (e.g. as shown in Figure 9 on the right). The guide plates (D-9) also have a corresponding course.

An optional construction element are baffles or channels (C-9), which are in the outer area of the rotor may be appropriate. These baffles could serve as turbine blades for parts of the for the Drive the rotor to recover energy expended on a large lever. You might as well a special rotor with a different ratio. If channels instead of the baffles (C-9) should be installed, they should be laid out analogously to the channels (B-9), but with their tear-off edges directed against the rotational movement of the fluid. Such channels could also be used for the recovery of Serve energy (if necessary, in turn mounted on a separate rotor) or they could be the other Swirl the fluid.

As an alternative to the principle of the above suction pump, the previously described potential swirl pump could also be based on this Construction elements be vortex containers. There, too, arise in the channels between the rotor and the main Stromrohr or this and the housing walls potential swirl flows, which are described in the above Can be directed to a circuit of the fluid by appropriate shaping.

The facilities required for filling or emptying the container are not shown here because easily possible with known technology.

Special ice properties and application

Like the above suction pump, this vortex tank requires only a small amount due to the low friction losses Use of energy, which may even be partially recovered if appropriately designed.  

The special feature of this machine is that it creates an ideal form of vortex formation. This swirling can take place exclusively by suction, with no "whirlers" being used become. This machine thus meets the requirements such as B. when mixing various ingredients are required in a fluid or to produce colloidal mixtures. With this machine, too The objective of a gentle but intensive fluidization of a fluid is achieved in the best possible way e.g. B. for the production of "Levitated water" or "energetic water" or other is desired.

3.8. Ring swivel holder function

With this construction element, gentle swirling becomes a mixture of different components achieved in a fluid or an intensive swirling of a fluid with low energy consumption. The parts of the fluid are in principle moved on the orbits of a ring vortex.

Construction principle

Figure 10, top left, shows the cross section of a container. The container (A-10) is formed between an outer wall and an inner wall. Both walls have an almost similar shape, but the inner wall has smaller diameters. The container is U-shaped or V-shaped at the bottom, it is symmetrical to its axis of symmetry (B-10). The outer and inner walls converge at the top. This container is partially filled with fluid, e.g. B. with water up to a height of C-10. When this container is rotated around its axis of symmetry, the surface of the fluid has a convex shape.

Figure 10, top right, shows the same container with an inclined axis of symmetry. If this container is set in rotation about its axis of symmetry, the surface of the fluid has a different shape depending on the speed or the respective relation of centrifugal and gravitational force. If this container is rotated relatively slowly, the surface of the fluid will fluctuate between the walls during one revolution. The movement of the fluid with respect to the axis of symmetry can have at most the distance E-10.

This movement can be increased if, in addition to its rotation, the container has 99999 00070 552 001000280000000200012000285919988800040 0002019806507 00004 99880h its symmetry axis is rotated about an axis of rotation. Then both rotary movements overlap. Between the The outer and inner walls of the container can have baffles installed in a curved shape. Then this direction of movement also overlaps the previous movements. The cross sections of the between the Walls and the baffles formed in the container can have a cross-section in the shape above of a ring segment have a greater length than width, but with a rectangular cross section greater height than width. The movement of the fluid is then additionally spiraled. From the overlay of all For each fluid part, there is an approximation of a path course similar to that in a ring vortex.  

Constructional execution

In Figure 10, middle line of the illustration, a longitudinal section through an annular vortex container is shown schematically and as an example. An axis of rotation (RA) is mounted in a housing (GE) so that a rotor (RO) can rotate about this axis of rotation. A container (A-10) corresponding to the basic form described above is rotatably mounted in the rotor, the axis of symmetry (B-10) of the container being at an angle to the axis of rotation (RA). The rotor and container rotate in the same direction. These movements can be synchronized in a known manner via a gear. Here is a schematic and, for example, this gear consists of a ring gear (F-10) of the housing and a gear (G-10) of the container Darge. At the bottom, the container is rotatably mounted in a bearing (H-10) of the rotor. This bearing (H-10) protrudes into the container. A channel (I-10) is incorporated in this bearing, which allows or controls the flow of the fluid from one side of the container to the other.

Baffles are installed between the walls of the container. Figure 10, bottom left, schematically shows a top view of an annular vortex tank in the direction of its axis of symmetry (B-10). The container (A-10) should turn clockwise. The baffles (J-10) are basically shaped so that they are curved from the outside to the inside in the direction of rotation of the container. The baffles must be installed between the walls of the container at least in the area in which the surfaces of the fluid move. The baffles in the bottom of the container extend close to the bearing (H-10). The upper part of the container only serves to balance the pressure, e.g. B. the air above the water. Baffles are therefore not required there. On the other hand, the guide plates could also be brought together at the top. However, each channel formed between the walls and baffles could also be closed at the top. When the fluid flows into such a channel, a relative overpressure then forms at the top of this channel. If the fluid flows out of such a channel, this flow is supported by the reduction of this relative overpressure.

In Figure 10, bottom center, is a schematic and exemplary again a top view of a ring vortex container on a somewhat enlarged scale, but only shown in part. The rotor (RO) rotates clockwise around the axis of rotation (RA). The container (A-10) also rotates clockwise about its axis of symmetry (B-10). The baffles (J-10) of the container run in a spiral from the outside in. The container is supported by the bearing (H-10) of the rotor at the bottom center of the axis of symmetry. A channel (I-10) is incorporated in this bearing which allows the fluid to move from one side of the container to the other. Here, for example, this channel is designed so that a flow from direction K-10 can flow through the bearing channel (I-10) towards L-10.

In order to achieve a controlled sequence of movements in the bottom of the container, it is therefore advisable to do so Unit of time only a flow from one or more specific channels of the container into one or several other specific channels is given.  

Instead of a round container with many channels, a container could only consist of the shape corresponding to one channel. Figure 10, bottom right, shows a schematic and exemplary top view of such a channel (M-10) in the direction of its axis of symmetry (B-10). It is then no longer necessary to control the flow of movement at the bottom of the container through the above channel (I-10). This container channel then has a continuous course from top-outside to bottom-center to top-outside. Its cross section could also be round. However, if the cross-section is in principle rectangular in shape and coiled, this causes an additional rotation of the fluid. Several such channels could be arranged on an axis of symmetry in a different axial plane.

Figure 10, middle line, shows two containers. Of course, three or more containers could also be mounted on the rotor. The surfaces of the fluid are drawn as thick lines in the containers. That of the left container could, for example, indicate a fluid level as it could be given just before the flow in this sector. The surfaces of the fluid in the right container, for example, could indicate the fluid level shortly after the flow in this sector has ended.

The facilities required for filling and emptying the container are not shown here because with conventional means easily feasible.

Special properties and application

In this ring vortex tank, fluid is rotated, accelerated and decelerated raised against gravitational force and flows downward due to gravitational force. All this power effects cancel each other out. To operate this vortex tank is only in the start phase special energy expenditure required, after that only to overcome the friction. This ring vortex container can therefore only be designed for manual drive using a hand crank.

Due to the basic shape of the container and the superposition of the rotary movements of the container that of the rotor can be achieved that in the upward-facing sector of a container only one low centrifugal force is given, while the gravitational force corresponds to the height of the fluid column created the pressure down in this sector. In the outwardly facing sector of a container, this becomes Fluid accelerates strongly, whereby the fluid therein is exposed to a corresponding centrifugal force is. The fluid in the container will therefore flow back and forth in the channels. This constant acceleration and Braking is not a harmonious movement in the sense of a continuous flow. Through the Superposition of this movement by the rotation of the container as the rotation of the rotor move however, the parts of the fluid are very harmonious, almost on the basic path of the movements of a Ring vortex. With this construction element, the ring vortex container becomes an ideal form of the fluid technically representable movement.  

This construction element is used, for example, for mixing different components or for producing "Levitated water" and the like can be an ideal instrument. In addition, this intense movement flow in the basic form of a ring vortex open up further application options.

3.9. Pressure pump function

This control element transfers mechanical energy to a fluid by applying almost exclusively pressure is practiced. This pressure pump is particularly suitable for generating high pressure in compressible fluids.

Construction principles

With conventional blades, there is always a pressure side and a suction side. If pressure in the first place the suction side is relatively unproductive. With this pressure pump here are why the blades shaped differently. In the rear area of the pressure pump, the two sides of the blades in about a right angle to each other. In principle, one side is arranged radially, the other side of the In principle, the blade is arranged tangentially. The blades face a steep slope opposite the axis of rotation, an increasingly flatter position towards the front. Create the sides of the blades thus initially an axial movement, but increasingly a centrifugal and tangential movement. in the In the inlet area, these blades form open channels, whereas in the front area, these channels are all-round closed by walls of the rotor. The total rotational energy used as well as the centrifugal force are thus transferred to the fluid. The fluid leaves the machine with a strong rotation movement and less movement in the axial direction.

Constructional execution

In Figure 11, above, a longitudinal section through an exemplary embodiment of a pressure pump is shown schematically, only one half of the symmetrical machine, including schematic and sections of three cross sections. The inlet area (on the left in Figure 11) is shown in a funnel shape through the walls (A-11) of the housing (GE). Baffles (B-11) could be mounted on these walls in order to steer the sucked-in fluid into the desired rotational movement. The rotor (RO) rotates on the axis of rotation (RA). The rotor has a small radius in the inlet area. The blades have a low height there, as shown in Figure 11, middle row of images on the left. These blades practically have the shape of teeth of a gearwheel, which point in the direction of rotation (here assumed clockwise). Due to their position in relation to the axis of rotation, the teeth first point forward, then increasingly in the tangential direction.

The radius of the rotor increases further towards the front, as does the cross-section of the channels (C-11) formed by the blades, as shown in Figure 11, middle row of representations, in the middle, as an example. The radius of the inner walls (A-11) of the housing also increases again in this area. The channels (C-11) that were previously open go further into closed chambers (D-11) of the rotor.

Figure 11, middle row of illustrations on the right, shows schematically how the triangular cross section of the channels changes into an arcuate cross section of the chambers. The inside is raised more than the outside, which means that the fluid is compressed in the centrifugal direction.

The flow within the chambers is of course turbulent. It is advisable to continue the flow after exiting the rotor in spiral paths or in housing screws or in the construction element of the pressure lock described above. Figure 11, below, shows schematically how the fluid can be fed tangentially through a transfer channel (E-11) to a housing screw (F-11), which merges into a second screw (G-11), which in turn is tangential the fluid flow (H-11) can be removed. All of this represents additional, "wetted" surfaces. However, if the fluid pressure generated by this machine is not the end purpose, but ultimately speed is to be achieved, this fluid pressure becomes valuable only through these measures, the friction on curved surfaces being positive works.

Special properties and application

This pressure pump creates turbulent flow like conventional pumps. The mechanical energy is here, however, consistently implemented in fluid pressure. The special shape of the blades creates Already in the inlet area there is a high back pressure in the channels or there is a strong rotation of the fluid prepared. The centrifugal force is also converted in the closed chambers at the front. This Machine does not take advantage of the potential swirl flow, it only provides one Improvement of conventional pumps. The fluid is continuously one during the throughput exposed to higher pressure. This pressure pump will therefore be used especially when high Speed a compressible fluid is to be compressed.

3.10. Combustion chamber function

This construction element is suitable for a significant increase by supplying thermal energy to achieve the speed of potential swirl currents.

Construction principles

If heat is added to a fluid in the context of turbomachines, the objective is not the heat development and not the given pressure increase but ultimately a possible Large mass throughput at the highest possible speed. It was already explained in the pipe invention that this goal can best be achieved by means of potential swirl flow. All of the above Pumps produce this potential swirl flow, or even a previous pressure pump can are produced by appropriate construction elements of the pipe invention or this invention here. As shown there or here, a potential swirl flow can be increased if external pressure is exercised.  

The decisive characteristic of this construction element is the combustion chamber Heat generated pressure from outside to inside on an existing potential swirl to let the flow act.

In principle, all pumps shown above release a potential swirl flow through a ring shaped cross section, the rotational movement in relation to the axial movement always has a large share. As a rule, combustion chambers have swirl plates in order to produce a rotating movement of the fluid. This requirement is therefore optimally met by the pumps of this invention. The annular emerging The fluid jet of these pumps therefore only had to be acted upon from the outside by a heat source and could then be reduced to a smaller radius corresponding to the accelerating one Total fluid flow speed. However, the fluid flow of the pumps will be more advantageous First collect in a screw housing and create the combustion chamber in it.

Constructional execution

In principle, this screw is to be arranged as shown in the pressure lock discussed above or in Figure 6. There, for example, the housing screw consisting of three segments is shown and in a spiral arrangement, essentially on an axial plane. In Fig. 11 bottom right, the pressure lock is shown schematically in an arrangement essentially on a radial plane. There are many combinations of these basic arrangement options.

In Figure 12, the housing screw, including the combustion chamber installed in it, is not shown in cross-section, but the housing screw is seen as rolled on a drawing plane and a basic longitudinal section is shown. This representation can be seen purely schematically, e.g. B. also as far as the dimensions are concerned. Figure 12, illustration column on the left, shows this basic structure of the design of the combustion chamber and its arrangement in this (unrolled) housing screw overall. The auger is basically made up of various sections (A-12 to F-12, marked by auxiliary lines) of different functions.

The inlet area (A-12) is represented by a tube with a cross-section increasing from the rear to the front (G-12), into which the outlet fluid flow (H-12, only shown schematically) of a pump enters tangentially.

The pressure lock area (B-12) is a piece of the housing screw without side openings and with in Principle of constant cross-section. In this area, the entire fluid flow moves with strong potential swirl flow, which acts practically as a check valve.

In combustion chambers, as a rule, the fluid available is initially expanded Cross-section. The cross section expansion area (C-12) corresponds to this objective.  

In the pipe invention, a construction element "pipe cross-section extension" was presented, this one The task is performed as best as possible. With the expansion of the pipe diameter, one is in the middle built, round, pointed to the rear and front, called Insel (I-12), initially only a small one Expansion of the cross-sectional area available to the fluid was achieved. Baffles (J-12) serve the Holder of the island and at the same time strengthen the swirl movement of the fluid through its shape.

At the end of this cross-sectional expansion area (C-12) is a situation analogous to the outlet here given pumps: the fluid is in a rotating and axial movement in one annular channel. The following criteria of the combustion chamber area (D-12) also apply analogously for the above-mentioned alternative, in which the combustion chamber directly to the outlet of the one presented here Pumps was added.

The combustion chamber area (D-12) begins with an increase in the cross-sectional area, which is the same permanent diameter of the pipe is achieved by the smaller radii of the island (I-12) can be. In this section, fuel is supplied (K-12, only shown schematically) or heat energy from its combustion. It will be appropriate to use the amount of air required for combustion delimit with baffles (L-12) or protect the flame with them. The rapid rise in pressure of course, the heat supply initially creates a turbulent molecular movement, although this the principal direction of the potential swirl flow is still impressed. This turmoil like this Pressure must not be applied suddenly inwards or only in the axial direction. That's why they should Baffles (L-12) initially form delimited areas, practically in the form of a pipe section with from behind forward smaller radius. Between these baffles and the outer tube wall, baffles should be in radial direction and with spiral promote the swirl movement. So that we can optimally accelerate the Total potential swirl flow reached.

In the subsequent stabilization area (E-12), on the one hand, afterburning can take place, on the other hand the potential swirl flow can further stabilize there. Although the cross in the combustion chamber area cutting area becomes larger and in principle remains the same size in this stabilization area, there is none Danger of a backlog effect. Due to the significantly increased speed of the Fluid flows, in particular the rotational movement, result in a mass flow rate that is many times higher, that is, a suction on the flowing fluid.

The outlet area (F-12) is to be designed in principle as above for the pressure barrier construction element discussed: the cross-sectional area (M-12) gradually decreases, while the fluid tangential (N-12) drains away. Only the outer parts, i.e. H. the relatively slowest, the fluid flow tapped, so that the potential swirl flow is maintained over long distances.  

In Figure 12, center and right, another example of this construction element is shown schematically and by way of example, with the acceleration of potential swirl flows taking place in two ways.

Figure 12, in the middle, shows a housing screw including combustion chamber analogous to the description above. In this, however, only a subset of the fluid is accelerated by the application of heat, e.g. B. only the secondary current from the potential swirl pump described above. The housing screw of the main stream is shown in Figure 12, right. It initially only consists of the inlet area (A-12) and a pressure lock area (B-12), which can be very short ( Figure 12 shows only the schematic structure). The accelerated fluid of the side stream is fed tangentially from its outlet area into a transfer channel (O-12), from there again tangentially to a mixing area (P-12) of the main stream. The increased pressure from the outside inwards leads to an acceleration of the potential swirl flow of the main flow.

This technology is already in the pipe invention as a construction element "introduction or discharge" described in detail. It is also stated there that the weaker potential swirl flow of the stronger should be mixed. As an alternative to the previous solution, the main stream could therefore also be the stronger sidestream can be added by adding heat.

The entire fluid flow can stabilize in a stabilization area (F-12) and is over the Outlet area (F-12) delivered.

Special properties and application

The construction of this housing screw including combustion chamber with the various sections and functions May seem expensive, but it is the logical solution to the ultimate goal of heat supply in turbomachines: in relation to the use of energy, a maximum mass throughput at maximum To reach speed.

It may seem harmful that there is a lot of "wetted area". However, this does not produce any harmful Friction, but promotes the potential swirl flow. Starting from the inlet of a pump (the one here types) until the end of this machine, the fluid experiences a continuous and harmonious Acceleration in always the same rotational movement as in the axial direction. The unrolled here The housing screw shown will actually be arranged in a circular or spiral shape, that is to say build relatively small. Each of the sections listed here can be dimensioned according to requirements. Through the circular arrangement can e.g. B. the combustion chamber or stabilization area as required for optimal combustion. Even with the elaborate concept of separating the Fluid flow in the secondary and main flow, the construction effort is justifiable. Because this stands the essential The advantage over accelerating only a subset of the fluid with heat and still a serious one To achieve acceleration of the entire fluid mass.  

3.11. Turbine inlet area function

This construction element is suitable for optimally supplying the fluid flow to a turbine.

Construction principles

In the inlet area of turbines such. T. tails attached, which should generate a swirl. If that incoming fluid consists only of turbulent flow, this is not a problem. If that flows If the fluid already has swirl, the angle of attack of the tail unit is problematic. Some of this guide plants are adjustable so that the flow rate can be regulated. In this case too Angle of attack problematic or turbulence is the inevitable result. Furthermore, the angle of attack the blades of conventional turbines are always problematic. Depending on the relation of the speeds of the fluid the direction of the relative movements changes compared to that of the rotor. Theoretically there is only one only direction in which the direction of the rotor movement is identical to the direction of the fluid movement is under all conditions: the tangential direction.

Theoretically, therefore, the flow plates may only be flowed tangentially in the case of fluid flow with swirl and in particular, the transfer of the fluid from parts of the housing to parts of the rotor is therefore only permitted in tangential direction.

The conversion of the kinetic energy into the rotary movement of the rotor takes place by redirecting the fluid current. It makes no sense to have this deflection in the rotor with a small lever arm and less letting force component take place. Due to the design of the inlet area of a turbine rather be ensured that the decisive deflection of the fluid flow through the rotor on one large lever arm takes place.

Essential design principle in the design of the inlet area of a turbine must therefore be the Feed the fluid flow almost tangentially to a rotor with a relatively large radius. One is possible organize a harmonious flow. The inlet area of turbines can meet this goal can be realized in various designs according to and according to the circumstances.

Constructional execution using the example of a river turbine

In a hydropower plant such. B. is usually only a low flow rate of the water or only a limited drop height is available. All the more important is the water in a harmonious movement supply to the turbine. A river power plant usually has a large area for this addition. This should be used to organize a large swirl of water. The water has to in a large diameter inlet area on a parabolic path, horizontal and vertical, of the turbine be fed. The friction on the outer wall of this inlet area causes a centripedal Pressure. The inner wall recedes accordingly. All water parts move with it on one  rolling web. Baffles are corresponding between the outer and inner walls of the inlet area end spiral, whereby the inlet area is divided into channels. These channels have a ring-shaped cross-section at the back, the length of which is greater than its width. This Channels have a rectangular cross-section at the front, the height of which is greater than its width. The water the entry area also moves on a coiled path. It hits in the turbine a relatively thin jet onto a relatively large pressure area of the blades. The water is still there sometimes rolled up more. An intensive eddy current potential is formed in the outlet area. This causes on the one hand a suction on flowing water, on the other hand ensures a quick drain.

Figure 13, above, shows schematically and by way of example a longitudinal section through a river turbine. A head is available between the surfaces of the upper water (OW) and the lower water (UW). The inlet (A-13) at the rear represents a large, circular area. From there, the water is fed to the rotor (RO) in a parabolic manner through channels (B-13) of the inlet area. The rotor is rotatably mounted on the axis of rotation (RA) in the housing (GE). Rotor channels (C-13) are formed between blades in the rotor. The water flows through the outlet area (D-13) into an outlet channel (E-13) into the underwater.

Figure 13, below, schematically shows a section of a top view in the direction of the axis of rotation. The rotor (RO) rotates clockwise around the axis of rotation (RA). Channels (B-13) are installed in the housing (GE), which are limited by the outer and inner walls of the inlet area and by baffles. The guide plates have an increasing curvature in the direction of rotation of the rotor from the outside in. The blades of the rotor, on the other hand, have an increasing curvature from the inside to the outside in the direction of rotation of the rotor.

Special properties of the inlet area of a river turbine

In known river power plants primarily attempts are made to convert the pressure of the water column into mechanical ones Implement rotary motion. The water is supplied to the turbine, e.g. T. in a linear direction. The the preferred direction of movement of all fluids is the rolling movement.

With a river turbine of the above construction principles, the path movement becomes a big one in the inlet area Replica water vortex. The water moves on a rolling track in horizontal and vertical Direction. It hits the rotor almost tangentially in a flat jet. The normal pressure is there the corresponding water column. In addition, however, the friction has caused a directional one Flow occurs in which the majority of the water molecules move in the same direction. The Water has a higher order of all directions of movement when it hits the turbine blades, it in this sense also has a higher density. The delivery of kinetic energy to the blades of the Turbines do not lead to turbulent flow.  

In Fig. 13, below, it is shown as a thick, dashed line that the basically rolling movement also continues within the turbine, the movement component of which now increases in the axial direction. There is also an orderly movement in the outlet area. This river turbine has a relatively large wetted area. The friction on this is not disadvantageous, but causes a higher mass throughput and made a larger share of the total speed potential usable by the higher order of all movements.

Constructional design with axial inflow from a tube

If a turbine is to operate under constant conditions only, the result is relative Known direction of movement of the fluid and the angle of attack of the blades can be designed accordingly become. Only under this condition does it make sense to feed the incoming fluid directly to the rotor to lead. In this case, the rotor practically creates a swirl. Redirecting the fluid flow through the rotor, however, should take place at a relatively large radius. That's why in practically all cases sensible to guide the fluid flow through tail units of the housing so that the fluid almost the rotor is fed tangentially on a relatively large lever arm.

If only turbulent flow is present in the inlet pipe, its axial movement must be almost 90 degrees in the radial direction and again by almost 90 degrees in the tangential direction. Corresponding There are friction losses and the turbulent flow is difficult in a laminar To bring current.

Figure 14, top left, shows a schematic and exemplary view from the back to the front in the direction of the axis of rotation. The fluid flow (A-14) of the inflow pipe is to be directed through baffles in channels (B-14) and thus to be directed in the tangential direction. Figure 14, top right, shows an enlarged view of how the fluid flow from channels (F-14, corresponding to B-14) of the housing (GE) emerges almost tangentially and also almost tangentially into channels (G-14) of the rotor (RO ) entry. The basic direction of this transfer of the fluid flow is shown as a thick, dashed line. The difference between the speed of the fluid in the channel (F-14) and the rotational speed of the rotor is the effective, relative speed. In any case, their direction is almost tangential.

In Figure 14, below, a longitudinal section through a corresponding turbine is shown schematically and as an example. The outer and inner walls of the housing channels are to be designed in such a way that in principle the total cross-sectional area available to the fluid is constant from the rear to the front, so that the speed in the inflow pipe is also retained in the channels. This cross-sectional area could also be reduced from the back to the front so that a nozzle effect occurs, that is to say the speed of the fluid flow when it is transferred to the rotor is as high as possible.

If there is a swirl movement in the inlet pipe, the axial movement component must be reversed as above be directed. The rotational movement of the swirl, however, only has to be raised to a larger radius become. The centrifugal force of a rigid vertebra supports this. Nevertheless, there is turbulence a twisting motion in the form of a rigid vortex. Its outer layers have relatively high motion energy, but only have to travel a relatively short distance when redirecting from an axial to a radial direction Return. The inner layers have to travel the relatively long way of this redirection, but this have relatively little kinetic energy.

Only if there is a potential swirl flow in the inlet pipe can the deflection be carried out without any problems. Because the situation there is reversed: the inner fluid layers of the inflow pipe have higher ones Kinetic energy and can therefore go the outer, long way of this deflection, the outer fluid Layers of the inflow pipe have less kinetic energy and accordingly only need the inner, go shorter path of this redirection.

Figure 14, middle line on the left, shows schematically and exemplarily a view from the back to the front in the direction of the axis of rotation. The fluid flow (A-14) of the inflow tube has a potential swirl flow with a swirl direction in the clockwise direction. This fluid flow can be tapped without friction in the tangential direction by baffles and directed into the channels (C-14 or D-14) of the housing. Due to the deflection of the baffles towards the outside, there is less pressure from outside to inside, the fluid can now slide due to inertia in the tangential direction of larger radii. The current flow so far remains unchanged. Only a few baffles are required. The tangential flow should only be guided safely on the outside by additional baffles.

The channels (D-14) thus correspond to the above channels (B-14 and also F-14), so that the longitudinal section shown in Figure 14, below, can also serve as an example for an inflow due to potential swirl flow.

The objective of an almost tangential transfer of the fluid from the housing to the rotor is not limited to the transfer of the fluid from the inside to the outside. The same direction of the relative speed is always given if the fluid is transferred almost tangentially in a direction parallel to the axis of rotation or in a diagonal direction. In Figure 14, middle display line, right, two options are shown schematically. With H-14 the fluid is transferred parallel to the axis of rotation. At I-14, the cut surface between the housing and the rotor is arranged diagonally.

Special properties with axial inflow from a pipe

Fluid must be deflected in the inlet area of a turbine. A potential swirl flow can be with redirect the least effort and the least resistance. A potential swirl flow has in a pipe  same diameter a higher throughput in the axial direction and in addition it has the movement components in the direction of rotation. A turbine rotates kinetic energy of a fluid implemented. It is logical that the potential swirl flow is the ideal prerequisite for this. With one after The built-in area of a turbine according to the above criteria shows the entire movement potential of the Potential swirl flow on a large lever arm with the best possible mass throughput and the best possible Speed made available to the rotor.

Constructional design with tangential inflow from a pipe

A tangential flow in the inlet area of a turbine is possible without being deflected by baffles, when the inflow pipe leads almost at right angles to an inlet area and tangential around it Is curved around. The fluid is then through the outer wall in a circle or spiral diverted path. The friction on the outer wall then has a positive effect in this sense of rotation. Even a turbulent flow thus gets a better oriented form of movement. However, it is particularly valuable is when there is a potential swirl flow in the inflow tube. The fluid flow should then, as above, be more described, tapped tangentially and flowing into a transfer channel. This in turn should be almost point perpendicular to the wall of the inlet area. So the axial motion components like the swirl component of the potential swirl flow completely into a tangential flow in the inlet area transferred. In principle, it is a feed of the inflow pipe on the outside of the inlet area or alternatively also feasible inside the inlet area.

Figure 15, left-hand column, shows the various options in a schematic and exemplary representation of a longitudinal section of the inlet area. The cross sections are shown accordingly in Figure 15, right-hand display column.

Figure 15, upper line of the illustration, shows the feed of an inflow pipe (A-15) almost perpendicular to the axis of the inlet area. The inflow pipe is curved around the inlet area, thus forming an inflow channel (B-15), the cross-sectional area of which is continuously reduced. The inflow channel is open to the inside, whereby the fluid flows into the inlet area (C-15). The inlet area is in the form of a double-walled tube in which there is a circulating flow on a path almost perpendicular to the axis of this inlet area. From there, the fluid can be supplied to a rotor almost tangentially (not shown here).

A corresponding concept is shown in Figure 15, second display line. Here, however, the inflow pipe (D-15) is fed inside into the inlet area, ie the inflow channel (E-15) releases the fluid flow to the outside into the inlet area (F-15).

This tangential feed can be used for any form of movement in the inflow pipe. In the case of a swirl or potential swirl flow in the inflow tube, its swirl component can also be used in addition. Figure 15, third line of the illustration, shows the external supply of such an inflow in principle.

The fluid of the inflow pipe (G-15) should, as described several times, be tapped tangentially and in a transfer channel can be directed. The swirl is thus set up. Here is this transfer channel (H-15) Aligned almost perpendicular to the wall of the inlet area. Due to the curvature of the inflow pipe the inlet area, the fluid emerges from the transfer duct and in an almost tangential direction Infeed area (I-15). The swirl and axial motion components are in a tangential flow transferred. If there is a clockwise swirl in the inflow tube, the inflow tube should also be clockwise be curved clockwise around the inlet area. Both movements add up and also result in Infeed area a clockwise rotation.

A corresponding concept is shown in Figure 15, lower display line. Here, however, the inflow pipe (J-15) is fed inside into the inlet area, ie the inflow channel (K-15) emits the fluid flow to the outside into the inlet area (L-15).

This concept of using a potential swirl flow can also be used if only one swirl flow is present.

Special properties with tangential inflow from a pipe

A tangential supply of the fluid in the inlet area of a turbine is without the above principles Baffles, d. H. with low friction losses, possible. Even turbulent flow is caused by the einrol lend movement into a more aligned flow. This concept is particularly valuable for Supply of a (potential) swirl flow, because its additional swirl components also without deflection is fed to the desired direction of movement on baffles.

3.12. Exhaust gas turbocharger function

This construction element is suitable for using the kinetic energy of the exhaust gases of an engine by Combustion air is supplied to the cylinders with increased pressure.

Construction principles

The exhaust gas should be discharged from the cylinders so that there is a swirl movement in the exhaust pipe. This is to be fed to a turbine as described above. The pump should be described accordingly a pressure pump and the combustion air into a potential swirl via a housing screw to transfer current. A partial return is always useful with regard to the movement sequence.  

Constructional execution

A longitudinal section through an exhaust gas turbocharger is shown schematically and as an example in Figure 16. A rotor (RO) is rotatably mounted in the housing (GE) about its axis of rotation (RA). The pump (left) and the turbine (right) are on the same axis. The pump is basically designed according to the pressure pump described above. The inlet area to the turbine is basically created according to the previously described tangential inflow from a pipe with (potential) swirl flow, details of these construction elements are described there in each case.

The combustion air is drawn into the inlet area (A-16) of the turbine. It is tooth-shaped Channels (B-16) or closed channels (C-16) of the rotor of the pressure pump detected and in rotary motion transferred. It is essential here that the pressure pump tangentially the combustion air into a housing screw (D-16), in which an intense potential swirl flow arises. In this form of movement is supply the combustion air to the cylinders, e.g. B. in the form of the following rotary valve tube.

It makes sense to pump more combustion air than necessary. The unused amount of air should to be led back. It should be fed to the pressure pump in the axial direction (E-16). Your kinetic Energy is by no means lost, on the contrary, it intensifies the desired one Fluid movement in the inlet area of the pressure pump.

The movement in the exhaust pipe (F-16) should be a swirl movement. The exhaust pipe should be almost vertical to the inlet area of the turbine. The exhaust gases should pass through transfer ducts from the exhaust pipe be directed into the inlet area. The transfer channels should be almost perpendicular to the wall of the inlet area show. The exhaust gases are thus directed almost tangentially into the inlet area. This current can be deflected in the axial direction (H-16) by appropriately shaped blades (G-16) of the rotor.

A portion of the exhaust gas (I-16) should be tapped there and directed back to the beginning of the exhaust pipe be, so that there is a cycle.

Special properties

The pressure pump presented here is particularly suitable for generating increased air pressure. The tangential Lead into a housing screw results in a strong potential swirl flow. Due to the partial repatriation This flow is not destroyed in the pressure pump, but is still promoted.

It is relatively easy to organize a swirl movement in the exhaust pipe. This can be done much easier is more usable in the turbine and also results in a less turbulent behind the turbine Flow for the further discharge of the exhaust gases. Here, too, all movements are partially Return of the exhaust gases stabilized.  

3.13. Rotary valve tube function

This design element is suitable for controlling the fluid throughput in reciprocating piston machines.

Construction principles

Intake and exhaust valves are installed in the cylinder head of conventional reciprocating piston machines and is operated by The combustion air is fed to each cylinder individually or the exhaust gas is removed. Instead of only one pipe should be installed parallel to the engine longitudinal axis for the supply of combustion air to all Cylinder. This rotary valve tube is called "air tube" in the following. Accordingly, only one pipe for discharge of exhaust gases of all cylinders must be installed. This rotary valve pipe is called "exhaust pipe" called. The fluid flows into and out of the cylinder through openings in the jacket of these tubes. These tubes must be rotatably supported and half a turn one turn of the crankshaft To run. The combustion air should move in the form of a potential swirl flow in the air pipe Exhaust gases should move in the form of a swirl flow in the exhaust pipe. More fluid should be pumped are considered necessary so that aliquots of the fluid are returned to a circulatory system form with stable swirl movement or potential swirl movement.

Figure 17 shows a schematic top view of a reciprocating piston engine. The three circles in the middle represent three cylinders. The rotary valve tubes are highlighted by thick lines. The air pipe is at the top, the exhaust pipe at the bottom. The exhaust gas turbocharger pressure pump described above could deliver the fluid to the air pipe. The fluid flow of the exhaust pipe could be supplied to the turbine of this exhaust gas turbocharger.

Alternatively, a pre-swirl generator is connected upstream of the air pipe. This construction element before swirl generator is described in detail above. As an alternative to the exhaust gas turbocharger above, here is the exhaust pipe immediately followed by a turbine.

Constructional execution

The various functional elements are only shown schematically in Figure 17. The following components of the housing (GE) and the rotary valve tubes serve principally for the fluid circuit: Combustion air is drawn in in an inlet area (A-17). Fluid is accelerated by the lamellar blades of a pre-swirl generator (B-17) and supplied to the air pipe (C-17) in the form of a potential swirl flow. The air tube rotates at half the engine crankshaft speed. This is easy to do, so a corresponding gear is not shown here. If the pre-swirl generator is rigidly connected to the air pipe, as shown schematically here, a corresponding amount of air is conveyed. If additional charging is desired, there should be no rigid connection between the air pipe and pre-swirl generator, but the pre-swirl generator should have a higher speed due to a gear ratio.

Combustion air flows through openings in the jacket of the air pipe through inlet openings (D-17) of the Cylinders in this one in the intake stroke. In the exhaust cycle, the exhaust gases leave through exhaust openings (E-17) Cylinder and flow through openings in the jacket of the exhaust pipe (F-17) into this. This transition is designed so that there is a swirl movement in the exhaust pipe. This twist can be achieved by shoveling (G-17) a turbine. As shown schematically here, this turbine can be firmly connected to the exhaust pipe. The exhaust pipe rotates at half the engine crankshaft speed. This is again easy to do, a corresponding gear is therefore not shown here. The turbine could again designed or translated differently. The exhaust gas becomes more functional in the outlet area (H-17) elements forwarded.

More fluid should be pumped than is required in the previous process. Dam is schematic here shown that at the end of the air pipe (C-17) excess combustion air through bends (L-17) or Pipes are returned to the inlet area (A-17). The supply line there (M-17) should be tangential take place so that the desired rotary movement is already initiated in the inlet area. The kinetic energy The amount of air returned is therefore not lost, on the contrary, it promotes the desired one Movements. Corresponding subsets of the should also be at the end of the exhaust pipe (F-17) Exhaust gases are discharged and returned (I-17, J-17 and K-17). The diversion should follow the criteria the discharge of partial fluid flows of the pipe invention. This diversion is here at the end of Exhaust pipe and shown in front of the turbine. The recirculated exhaust gas subset could also after the Turbine can be tapped. A third form of return is only shown schematically here (N-17): Partial quantities of the exhaust gas could also be returned to the combustion air circuit.

Figure 18, top left, shows a schematic and exemplary cross-section through the cylinder head of an engine. The recess of the cylinder (A-18) is located in the housing (GE), in which a piston (B-18) is located at top dead center. Round recesses are provided in the housing to accommodate the air pipe (E-18) and the exhaust pipe (G-18). The cylinder recess has an opening (C-18) in relation to the air tube recess and a corresponding opening (D-18) in relation to the exhaust gas recess.

In their recesses, the air pipe and the exhaust pipe rotate in the same direction at half the speed of the Crankshaft of the engine. Fluid moves in the same direction within the air pipe as the exhaust pipe Swirl (F-18 and H-18). These tubes have openings on the jacket through which fluid enters the cylinder can flow or is received from it. For example, here is a situation at the end of the Exhaust stroke shown. The outlet opening (D-17) has just been closed again by the outside wall of the exhaust pipe, the inlet opening (C-17) is next through the rotation of the air pipe open. Air pipe and exhaust pipe are formed by an inner wall and an outer wall. The The cross-sectional area available to the fluid will generally be larger in the exhaust pipe than in the air pipe.  

In principle, this area in the air pipe will decrease from the back to the front and will increase in the exhaust pipe. The openings on the casing of a pipe must be offset according to the cycle sequence for each cylinder. In Figure 18, top right, a cross-section through an air tube from the previous three-cylinder engine is shown schematically and as an example. The three openings on the jacket (I-18, J-18, K-18) must then be offset by 120 degrees each. The respective three cross-sectional areas are highlighted by lines of different thickness.

In Fig. 18, middle line, five cylinders (L-18) of a five-cylinder engine are shown schematically in cross section. The inlet opening (N-18, corresponding to C-18) is shown. Below this, the jacket development of the air tube is shown schematically, each quarter of the jacket corresponds to one of the four cycles (O-18, P-18, Q-18, R-18 of the left cylinder). The basic direction of the swirl movement is shown by oblique auxiliary lines. The openings on the jacket (M-18) must be arranged in the way that corresponds to the desired sequence. If the jacket moves from bottom to top with respect to the cylinder opening, z. B. reaches a firing order of cylinders 1-3-5-2-4 .

In Figure 18, below, the course of an inner wall (S-18) in relation to the outer wall (T-18) of the air pipe is shown schematically and as an example. In principle, the distance between the inner and outer walls increases from the back to the front. This room can e.g. B. can also be used for cooling purposes. The inner wall has a wavy contour, which runs spirally from the back to the front. The fluid moves in these rounded grooves in the axial direction as well as in the direction of rotation. The flow swings immediately in the pipe, after a jacket opening in the direction of the pipe center, in front of a jacket opening to the outside. The combustion air is thus optimally fed to the cylinder opening. The same applies to the exhaust pipe.

Special properties

These rotary valve tubes replace many conventional elbows and components of the intake and exhaust valves. The opening of the cylinders is large and free to design. The air is before the opening of the Inlet valve in the corresponding direction of movement and can open almost smoothly after opening flow. There is no abrupt braking of the fluid flows after closing an inlet valve. The Fluid only experiences a renewed pressure from the outside in, ie. H. an acceleration in the sense the potential swirl flow. Analogous to this is a continuous fluid flow with swirl in the exhaust pipe given movement. The exhaust gas can enter this swirl tangentially after opening the outlet valve, causes an intensification of the swirl, which in turn causes suction after the high pressure has been released effect on the remaining exhaust gas. A relatively smooth and complete charge change in the Cylinder is guaranteed. This function can be realized with a minimum of components, which also only have rotating movements. These rotary valve tubes can be used for both force and Working machines are used.  

3.14. Inlet and outlet rotary valve tube function

This construction element is suitable for controlling the fluid throughput through reciprocating piston machines.

Construction principles

This construction element is based on the principles of the rotary valve tubes shown above. In this respect apply The above statements are analogous here. Here, in addition, the function of supplying the fluid to Cylinder combined with the function of removing the fluid from the cylinders. Done in a tube both the infeed and the outfeed.

Constructional execution

In Figure 19, top left, a section of a cross-section through a reciprocating piston machine is shown schematically and in a highly simplified manner. In the housing (GE) there is a recess in a cylinder (A-19) in which a piston (B-19) is located at its top dead center. There is a round recess in the housing above the cylinder, in which the rotary valve tube (C-19) rotates. The rotary valve tube has half the speed of the machine. In the following it is assumed that the rotary valve tube rotates clockwise. The cross-section of the rotary valve tube is divided into two areas by a wall. This is called the "partition" below. One area is used to supply fluid to the cylinder, it is called the "air duct" (E-19) in the following. The other area is used to discharge fluids from the cylinder, it is hereinafter referred to as the "exhaust passage" (D-19).

Figure 19, top left, shows the basic situation at the end of the exhaust stroke. The opening of the exhaust duct (D-19) opposite the opening of the cylinder was just closed by turning the rotary valve tube clockwise, the opening of the air duct (E-19) now reaches the opening of the cylinder. The thick line through the diameter of the rotary valve tube schematically represents the partition between the two areas. The thin auxiliary line marks the 90 degrees that are available for one cycle. In principle, the entire cross-section of the rotary valve tube is available to both areas. The openings of the inlet and outlet, however, are limited to a maximum of this 90 degrees of an arc. This illustration only shows this basic arrangement. Nevertheless, it can already be seen here that relatively large openings are available for the gas exchange.

Figure 19, middle and lower display line, shows representations analogous to Figure 18. In Figure 19, middle display line, the five circles represent a top view of the cylinders (F-19) of a five-cylinder engine. The cross-section of the cylinder openings (G-19) could have a rectangular shape, for example. Figure 19, below, shows a jacket development of a rotary valve tube. The partition runs spirally in the rotary valve tube. This is shown on the jacket by the diagonal lines. The air duct (I-19) and the exhaust duct (H-19) are located to the left and right of the partition.

The respective openings of the exhaust gas duct (H-19) are shown below the five cylinders, then those of the air duct (I-19). In this illustration, it is assumed that the jacket of the rotary valve tube moves from the bottom to the top with respect to the cylinder. Who results from this arrangement then a firing order 1-3-5-2-4 .

The cross section of the rotary valve tube should not, as previously assumed, through a straight partition in Form a diameter can be separated into the two channels. The air duct must have a larger one at the rear Cross-sectional area have as front. Conversely, the front exhaust duct requires a larger cross-section area than behind. The partition should be designed accordingly and more aerodynamically efficient Shapes are used.

Figure 19, top right, shows various cross-sections of a rotary valve tube as an example. If the section is perpendicular to the swirl path of the channels, i.e. diagonally to the pipe axis, the round pipe cross section appears as an ellipse. The four cross-sections (I-19, K-19, L-19 and M-19) show an example of the situation of the four cycles, each for the first to fourth cylinders of a four-cylinder engine.

The intake stroke of a first cylinder is shown at J-19. The air duct (N-19) has its largest cross cut surface, through the large opening fluid can flow tangentially and without friction. One turn of the rotary valve tube in the clockwise direction is assumed, but the fluid in the air duct also has a strong swirl in the Clockwise. Both movements in the same direction lead to an optimal filling of the cylinder. Of the Exhaust duct (R-19) requires only a relatively small cross-sectional area in the area of this first cylinder. He up to here only the possible partial amount of exhaust gas has to be recirculated and the exhaust gases of this first cylinder.

At K-19 the compression stroke of a second cylinder is shown. The rotary valve tube has opposite situation J-19 made a 90 degree rotation. In this second cylinder, the cross section area of the air duct (O-19) can be reduced by the partial amount of fluid discharged into the first cylinder. In contrast, the exhaust duct (S-19) only has to be dimensioned such that it opens the exhaust gas of the second cylinder can take. The partition is moved towards the center of the pipe, the rounded shapes of the channels enable or result in a well-directed swirl movement.

The expansion stroke of a third cylinder is shown at L-19. The rotary valve tube has one Rotated 90 degrees from K-19. The cross-sectional area of the air duct (P-19) is now again reduced (compared to previous 0-19). The cross-sectional area of the exhaust duct (T-19) is now significantly expanded (compared to the previous S-19) as well as larger than that of the air duct P-19.  

M-19 shows the exhaust stroke of a fourth cylinder, with the rotary valve tube again turning 90 Degrees to L-19. In the wide opening of the exhaust duct (U-19) the exhaust gas can run smoothly flow in, thereby increasing the swirl movement in the exhaust duct. The cross-sectional area of the air duct must only be dimensioned here so that the subsequent filling of this fourth cylinder can take place. It will also be very useful not to let this air duct end afterwards. Rather, it should Excess quantities of combustion air are carried in this channel and returned to the charge air pump. The advantages of this measure with regard to an optimal movement sequence are addressed several times and or apparently.

These four representations of cross sections (J-19 to M-19) show the basic positions on the one hand of the air and exhaust gas channels during a full rotation of the rotary valve tube, which is the four cycles and thus corresponds to two revolutions of the crankshaft of a four-stroke engine. On the other hand, these four show Representations of cross sections (J-19 to M-19) the basic size relationships of the air or exhaust gas channel from back to front in this machine. The first cylinder was the rear, the fourth the front Called cylinder. The principles of this concept for an engine can be applied analogously to the design of a pump.

Special properties

The advantages of this rotary valve tube correspond to those of the previously described version. Opposite this the supply and discharge of fluid to and from cylinders were combined in one tube. This results in a further reduced construction effort, fewer components, less effort on gear, less mechanical friction and, for example, simplified sealing. On a single axis can the functional elements of a charge pump, the transport of fluids to and from the cylinder, install the intake and exhaust controls and an exhaust gas turbine. There is one from the back to the front directional fluid movement in the form of potential swirl flow or at least swirl flow.

3.15. Reciprocating gear function

This construction is suitable for producing a linear stroke movement of a piston.

Construction principle

A circular disc is eccentrically attached to a rotational axis mounted in the housing. This In the following, the disk is called the "eccentric disk". This eccentric disc can be rotated in another round washer, which is called "connecting rod washer" in the following. The eccentric disc is in the Conrod bearing mounted eccentrically. The eccentricity is the same in each case, i. H. the distance between the Axes of the axis of rotation and the eccentric disc is the same size as the distance between the axes of the Eccentric disc and the connecting rod disc. The speed of the axis of rotation, including the eccentric disc,  and the connecting rod is the same size, but in the opposite direction. The connecting rod is rotatably mounted in the piston. At half a revolution of the axis of rotation, including the eccentric disc, and one counter-rotating, half a turn of the connecting rod, the piston performs a fourfold stroke Way of eccentricity.

This situation is shown schematically in Figure 20, in the top two display lines. The eccentric disc (A-20) is firmly connected to the axis of rotation (RA). This rotates around the axis of the axis of rotation, here clockwise. The situation after a rotation of 30 degrees is shown from figure to figure. On the other hand, the eccentric disc (A-20) is rotatably mounted in the connecting rod disc (B-20), again with the same eccentricity the situation after each rotation by 30 degrees is shown. The respective upper edge of the connecting rod washer is connected from illustration to illustration by a curved line. The distance (C-20) to the axis of rotation (RA) represents the stroke movement. It should be noted that this curve is a straight line in the central area.

Constructional execution

In Figure 20, lower line of the illustration, a cross-section through a motor is shown schematically and as an example. The axis of rotation (RA) is rotatably mounted in the housing (GE). The eccentric disc (D-20, analogous to A-20) is firmly connected to this. The connecting rod (E-20, analog B-20) is rotatably mounted on this. The piston (F-20) is rotatably mounted on this. On the other hand, this is movably mounted in the housing (GE) and can therefore perform linear lifting movements in corresponding recesses in the housing.

As a functional element of the inlet and outlet here is, for example, the inlet and outlet described above Rotary valve tube marked with the two areas of the exhaust duct (H-20) and the air duct (I-20). The rotation of the inlet and outlet rotary valve tube is assumed to be clockwise.

Figure 20, bottom left, shows the situation at the end of the exhaust stroke. The piston (F-20) is at its top dead center, the opening of the cylinder opposite the exhaust duct (H-20) has just closed, while the opening opposite the air duct (I-20) will be opened by the further rotation of the Inlet and outlet rotary valve tube clockwise. The top dead center of the piston (F-20) is reached when both the axis of the eccentric disc and the connecting rod disc are perpendicular to the axis of the axis of rotation.

In picture 20, bottom center, the situation is shown after half a turn of the axis of rotation, and thus also of the eccentric disc, like a half, counter-rotation of the connecting rod. The piston was moved down the stroke. This situation marks the end of the intake stroke. The opening to the air duct does not yet have to be completely closed in order to achieve a "reloading effect".

It is clearly recognizable how the swirl flow in the air duct can flow optimally into the cylinder.

Figure 20, bottom right, shows schematically and as an example how the positions of the rotation axis (RA), eccentric disc (D-20), connecting rod disc (E-20) and piston (F-20) are in an upper, middle and lower position of the reciprocating piston.

The connecting rod disc (E-20) has practically the function of a connecting rod. Like this, it shows two joints. A joint of a connecting rod is rotatably mounted on the crankshaft, the bearing is corresponding here Connecting rod disc on the eccentric disc. The other joint of a connecting rod is rotatably mounted in the piston, here is the bearing of the connecting rod in the piston. The radius of this bearing is in the piston however chosen much larger than a connecting rod. This radius is so large that it is Includes the connecting rod bearing on the eccentric disc. In contrast to a connecting rod, can so that the connecting rod disc moves on a continuous path around the eccentric disc. So that results there is also a stroke in the amount of fourfold eccentricity.

This reciprocating gearbox can be used with both reciprocating engines and pumps. With this Gearboxes could also be used on both sides of the piston in the sense of a boxer engine.

Special properties

This reciprocating gearbox has eccentric rotary movements, but the mass moments are equalized due to opposite movements. There is no connecting rod with various mass moments here, but just a linear stroke. So this machine runs extremely quietly and correspondingly high Speeds are feasible, especially in connection with the above rotary valve tubes. The relative rotation Conditions between the eccentric disc, connecting rod disc and piston point constantly in the same direction. Across from Conventional crank mechanisms have a double lifting height. The torque acts on the eccentric disc. The pressure is transmitted through the connecting rod. The printing direction is by no means only vertical Direction, but given over long rotation phases in the tangential direction to the eccentric disc.

3.16. Four stroke rotary piston engine function

This construction is suitable to represent a four-stroke engine of special quality. This engine points on the one hand pistons and cylinders according to conventional reciprocating pistons and thus their advantages z. B. regarding simple and safe sealing. On the other hand, this motor has the features of a rotation machine and thus their advantages e.g. B. with regard to a smooth run by continuous rotation movements or the relatively simple design of the functional elements for the gas exchange, the burning fuel supply and ignition.  

Construction principle

A rotor is rotatably mounted in the housing about its axis of rotation. This rotor is called the "cylinder" below rotor ". Cylinder recesses are made in the direction of a diameter in the cylinder rotor In these cylinders, a piston can perform a linear stroke movement from one side of the cylinder rotor to to the other side of the cylinder rotor and back. A round disc is rotatably mounted in the center of the piston, which is called "connecting rod washer" in the following. A shaft is rotatable eccentrically in this connecting rod stored, which is called "eccentric shaft" below. This eccentric shaft is part of a crank shaft, which is stored in the housing and rotatable about the axis of rotation. The distance between the The axis of rotation and the axis of the eccentric shaft are hereinafter referred to as "eccentricity". The distance between the axis of the eccentric shaft and the axis of the connecting rod is the same size as this eccentricity The cylinder rotor and the crankshaft rotate at the same speed, but in opposite directions. During a turn around The piston moves 90 degrees.

This situation is shown schematically in Figure 21, left-hand column. Figure 21, top left, shows a cross section with the basic arrangement of the moving parts. A crankshaft (A-21) is mounted in the housing and can be rotated about the axis of rotation (RA). An integral part of this crankshaft is an eccentric shaft (B-21), with a distance between the axis of rotation and the axis of the eccentric shaft, corresponding to the above eccentricity. The eccentric shaft is rotatably mounted in the round connecting rod disc (C-21), this bearing in turn being created with the same eccentricity with respect to the axis of the connecting rod disc. The connecting rod (C-21) is rotatably mounted in the center of the piston (D-21). The piston is movably mounted in the cylinder rotor (E-21) so that the piston (D-21) can perform a linear movement from one side of the cylinder rotor to the other side of the cylinder rotor. The cylinder volumes are shown on both sides of the piston.

Figure 21, top left, shows, for example, the situation in which the piston is at a dead center (left). The cylinder volume between this left side of the piston and the jacket of the cylinder rotor is minimal. On the other hand, on the opposite side of the piston (right), the cylinder volume (F-21) is maximum.

In Figure 21, on the left in the second representation, the situation is shown after the cylinder rotor (E-21) has been rotated clockwise by 45 degrees around the axis of rotation. At the same time, the crankshaft (A-21) rotated 45 degrees counter-clockwise around the axis of rotation. As a result, the eccentric shaft (B-21) now points downward to the left in relation to the axis of rotation. The connecting rod (C-21) is rotatably mounted in the piston (D-21) and is therefore indirectly subject to the rotary movement of the cylinder rotor (E-21). Due to their central bearing in the piston, the connecting rod disc axis is always on the longitudinal axis of the cylinder recess. The connecting rod disc always rotates about its axis in the same direction as the cylinder rotor. The conrod washer, on the other hand, is mounted on the eccentric shaft and is therefore indirectly subject to the rotary movement of the crankshaft. Compared to the previous situation, the connecting rod was turned 90 degrees around its axis.

The piston (D-21) is now in its central position. The volume of the right cylinder (F-21) has halved compared to the top, the left cylinder (G-21) now has a corresponding volume.

Figure 21, on the left in the third illustration, shows, for example, the situation after a further rotation of the cylinder rotor (E-21) by 45 degrees clockwise. The longitudinal axis of the cylinder now points in the vertical direction. Accordingly, the crankshaft (A-21) has rotated counterclockwise by a further 45 degrees. The eccentric shaft (B-21) now also points vertically downwards. The connecting rod disc (C-21) has also rotated accordingly and points vertically downwards. The piston (D-21) is now again at a (lower) dead center. The volume of the previously right (now lower) cylinder (F-21) is now minimal, the volume of the previously left (now upper) cylinder (G-21) is now maximum.

Figure 21, bottom left, shows the geometry of these movements. The axis of rotation (RA) is fixed in the housing. On the one hand, the cylinder rotor rotates around them, assumed clockwise here. The cylinder longitudinal axis (ZA-21) rotates clockwise, here by 90 degrees. At the same time, the crankshaft rotates in the opposite direction, so that the eccentric shaft, here the eccentric shaft axis (EA-21), rotates 90 degrees counterclockwise. The connecting rod disc rotates at twice the speed of the cylinder rotor. Its axis moves on the one hand in the direction of rotation of the cylinder rotor, and on the other hand on the longitudinal axis of the cylinder in a linear direction. The axis of the connecting rod disc (PA-21) performs a total of spiraling movements. It can be clearly seen from the corresponding curve shown in Figure 21, bottom left, that the pistons of these machines also have a smooth, harmonious course.

An initially left cylinder shows a minimum on the left, a maximum on the top, and right again minimum and below again a maximum volume, d. H. during a rotation of the cylinder rotor the four cycles of a four-stroke engine are shown. The connecting rod washer functions as a connecting rod rod, is supported or is guided on the one hand by the crankshaft, on the other hand by the piston. Here however, the piston is also subject to a rotary movement in accordance with the movement of the cylinder rotor. In contrast to a connecting rod, the bearings here are nested. In the narrowest space the movement sequences take place and at the same time always in the same rotating movement or on resulting, extraordinarily harmonious path.

Constructional execution

Figure 21, right-hand column, shows schematically and exemplarily an engine of this design. The principle of this concept is shown in cross-section in Figure 21, top right. The crankshaft (A-21) is mounted in the housing (GE), rotatably mounted around the axis of rotation. The eccentric shaft (B-21) is an integral part of the crankshaft. It is attached eccentrically to the axis of rotation. Here is the axis of the eccentric shaft z. B. with respect to the axis of rotation bottom left at an angle of about 22.5 degrees.

The cylinder rotor (E-21) is also mounted in the housing and can also be rotated around the axis of rotation. in the Cylinder rotor are the cutouts for the piston (D-21) or the cylinder (F-21 or G-21). The In this illustration, the longitudinal axis of this cylinder recess has an angle of approximately 22.5 degrees to Horizontal on, corresponding to the eccentric shaft, but in the opposite direction. In the middle of the piston (D-21) the connecting rod disc (C-21) is rotatably mounted. The connecting rod is on the other hand rotatably mounted on the Eccentric shaft with corresponding eccentricity between the axis of the connecting rod, the axis of the eccentric wave like between this and the axis of rotation.

If a rotation of the cylindrical rotor (E-21) is assumed to be clockwise, the piston (D-21) just left his dead center. The left cylinder (G-21) is, for example, in the intake stroke. The combustion air can flow into the cylinder through the intake port (H-21). There is a big one flat opening available. The inlet channel is shown here, for example, as a round channel, which runs diagonally to the axial plane, so its cross section appears elliptical here. In one such an inlet duct will be useful to bring the combustion air in with a swirl flow, with what the best possible friction-free and optimal loading of the cylinder can be achieved.

As the cylinder rotor (E-21) continues to rotate, the cylinder G-21 becomes vertical Position have reached the maximum volume, i.e. have completed the intake stroke. Another Rotation by 90 degrees then represents the compression stroke of this cylinder, which then points to the right will reach its smallest volume. There the supply and ignition of the fuel can take place, what is only shown schematically here (I-21). Another 90 degree rotation represents the expansion stroke, at which the cylinder will have reached its largest volume pointing vertically downwards. The remaining 90 degrees of rotation represent the exhaust stroke at which the exhaust gases escape into the exhaust duct (I-21) can, again through a large opening and again if possible opening into a swirl flow.

From this description it is apparent that the opposite cylinder (F-21) is 90 degrees staggered sequence of clocks will perform. When the cylinder G-21 is at its minimum volume, the cylinder F-21 has its maximum and vice versa its minimum when the cylinder G-21 has maximum volume. The cylinders can very well be on an axial plane with respect to the Axis of rotation must be arranged, the openings of the cylinders must be on the outer surface of the cylinder rotor however, be arranged on a different axial plane. Likewise, the functional elements of the and outlets such as the supply and ignition of the fuel for the two cylinders in the housing be arranged different axial level and also offset by 90 degrees.

Figure 21, right, middle representation, shows schematically a longitudinal section through an engine of this design. The crankshaft (A-21) is mounted in the housing (GE) and can be rotated about the axis of rotation (RA). Part of this crankshaft is the eccentric shaft (B-21), which is arranged eccentrically to the axis of rotation. Shown are two such eccentric shafts (B-21), pointing upwards to the left in the plane of the drawing, standing at the bottom center of the axis of rotation, i.e. pointing downwards or upwards in relation to the plane of the drawing.

The cylinder rotor (E-21) is also mounted in the housing (GE), also rotatable about the axis of rotation (RA). Shown are two recesses in the cylinder rotor for receiving the piston (D-21), horizontally at the top Pointing to the drawing plane, pointing perpendicular to the drawing plane below. In the piston (D-21) as on the The connecting rod (C-21) is rotatably mounted on the eccentric shaft (B-21). The piston (D-21) is at the top in a dead center (left) so that the cylinder (F-21) has its maximum volume.

In this illustration, a transmission for controlling the counter is also shown schematically and by way of example sensible rotation of the cylinder rotor and the crankshaft. The cylinder rotor (E-21) has a tooth for this wreath (K-21). A gear rim (M-21) corresponding radius is firmly connected to the crankshaft (A-21) Both are in mesh with a gear (L-21), which is rotatably mounted in the housing (GE). So that will same speed with opposite direction of rotation of the axis of rotation compared to the cylinder rotor. This facility can be created several times, here z. B. it is shown on the right and left. The function this transmission can also be realized with other known technology. The performance of the engine can increase the axis of rotation can be tapped.

Already with two cylinder recesses, which are arranged perpendicular to each other, an almost completely balanced engine can be built. In Figure 21, bottom right, the jacket processing of such a cylindrical rotor is shown schematically. The vertical, thin auxiliary lines mark the four bars (from left to right). Four cylinders (N-21 to Q-21, from top to bottom) are shown. Two of the four cylinders (N-21 and 0-21 as well as P-21 and Q-21) are located on an axial plane, which is shown by the thick, dashed lines. The openings (R-21) of the two opposing cylinders of an axial plane are to be arranged offset by 180 degrees each and must be created on a different axial plane. Here these cylinder openings (R-21) are shown schematically by rectangles, left and right of the dashed thin lines. The openings (S-21) of the two cylinders of the second cylinder recess should be created with a total of four cylinders so that all cylinder openings are offset by 90 degrees.

Accordingly, the functional elements of the inlet and outlet such as the fuel supply and the ignition be created in the housing be staggered. For example, here are only the openings of the Housing for the inlet shown as ovals (I-21). These inlet openings could be through an inlet duct be connected, which was then run around the rotor shell in a spiral shape. The offs are analogous to this create openings or an outlet channel. And analogously, the functional elements are the fuel supply or to arrange the ignition.  

Special properties

This four-stroke rotary piston engine is an engine in which the process runs in four cycles, that is the advantages of a four-stroke engine are given. This engine works with conventional pistons, however, a rectangular cross section is preferable because of the better use of space. The before Parts of the reciprocating piston with regard to a relatively simple and secure seal are given in any case. This Motor is based on a gearbox, which controls all necessary movements in the smallest of spaces. It gives only continuous rotary movements in the same direction. Only from the combination these rotary movements result in the stroke movement of the piston. But this also does not lead in the room linear motion with abrupt accelerations, but moves continuously on one except neat harmonic path. This engine is a rotary machine, instead of conventional valves to build the functional elements much easier and safer. This engine has one revolution of the crankshaft double the number of work cycles. This engine can with a much higher speed normal reciprocating pistons motors are driven. An engine of this type with four cylinders has only eight moving parts. If such a motor is built with a diameter of 20 cm and the same length, it corresponds in terms of smooth running and performance of today's eight-cylinder engine with a displacement of three to four liters.

One characteristic is particularly noteworthy: with a connecting rod, the pressure in the cylinder is only transmitted to the crank mechanism over a limited distance with a long lever arm and in the tangential direction. At the same time there is always an unproductive pressure of the piston on its guidance in the cylinder. Instead of a connecting rod, the force is transmitted through the connecting rod and thus to the crankshaft and at the same time to the cylinder wall and thus the cylinder rotor. Due to the opposite movement of the crankshaft and cylinder rotor, both force components are used productively. Already in the initial phase of the expansion stroke, i.e. at relatively high pressure, e.g. B. in a position accordingly Figure 21, top right, the crankshaft force component already in the tangential direction with respect to the axis of rotation. The cylinder wall force component always acts in the tangential direction and over long distances on a relatively long lever arm. The work cycle of this engine will therefore deliver a comparatively extraordinarily high torque even with a relatively low eccentricity.

3.17. Rotary piston gear function

This construction is suitable for producing a linear stroke movement of a piston, whereby the piston rotates about an axis of rotation.

Construction principle

A rotor is rotatably mounted in the housing about its axis of rotation. This rotor is called the "cylinder" below rotor ". In the cylinder rotor, cylinder cutouts are made in the direction of a diameter, in which a piston can perform a linear stroke movement from one side of the cylinder rotor to other side of the cylinder rotor and back. A round disc is mounted in the center of the piston  the following "eccentric disk" is called. This eccentric disc is firmly connected to a shaft, which hereinafter referred to as "eccentric shaft". The eccentric disc is eccentric on the eccentric shaft assembled. The distance between the axis of the eccentric disc and the axis of the eccentric shaft is in hereinafter called "eccentricity". The eccentric shaft is rotatably mounted in the housing. Between the axis of the The eccentric shaft and the axis of rotation are given a distance corresponding to the previous eccentricity.

The cylinder rotor and the eccentric shaft, and thus also the eccentric disc, rotate in the same direction. The eccentric however, shaft rotates at twice the speed of the cylindrical rotor. A gear synchronizes this movement process. With half a revolution of the cylinder rotor, the piston performs a stroke movement of one Side of the cylinder rotor to the other. The piston is preferably used on both sides, i. H. within one Two cylinder volumes are shown in the cylinder recess.

Figure 22, top left, shows schematically and exemplarily cross sections through such a gear. An eccentric shaft (A-22) is rotatably mounted in the housing. An eccentric disc (B-22) is mounted eccentrically on this eccentric shaft. This eccentric disc is rotatable and mounted in the center of a piston (C-22). This piston is mounted in recesses in the cylinder rotor (E-22) so that it can perform a linear movement on a diameter of the cylinder rotor (D-22). The cylinder rotor is rotatably mounted in the housing around its axis of rotation (RA). The same eccentricity is given between this axis of rotation and the axis of the eccentric shaft (A-22) and between the axes of the eccentric shaft and the eccentric disc.

Figure 22, top left, shows four situations (G-22 to J-22). The cylinder rotor rotates clockwise by 45 degrees from picture to picture. At the same time, the eccentric shaft rotates clockwise by 90 degrees from picture to picture. The cylinder E-22 has its largest volume at G-22. In the course of half a turn of the cylinder rotor (via H-22, I-22, J-22 back to G-22) this volume decreases to the smallest volume. At the same time, conversely, on the other side of the piston, a cylinder F-22 has increasing volume.

Figure 22, third line on the left, shows the geometry of this gearbox. The same distance exists between the axis of rotation (RA) and the eccentric shaft axis (EA-22) as between the eccentric shaft axis (EA-22) and the eccentric disc axis (BA-22). The eccentric shaft rotates clockwise so that the eccentric disc axis z. B. comes in the position of BB-22, ie has made a rotation around EA in the angle of BA-EA-BB. The longitudinal axis of the piston then points from RA-22 towards BB-22, ie the cylinder rotor must have rotated at an angle from BA-RA-BB. It is obvious that this angle of rotation of the cylindrical rotor is always half as large as the angle of rotation of the eccentric shaft. If both elements are supported by a corresponding gear, the piston slides easily in the cylinder recess of the cylinder rotor.

In Figure 22, right-hand column of the illustration, longitudinal sections through this rotary piston transmission are shown schematically and in sections. Figure 22, top right, shows the eccentric shaft (A-22) and the eccentric disc (B-22), which is rotatably mounted in the piston (C-22). Above the eccentric disc (B-22) points to the right, the piston (C-22) is in a central lifting position, such as e.g. B. at I-22 represents Darge. Below this is the situation according to G-22. The eccentric disk points to the left, and the piston is also at a dead center on the left.

Figure 22, center right, shows the cylinder rotor (D-22) in corresponding positions, for example. At the top, the piston can move in the cylinder recesses perpendicular to the plane of the drawing, at the bottom the piston can move in the plane of the drawing. It is also shown here that the cylinder rotor must have a round recess in the middle so that the eccentric shaft can rotate relative to the cylinder rotor.

In Figure 22, bottom right, these two construction elements are shown assembled, schematically and, for example, their storage in the housing as well as a gearbox for coordinating the movements. The cylinder rotor (D-22) is rotatably mounted in the housing (GE), as is the eccentric shaft (A-22). An inwardly facing ring gear (K-22) is firmly connected to the cylinder rotor (D-22). A gearwheel (L-22) is fixedly connected to the eccentric shaft (A-22) or this eccentric shaft is shaped there as a gearwheel. The gear (L-22) is in mesh with the ring gear (K-22). The gear rim has twice the radius of the gear. The eccentric shaft is therefore twice as fast as the cylinder rotor. The machine can be driven or driven, for example, on the eccentric shaft. This transmission is only shown schematically and by way of example and can be implemented in a variety of ways using known technology. The required openings in the housing are not shown here.

In Figure 22, bottom left, is a schematic cross section through such a rotary piston transmission Darge presents. The cylinder rotor (D-22) is in a position analogous to I-22. A clockwise rotation is assumed, as is pressure or a fluid flow in the inlet area (M-22). As a result, pressure is exerted on the piston (C-22) and a torque is thus exerted on the eccentric disc (B-22) or the eccentric shaft (A-22). However, it can also be clearly seen that pressure is preferably exerted on the inner wall (right in the illustration) of the cylindrical rotor (D-22). This torque acts on a large lever arm, up to four times the eccentricity.

Special properties

The operation of this machine is best comparable to that of an impeller. The power transmission or force effect is in no way conveyed solely by the pistons, but to a considerable extent the inner walls of the cylinder rotor act like blades. Although these are completely flat, there is a harmonious fluid flow. The thick, dashed lines in Figure 22, bottom left, represent, for example, an outer and an inner streamline. The fluid either flows through the machine in a parabolic path or in a path that rolls in and out. It should also be noted that the inlet and outlet openings of the cylinders can be made extremely large. It is also noteworthy that almost half of the cross-sectional area of the cylinder rotor is available as an effective cylinder area. This rotary piston transmission combines the advantages of conventional pistons with the advantages of rotary machines. Both the cylinder rotor and the eccentric shaft including the eccentric disc and the piston are in continuous, concentric rotary movements. Only a single gear engagement is required as a gear. This rotary piston gearbox will therefore be used extremely advantageously in different machines, both as a pump and as a turbine.

3.18. Rotary piston machine function

This construction element is suitable for fulfilling the function of a pump or a turbine.

Construction principle

This machine is based on the above rotary piston transmission. The descriptions there apply analogously here. The functional sketch shown in Fig. 22, bottom left, already shows a feed pump for a non-compressible fluid. If you want to work with compressible fluid, only the openings on the cylinder or the housing have to be designed in a suitable manner compared to this schematic diagram. In the case of a pump, the inlet must be relatively large and the outlet must be dimensioned relatively small, and vice versa in the case of a turbine. In addition, in the case of a turbine, the blade effect is to be used in that the piston surface is shaped like a blade.

Constructional execution

Figure 23, upper line of the illustration, shows the cross-section of a pump schematically and as an example. In Fig. 23, top left, the various functional elements are initially shown and labeled. The eccentric shaft (A-23) is rotatably mounted in the housing (GE). The eccentric disc (B-21) is firmly connected to this. This eccentric disc is rotatably mounted in the center of the piston (C-23). This piston is mounted in a cylinder rotor (D-23) so that it can perform linear movements from one side of the cylinder rotor to the other and back. This cylinder rotor has corresponding cutouts on a diameter in which the piston can move or in which the volume of the cylinders is shown. This cylinder rotor is mounted in the housing and can be rotated around the axis of rotation (RA). There is a distance between the axis of rotation and the axis of the eccentric shaft, which is referred to below as "eccentricity". There is a distance corresponding to this eccentricity between the axis of the eccentric shaft and the axis of the eccentric disk.

The cylinders (E-23 or F-23) are not with their entire cylinder cross-section compared to the housing open area. Here, the openings are limited to approximately one sixth of this area, for example.  

Figure 23, top left, shows a situation in which the cylinder F-23 has almost reached its minimum volume. A rotation of the cylinder rotor (D-23) clockwise is assumed here. The compressed fluid can be discharged through the opening in the cylinder and through the opening in the housing into a channel (G-23). This channel is referred to below as the "outlet channel". The compressed fluid is preferably introduced into this outlet channel in the tangential direction, so that a potential swirl flow or at least a strong swirl flow will form in the outlet channel.

In this situation of Figure 23, top left, the opposite cylinder (E-23) has to be almost maximum volume reached. The fluid could rotate in this cylinder for a long distance Cylinder rotor flow through a relatively large channel I-23). This channel is in the hereinafter called "inlet duct".

Figure 23, top right, shows a situation in which the cylinder rotor has rotated clockwise by about 15 degrees. In this horizontal position of the piston in its dead center (left), the cylinder F-23 has reached its minimum volume and the cylinder E-23 has reached its maximum volume. The openings in the cylinders no longer coincide with the openings in the housing. The compression stroke of the left cylinder is now complete, it will execute the intake stroke next. Conversely, the intake stroke of the right cylinder is now complete; it will execute the compression stroke next.

Corresponding cross-sections are shown schematically and exemplarily for a turbine in Figure 23, middle display line. In the case of a turbine, the fluid under pressure should be delivered in a potential swirl flow or at least in a swirl flow in a relatively small inlet duct (J-23 or L-23). The fluid should flow out of this inlet channel in a tangential direction and flow into the cylinder through the opening of the cylinder. The pressure of this fluid is delivered to the eccentric shaft via the piston. The speed of this flow can also be used by hitting the inside wall of the cylinder while it is flowing into the cylinder and causing a torque on the cylinder rotor there. It is advantageous if the inflow also takes place tangentially to the cylinder rotor and, in addition, the surface of the piston (K-23) is shaped like a blade, for. B. as indicated by the dashed lines.

Figure 23, middle display line, right, shows the situation after a rotation of about 15 degrees. The inlet opening of the housing opposite the opening of the cylinder (M-23) should only coincide during a short phase, as shown here for example. The speed of the fluid flow is thus only used in this relatively short phase. The pressure in the expansion phase is then used over a relatively long phase. After completion of this expansion phase, the opening of the cylinder (O-23) reaches a relatively large opening of the housing (P-23), in which the fluid can be discharged without friction. The pressure of a fluid is thus built up in limited mass or volume units, two times in each case one revolution of the cylinder rotor.

In Figure 23, below, a longitudinal section through a rotary piston machine 88462 00070 552 001000280000000200012000285918835100040 0002019806507 00004 88343ine is shown schematically and as an example. The eccentric shaft (A-23) is rotatably mounted in the housing (GE), offset by the above eccentricity with respect to the axis of rotation (RA). The eccentric disc (B-23) is firmly connected to the eccentric shaft. This in turn is centered and rotatably mounted in the piston (C-23). The piston is mounted in the cylinder rotor (D-23) so that it can perform a linear movement. In Figure 23, below, left, the cylinder recess is shown so that the piston can move in the plane of the drawing. The piston is at its top dead center, the cylinder E-23 has reached its largest volume. The cylinder rotor (D-23) is mounted in the housing so that it can rotate around the axis of rotation. The eccentric shaft is formed in a partial area as a gear (S-23), which is in engagement with a ring gear (T-23) of the cylinder rotor. The ring gear has a radius twice as large as that of the gear wheel. The eccentric shaft rotates twice as fast, but in the same direction as the cylinder rotor.

So far, the pistons have always been shown with a rectangular cross section in the drawings. Self ver Of course, the cross-sectional area of the cylinders can also be round, as is the case with conventional lifting cylinders. Ent a piston (R-23) with a round cross-sectional area is shown in the illustration on the right. The room however, use is cheaper with a rectangular cross-section. It will be more advantageous than less round cylinder to create several rectangular cylinders.

The cylinder openings should not be in the center. It is more advantageous to create these openings asym metrically in the direction of rotation of the cylinder rotor. In the figures above in Figure 23, the openings are z. B. so far in the direction of rotation of the cylindrical rotor that only a sufficiently large distance between the inlet and outlet opening of the housing is given. With this arrangement, it is achieved with a pump (e.g. Fig. 23, top left) that in the last phase of the compression the fluid is mostly pressed out of the cylinder into the housing in the direction of rotation of the cylinder rotor. This intensifies the swirl flow desired in the outlet duct (G-23). Conversely, this arrangement of the cylinder opening in a turbine (e.g. Fig. 23, center, left) has the effect that the tangentially flowing flow hits the inside wall of the cylinder and has the desired effect of a blade there.

Special properties

With the design principle of this rotary piston machine it is a pump as well as a turbine to build. Only a few components are required, the machine is light and completely balanced. On Many cylinders can be arranged in the smallest of spaces. This makes it possible that fluid pressure in a con continuous electricity is built up or down. This rotary piston machine can be driven at speeds, which were previously reserved for turbo machines. This rotary piston machine has compared to these the advantage that z. B. a fluid pressure in defined mass or volume units and in certain Scope can be reduced or converted into mechanical energy. Except for the examples presented here various variations of this design principle can be used for different purposes.  

3.19. Rotary stroke engine function

This design element is an engine with rotating reciprocating pistons and continuous combustion.

Construction principle

This engine is based on the above-mentioned rotary piston gear or above-mentioned rotary piston machine and above described combustion chamber. This motor has three functional elements: one pump delivers by one Large number of cylinders a continuous flow of compressed combustion air, in a combustion chamber fuel is continuously supplied and burned, the high pressure and the The speed of the exhaust gases is converted into mechanical energy by a large number of cylinders.

Constructional execution

Figure 24, left-hand column, shows schematically and exemplarily three cross-sections through a motor based on these design principles. In Figure 24, top left, the pump part of this motor is shown schematically and as an example. The construction of this pump is analogous to the rotary piston machine, which is described in detail above. An eccentric shaft (A-24) is rotatably mounted in the housing (GE). An eccentric disc (B-24) is permanently connected to this eccentric shaft. There is a distance between the axes of the eccentric shaft and the eccentric disk, which is called "eccentricity" in the following. The eccentric disc is in turn rotatably mounted in the center of a piston (C-24). The piston is mounted in a cylinder rotor (D-24) so that it can perform linear movements from one side of the cylinder rotor to the other. Corresponding recesses are made in the direction of a diameter in the cylinder rotor, in which the piston can move or through which the volume of the cylinders (E-24 and F-24) is represented. The piston is used on both sides. The cylinder rotor is mounted in the housing and can be rotated around the axis of rotation (RA). The cylinder rotor and the eccentric shaft rotate in the same direction, but the eccentric shaft at twice the speed of the cylinder rotor. A clockwise rotation is assumed in the figures.

Figure 24, top left, shows a situation in which the piston (C-24) is at top dead center. The cylinder F-24 has reached its minimum volume and has completed its compression stroke. Shortly before, at the end of its compression stroke, this cylinder F-24 delivered the compressed combustion air to a duct (G-24), which is called "compressed air duct" in the following. It is advantageous if the fluid flows from the cylinder in the tangential direction into the compressed air channel, so that a strong swirl flow or even potential swirl flow will form there. The cylinder F-24 will now perform an intake stroke by further clockwise rotation. For this purpose, combustion air is sucked in or made available in a duct (H-24), which is called "air duct" in the following. It will again be advantageous if there is a swirl flow in this air duct so that it can flow into the large-area inlet area (I-24) as smoothly as possible. This inlet area is almost 180 degrees.

The cylinder E-24 has just completed this intake stroke and is now entering the compression stroke. With a piston (C-24), twice the compressed fluid is rotated into the cylinder rotor Compressed air duct issued. It will be advantageous to use several pistons, each correspondingly offset to each other, so that an almost continuous fluid flow with strong swirl and high pressure in Compressed air duct is given.

Figure 24, bottom left, shows a corresponding turbine, which is basically designed analogous to the previous pump or corresponds to the rotary piston machine described in detail above. Here exhaust gas of high pressure, high speed and in a swirl flow is delivered in a channel (J-24). This channel is hereinafter referred to as the "pressure exhaust gas channel". This fluid flows into the cylinder through the openings in the housing and in the cylinder. The pressure is passed on to the eccentric shaft via the piston. The inflow of the fluid at high speed also exerts an angular momentum on the cylinder inner wall. This function of a turbine blade is preferably also additionally used by a corresponding, blade-shaped shaping of the piston surface. The openings of the housing and the cylinder are only covering for a short time, the remaining phase serves for the expansion of the fluid, so that the pressure of the fluid is reduced and converted into mechanical kinetic energy.

In Figure 24, bottom left, the cylinder E-24 has completed its expansion stroke, after which the exhaust gas can flow into a channel (K-24) via the large exhaust area (L-24). This channel is called "exhaust gas channel" in the following. Again, it will be advantageous to introduce the exhaust gases tangentially into this exhaust gas duct. There is thus a swirl flow in the exhaust duct, which can be used for further use.

The combustion chamber is arranged between the functional elements of the pump and the turbine. This combustion chamber can be designed differently. However, a combustion chamber of the type detailed above is advantageous. Details of this can be seen above. In Figure 24, center left, a cross-section through a combustion chamber of the type described above is shown schematically and as an example. The compressed air duct (G-24) experiences an expansion of the pipe diameter, although the cross-sectional area initially remains approximately the same size. This is achieved by installing a round, tapered body in the center of the compressed air duct, which was called "island" (N-24) here. The cross section of the compressed air duct has the shape of a ring (M-24). There is a strong swirl flow in this, which acts as a pressure lock. Baffles may support this function.

In this middle functional area, the cylinder rotor can also be mounted in the housing again or the eccentric shaft. All other details can be better represented in the longitudinal section or the top view or to describe.  

Figure 24, right, shows a schematic and exemplary top view of a rotary piston engine. The functional element of the pump is shown at the top, that of the combustion chamber in the middle, and that of the turbine at the bottom. The cylinder rotor (D-24) is mounted in the housing (GE) and can be rotated about the axis of rotation (RA). The eccentric shaft (A-24) is mounted in the housing and can also be rotated around the axis of rotation. An internal ring gear (P-24) is firmly connected to the cylinder rotor. A gearwheel (Q-24) is firmly connected to the eccentric shaft or it is shaped there as a gearwheel. The gear meshes with the ring gear. The gear has a radius that is half as large as that of the ring gear. The eccentric shaft thus rotates in the same direction as the cylinder rotor, but at twice the speed of the latter.

Eccentric disks are permanently mounted on the eccentric shaft, these are mounted centrally and rotatably in pistons movably mounted in recesses of the cylinder rotor, in these recesses the cylinders are removed forms. These construction elements are not shown here. The dashed cross lines are only intended indicate that various cylinders (R-24) are created here, for example seven, each acting on both sides Pistons, i.e. a total of fourteen cylinders in the pump and, accordingly, also in the turbine.

Rather, the functional elements of the housing are highlighted by thick lines in this plan view to schematically mark their basic position or arrangement, for example. The air duct (H-24) extends over all cylinders of the pump. Its inlet areas are almost 180 degrees. From these flows Air in the intake stroke into the cylinders. The eccentric discs must of course be offset from each other are arranged so that the clocks of the intake and compression of the various cylinders in a corresponding manner chronological order are executed. The result of the compression strokes in the form of compressed fluid is released into the compressed air duct (G-24).

Due to the tangential introduction of the fluid into this compressed air duct, this becomes an extraordinary one strong movement component in the direction of swirl. It is pointed out here that in this Compressed air duct so that the phenomenon of a "vortex tube" will occur. In this compressed air duct, that is Fluid have greater heat according to the pressure than the fluid in the air duct, that is, before Compression. However, the measurable temperature of a fluid is only an average, which is the result Molecular movements of very different speeds and energy results. The mass of the fluid will flow (down here) towards the combustion chamber. At the other end of the compressed air duct (here after above) an opening could be made in the middle and the vortex tube phenomenon observed or closed be useful: there will escape fluid with relatively low pressure and extremely low heat. The The temperature of this fluid will be well below that of the fluid in the air duct, even below freezing. This amount of fluid could be returned to the air duct to have the effect of charge air cooling to reach. On the other hand, this amount of fluid could be supplied to a condenser if, for. B. this engine a steam turbine is connected downstream. This phenomenon is well known, vortex tubes are practical Use, the reasons for this phenomenon have not been finally clarified, nor have they been investigated in detail here.  

The compressed air duct (G-24) is shown here with the same radius) to match the one addressed Point out phenomenon. The compressed air duct could also have an increasing radius from the beginning.

In Figure 24, center right, the functional elements of the combustion chamber are shown schematically and as an example. The main characteristic of this combustion chamber is that the pipe diameter of the compressed air duct is expanded here, with a round body (N-24), which is pointed at the front and rear, installed in the center, which is called "island" here. The cross-sectional area available to the fluid thus initially remains the same in principle. The cross section of the compressed air duct (M-24) is ring-shaped in this area. The flat flow with strong swirl in this area acts as a pressure lock. The drawings are only schematic and in no way to scale. The top of the island could e.g. B. reach much further up in the compressed air duct.

In the area of the largest pipe diameter are the functional elements of the fuel supply and the Arrange ignition (O-24). These are not shown in detail here and are based on known technology shape. It is essential, however, that in the further course the fluid is available Cross-sectional area becomes larger, especially due to the decreasing radii of the island. The pipe too cross section must then be reduced. Details of this combustion chamber, e.g. B. the use of baffles are above shown. These measures result in a forward flow with strong swirl component and a potential swirl flow will form in the subsequent pressure exhaust duct (I-24). From this channel, the fluid flows into the cylinders of the turbine, from there into the exhaust gas channel (K-24). These impending swirl flow can be used otherwise, e.g. B. in an exhaust gas turbocharger.

Special properties

This rotary piston engine has all the advantages that are due to the above rotary piston gear or given above rotary piston machine and listed there. It also follows from the clear Separation of the functions of compression, combustion and expansion gives the possibility to optimize them shape, e.g. B. to be able to dimension the pump and turbine differently. Through this separation For example, the compression cylinders remain relatively cold and, on the other hand, become exhausted in the expansion cycle the hot walls of the cylinder do not withdraw energy from the process at an early stage. The continuous scorching On the other hand, there are advantages that are otherwise only available in turbomachinery. Through that After all, the rotating components also reach into the speed ranges, which otherwise flow machines are reserved. However, this engine delivers power even in the lower speed range, because old-established piston technology is used here. And all of this is extraordinary with one low construction costs and feasible with comparatively extremely small dimensions. This rotary piston motor thus represents an engine of completely new quality and dimensions.  

3.20. Tangential turbine function

This construction element is suitable for the kinetic energy or the pressure energy of a fluid to transfer mechanical energy.

Construction principles

The basic design of the blades of a rotor is first discussed here. Principal problems of energy conversion by shovels have to be clarified beforehand. Some schematic representations in Figure 25 are used for this.

In Figure 25, top left, a longitudinal section through a rotor (RO) is shown schematically, which can be rotated about an axis of rotation (RA). In gas or steam turbines, sometimes also in water turbines, a fluid flow (A-25) is directed laterally onto such a rotor disk, the fluid flow is deflected by blades of different designs (for example the basic shapes as shown in B-25 and C-25) , after which the fluid flow leaves the rotor again at the same radius. The problem of this kind of diversion was already discussed in the discussion of the physical basics. Such blades always have a pressure side and a suction side. Only the deflection of the fluid on the pressure side is productive. Any deflection caused by suction is completely worthless. In addition, turbulent flow automatically arises between these blades. For this reason, relatively few blades are used, particularly in water turbines. However, the fluid jet between the blades thus has a relatively large cross-sectional area. As a result, a large part of the energy of the fluid is only indirectly transferred to the rotor, and a considerable part flows through the rotor without giving energy to it. The fluid flow (D-25) is in principle deflected by about 90 degrees in this type of blades. It is advantageous with this type of deflection that this deflection takes place perpendicular to the radius, and the pressure side is in principle parallel to the axis of rotation (represented by the thin auxiliary line).

Figure 25, center left, shows another basic type of rotor or blades. For example, in the case of water turbines, the fluid flow (E-25) is preferably directed onto the rotor in the radial direction and deflected by means of blades, so that the fluid flow leaves the rotor in the axial direction. This type of redirection basically consists of two redirections. In the middle of Figure 25, a cross section through a rotor (RO) is shown, which rotates around the axis of rotation (RA). One redirection is shown in this illustration. The fluid flow (F-25) flowing in from outside points predominantly in the tangential direction and is deflected in the radial direction. This fluid flow (G-25), which basically points in the radial direction, is then deflected in the axial direction. This ensures that the fluid flow is deflected twice around 90 degrees. In principle, a higher proportion of the energy of the fluid can be implemented. It is also advantageous that with this type of deflection, the blades need only have a small profile. The cross-sectional area available to the fluid is therefore relatively constant. The flow between the blades is therefore less turbulent, also because the streamlines have a curved path. On the other hand, it is disadvantageous that this type of deflection results in both radial and axial force components which are unproductive in terms of the desired energy conversion.

The best efficiencies are achieved with free jet turbines. In Figure 25, bottom left, the principle of operation is shown schematically using a longitudinal section or a top view. The fluid flow (H-25) is directed in a tangential direction onto the jacket of the rotor. For reasons of symmetry, it is divided into two streams. Both are deflected by almost 180 degrees. The deflection of the currents (I-25) takes place almost completely perpendicular to the radial direction. Practically only one force component is generated in the desired tangential direction. Another advantage of this type of deflection is that the blades have no suction side, ie the deflection takes place exclusively by means of pressure. The free jet turbines achieve the best efficiency levels. The only disadvantage of known designs of these turbines is that only relatively few blades and also only relatively few nozzles can be used. As a result, there is no continuous frictional connection in the blades and the flow conditions are not constant. Energy is lost at the beginning and at the end of the partial beam hitting the blades. Nevertheless, this type of redirection is in principle the most advantageous and should generally be used.

This type of deflection is by no means restricted to an arrangement of the blades on the jacket of the rotor. In Figure 25, bottom center, it is shown schematically that a fluid flow (I-25) can be directed onto a rotor disk in the tangential direction, and laterally towards the rotor disk. A deflection in the radial direction can then take place within the rotor, shown here inward, in principle also in an outward-directed jet. This fluid flow then pointing in the radial direction can be redirected again to the other in the tangential direction. Here, too, a deflection of a total of approximately 180 degrees is achieved and the deflection takes place perpendicularly to the radius, so that only the desired force component results in the tangential direction.

A basic characteristic of the design of blades or of the rotor according to this invention is therefore that generally a deflection of the fluid flow should be achieved by 180 degrees. In principle, that's only too achieve by two deflections of about 90 degrees.

If in principle the fluid flow is directed tangentially onto the jacket of a rotor, the deflections must be made in principle take place first in the axial direction and then again in the tangential direction, analogous to basic design of the free jet turbines. Essential for this tangential flow onto the jacket A rotor is that the inflow and outflow of the fluid take place on different axial levels.

If the fluid flow is directed tangentially and laterally onto a rotor disc, the Um Steering takes place first in the radial direction and then again in the tangential direction.  

It is therefore essential for this tangential flow against the side wall of a rotor disk that The inflow and outflow of the fluid take place at different radial levels. This principle is partial e.g. B. realized with Francis turbines.

Both construction principles are usually limited to water turbines. Essential characteristic of this The invention is to make these construction principles applicable to gas and steam turbines. To do this, however apply some of the principles already outlined in the physical principles. These are in essential: the fluid must be transferred from the housing to the rotor in an almost tangential direction. In principle, this also applies to fluid flows from the rotor back into the housing. The fluid must be in one Impact relatively thin beam on parts of the rotor so that the kinetic energy of all fluid parts as possible can be delivered directly to the rotor. There must be a continuous flow of fluid also within of the blades are organized, preferably creating or maintaining swirl flows. The The conversion of the energy of the fluid into mechanical energy must only be done by pressure. The shovel must therefore have no suction side. The following criteria meet these criteria provided construction principles and corresponding construction elements.

Figure 25, top right, schematically shows the outer area of a rotor shell (L-25 and M-25), just a section of a cross section. The position of the axis of rotation of this rotor is assumed on the left outside of the drawing. Compared to common turbines, a much higher number of blades has to be installed. The blades consist of an inner wall which has an acute angle to the tangential direction. These inner walls overlap and are connected to a floor. With L-25 this blade shape with straight walls is only shown schematically. At M-25, for example, Darge shows that this bottom can also be rounded.

In Fig. 25, bottom right, the basic blade shape is shown again schematically from three viewing directions on a larger scale. N-25 first identifies the outer area of a rotor shell. To simplify, this coat is shown here without curvature. An inner wall (0-25) has an angle as acute as possible to the jacket. A second inner wall (P-25) is shown, which is overlapping with the first inner wall. Both inner walls are connected by a floor (Q-25). The blade therefore consists of an open area (R-25), which is called "blade opening" in the following. In the area of the overlap of the inner walls, the blade consists of an area (S-25) which is closed to the outside and which is referred to below as the "blade pocket". This shovel pocket ( 5-25 ) is thus formed in cross section by an inner wall (here O-25), the shovel bottom (here Q-25) and a subsequent inner wall (here P-25), which represents the outside of the shovel pocket. Figure 25, at the bottom right, schematically shows the view in the tangential direction of the rotor shell. The bucket opening (R-25) is always on the jacket, the bucket pocket (S-25) with the bucket bottom is located somewhat inside the rotor. The view in the direction of the axis of rotation is shown schematically above this.

Above is the bucket opening (R-25), below the bucket pocket ( 5-25 ). The bottom of this shovel bag is round, which is shown here by the dashed circular arc. A fluid flow entering the blade opening on the left is deflected by about 180 degrees at the bottom and leaves the blade opening on the right. The thick dashed line shows this basic path of the fluid in this type of blade.

In figure 25, bottom right, area N-25 was previously referred to as the outer area of a rotor shell. The blade opening (R-25) thus points outwards on this jacket. The area N-25 can, however, also be viewed as a top view of a rotor disk. Corresponding blade openings would thus be provided on the right side of this rotor disk. The deflection of the fluid then corresponds to the shape shown in Figure 25, bottom center. The fluid flowing there tangentially (J-25) is directed laterally onto the rotor disk. Its deflection by around 180 degrees (K-25) can be carried out in a corresponding manner using the above blade. In principle, this blade shape can therefore be used on the jacket of a cylindrical rotor or on the side surface of a disk-shaped rotor, of course also in combinations thereof or in a diagonal arrangement.

Figure 26 shows some more details of this bucket and some construction variants. Figure 26, top left, shows the outer area of a rotor (RO) with a blade opening (A-26) and a blade pocket (B-26). The bottom of this shovel pocket is rounded, for example. Figure 26, top center, shows a schematic view of the jacket of this rotor. The bottom of the shovel pocket (B-26) is also rounded in this direction. Below this is the view from a tangential direction of this area of the rotor shell. The blade opening is located on the outside of the rotor casing, the blade pocket extends into the rotor, the bottom (B-25) of the blade pocket generally having an inward curve.

Figure 26, top right, shows schematically and, for example, a cross section through the jacket of a rotor. In principle, this section corresponds to a free jet turbine. For reasons of symmetry, two blades (C-26) of the type described above are installed next to one another in the rotor (RO). The axis of rotation is not shown here, it is assumed to lie horizontally above the drawing. In the housing (GE) is the inlet area, in which the fluid flow (D-26) is directed in a tangential direction to the jacket of the rotor. Only the radial component of this direction of movement can be represented in the drawing plane. The tangential motion component is directed from above onto the plane of the drawing. The fluid stream (D-26) is centered on the two blades (C-26), is deflected in their blade pockets and the fluid stream (E-26) emerges from the rotor, again in the tangential direction (again in this view only the radial directional component can be represented).

This design principle has significant advantages over known free jet turbines: the Inflow, the deflection and the outflow represent a continuous fluid flow with constant  Flow conditions. So there is always a frictional connection. There are comparatively many shovels too install, so that in a relatively thin fluid jet, as many fluid parts as possible immediately apply their energy can deliver the rotor. The blades of this design principle point like the well-known free jet turbines no suction sides. In known free jet turbines, energy passes through the beam being deflected or lost to the process due to "splashing water", especially at the beginning and at the end of each partial jet. At If this design principle is shoveled here, the deflection takes place in shovel pockets. The fluid cannot move sideways during the deflection. The entire fluid energy can thus be implemented become.

In the case of liquid or high-density fluid, the energy of this fluid can be converted in a single process step, for example in the case of water turbines, by this unique deflection by approximately 180 degrees. In the case of gas or steam turbines, on the other hand, the pressure energy of these fluids can generally only be adequately used by several process sections. The above design principle is suitable for repeatedly executing such energy conversion processes. This essential variant of this design principle is shown schematically in Figure 26, middle display line.

In Figure 26, middle display line, left, the jacket area is drawn again in accordance with the above illustration. It shows a bucket opening (A-26) and a shovel pocket (B-26). The fluid mainly flows tangentially into the blade opening (here from top right to bottom left), is deflected in the blade pocket and flows out through the blade opening in the opposite direction (at different axial levels, here from bottom left to top right) . To the left of this, an area of the housing (GE) is now shown with corresponding blades, which, however, point in the opposite direction. The fluid flow is received in the blade openings (F-26) of the housing (here from bottom left to top right), deflected in the blade pockets (G-26) of the housing, so that the fluid flow flows through the blade opening (F-26) Leaves the housing again in the opposite direction (here from top right to bottom left). The fluid flow is thus directed against the rotor shell in its original direction. The process of redirection and thus the conversion of energy can thus be repeated.

In Figure 26, middle display line, in the middle, schematic representations are shown analogously to the above. In principle, this blade has a U-shaped cross section when looking at the rotor casing. Below is the shovel pocket (B-26), above the shovel opening. Here it is useful to differentiate between a part of the blade opening in which the fluid flows into the blade. This part is hereinafter referred to as "bucket inlet" (I-26). Correspondingly, there is a part of the blade opening from which the fluid leaves the blade and accordingly this part is hereinafter referred to as the "blade outlet" (J-26). A web (H-26) is drawn between the two parts, which is attached to the jacket throughout. Below this, in accordance with the above illustration, the view is again shown tangential to the rotor casing. Instead of the above-mentioned blade opening (A-26), the blade inlet (I-26) and blade outlet (J-26) are shown here, the web (H-26) between the two. Such webs (H-26) have both the blades of the rotor and those of the housing, they run along the outer surface of the rotor shell and along the opposite housing surface. The required seal between the process sections takes place in or by means of these webs.

In Figure 26, middle line on the right, a schematic cross section in sections shows the basic arrangement of these construction elements to each other. In the housing (GE) there is a channel that serves to supply the fluid flow (K-26). This fluid flow is directed almost tangentially onto the jacket of the rotor (RO). The fluid flows into the blade of the rotor through the blade inlet (I-26), is deflected in the blade pocket (B-26) and leaves the rotor through the blade outlet (J-26). The fluid flow now flows in an almost tangential direction into a corresponding blade of the housing and is deflected in its blade pocket (G-26) by almost 180 degrees. This process can be repeated.

In the drawing it is shown schematically that the webs of the rotor (H-26) like corresponding webs of the Housing can serve as a seal between the process sections. The blades of the case are to be arranged offset by half the blade width relative to the blades of the rotor. Middle and Such webs are to be arranged on the side of the blades. So these seals run around the entire rotor shell and must be created several times. However, it becomes a non-contact seal be perfectly sufficient. The surface of the jacket was basically drawn as a straight line. But it is for example, it is quite possible that this surface is corrugated, so that the entire blade is curved is curved. The blade openings are then not straight and then do not run parallel to the rotation axis, but are curved and positioned diagonally to the axis of rotation, each the blade inlet in different direction than the blade outlet. It practically becomes a labyrinth seal on a large scale achieved, which can be supplemented on the webs by a labyrinth seal on a small scale. A Such execution of this design principle is carried out later.

A major advantage of this arrangement of this type of blades in the rotor and in the housing compared to known blade wheels and tail units is due to the basic path of the fluid flow. Most of the known blade shapes and practically all tail units generate turbulent flows, which are absolutely harmful with regard to the energy conversion. Here, however, the fluid flow is in the same direction and constant, a continued swirl flow is obtained. In principle, the fluid flows from back to front through this machine along the surface line. It also runs through a helical path, partly in the rotor, partly in the housing. This path is easy to follow in Figure 26, middle display line, on the left in cross-section or on the right in longitudinal section. In this illustration, the sequence of movements is as follows: the fluid flows in the rotor at the back-down and at the front-up, then in the housing at the back-up and from-down. It moves on a circular path, which, however, represents an elliptical path due to the relative movement between the rotor and the housing. This flow is certainly more effective than turbulent flows or even abrupt changes in direction of known constructions.

A second essential variant is shown in Figure 26 in the lower display line, again in an analogous representation to the upper and middle display line. The arrangement of such blades on the jacket of a rotor was dealt with in the preceding, the fluid flowing into the rotor from the outside and also flowing out again to the outside. As an alternative to this, such blades can in principle also be designed in such a way that the fluid flow in principle flows from outside to inside or vice versa from inside to outside in the rotor. In this case, the rotor does not have the basic shape of a solid cylinder, but an annular cylinder. This alternative is shown below.

Figure 26, bottom left, shows a top view of the outer area of a rotor shell. This rotor has an outside, as previously assumed on the right, and an inside, now on the left below in this illustration. Blades are shown in this rotor. Fluid flows into the blade opening (L-26, analogous to A-26 above) from the outside, in this illustration from the right. At the bottom of the shovel pocket (M-26, analogous to B-26 above), the fluid is deflected by approximately 180 degrees. The fluid now does not emerge on the same side of the rotor as was previously assumed, but on the other side, i.e. in this illustration inwards or to the left (N-26). The inner wall of the blade is not represented here by a basically flat surface, but points in the blade outlet in a different direction than in the blade inlet. The thick dashed lines indicate this variant compared to the corresponding representations above.

In Figure 26, below, second representation from the left, a top view of this rotor shell is shown schematically. The blade has a generally U-shaped cross section. Below is the shovel pocket (M-26, analogous to the B-26 above). The blade opening above, however, now only has the blade inlet (L-26, analogous to I-26 above). The dashed rectangles show these areas schematically. The corresponding blade outlet (N-26) is not shown in this illustration. It is located to the right of the blade inlet (L-26), but on the other, inner side of the rotor.

Figure 26, below, third representation from the left, schematically shows a view in the tangential direction of this rotor shell. The blade outlet (N-26) now points in the opposite direction to the blade inlet (L-26). The round bottom of the shovel bag (M-26) now has a curved course. The blades shown above previously only had walls on both sides in the blade inlet, which merge into the bottom of the blade pockets at the bottom. This variant of blades additionally has a central wall in the area of the blade openings. In this illustration, it is drawn in as a vertical line. Below it is drawn as a curved line, which results in a streamlined course in the blade inlet (0-26) as well as the blade outlet (P-26). So far, the side walls of the blade openings have been drawn as a straight line. Of course, these can be rounded, as can the bottom of the shovel pockets. The side walls like this middle wall only have to form a straight line directly on the rotor shell.

In Figure 26, bottom right, a section of a cross-section is shown schematically, analogous to the top. In the housing (GE) is a channel in which the fluid flow (Q-26) is directed tangentially from the outside to the jacket of the rotor. It flows through the blade inlet (O-26) into the rotor and is deflected at the bottom of the blade pocket (M-26). The fluid flow (R-26) leaves the rotor through the blade outlet (P-26) inwards. The rotor thus forms an annular cylinder in this area. The axis of rotation is not shown here, its position is assumed to be horizontal above in the drawing.

This concept has all the advantages of the free jet turbine as described above and is shown schematically at the top of Figure 26. An additional advantage here is that the supply and discharge of the fluid are spatially separated. Theoretically, the process can also be repeated with this concept, analogous to the solutions shown in the middle display line in Figure 26. More important, however, is the variant, also mentioned above, of using this type of blades on a rotor disk accordingly. The area of a rotor shown in Figure 26, bottom left, could also be viewed in this sense as a top view of a rotor disk. This variant is shown in detail in Figure 27.

Figure 27, top left, shows a section of a top view of the jacket of a disc-shaped rotor (RO). Shovels of the type presented above are shown. The fluid is directed tangentially to one side of this rotor. It flows through the blade inlet (A-27) into the rotor, is deflected by about 180 degrees in the blade pocket (B-27) and leaves the rotor through the blade outlet (C-27) on the other side of the rotor disk. Figure 27, top center, shows a schematic cross section through a turbine with this type of blades. The rotor (RO) rotates around the axis of rotation (RA). In the housing (GE) is a channel through which the fluid flow (D-27) enters the bucket inlet (A-27) and is deflected through the bottom (B-27) of the bucket pocket. The fluid flow leaves the rotor through the blade outlet (C-27). In picture 27, top right, this turbine shows schematically from a third view, as a top view of one side of the rotor disk. This rotor (RO) rotates about its axis of rotation (RA), here clockwise. The blades are arranged on the edge of this rotor disk. Their cross-section, which is in principle U-shaped, is indicated by dashed lines. The blades are arranged to overlap. The bucket inlet (A-27) is visible in this top view. Covering this area is the inlet duct (D-27) of the housing, which is indicated by thick dashed lines. The corresponding blade outlet or outlet channel of the housing is located on the other side of the rotor. The deflection in the rotor is shown here from the inside out, it could also be done from the outside in.

The above-mentioned special advantages also apply to this design. This turbine can be used as Water turbine are used. However, this concept is particularly advantageous if the process of Energy conversion should be repeatable, as is required in gas and steam turbines. Because with that the effective deflection of approximately 180 degrees is also used in this area.  

In Figure 27, left, center, the top view of the jacket of the rotor disk is shown again, corresponding to the illustration in Figure 27, top left. In Fig. 26, middle line of representation, blades of an analog construction were arranged in the housing, but pointing in the opposite direction. This principle can also be applied here. When the fluid flow leaves the rotor through the blade outlet (C-27), it then flows into the blade inlet (F-27) of the housing, is deflected at the bottom (G-27) of the blade pocket of the housing and leaves through the blade outlet (H- 27) of the housing the blade of the housing. The fluid flow now points back in the original direction and can be fed again to the blades of a rotor.

Constructional execution

A turbine of this type is shown schematically and as an example in Figure 27, bottom right. A rotor (RO) is rotatably mounted in the housing (GE) around the axis of rotation (RA). Blades of the type described above are arranged in the outer region of the rotor. Three such rotor blade rings are shown here on three disk-shaped rotor parts. Corresponding blades of the housing are arranged on the same radial plane. Two such strator blade rings are shown here. The fluid flows through an inlet channel (D-27) of the housing in a tangential direction onto the first side wall of the rotor. The fluid is deflected several times as described above. The fluid leaves the housing through an outlet channel (E-27).

The inlet and outlet areas of the housing are not described in detail here. However, their design is from of extraordinary importance. You should follow the principles of inlet design described above area designed by turbines. All of the construction variants of this tangential turbine presented here require an annular supply of the fluid with strong swirl in the tangential direction to the rotor. Already in the Pipe invention like here are shown various construction elements, which this flow form ensure in an optimal way.

The basic path of the fluid through such a tangential turbine is shown here again schematically. The fluid flows through this machine with an axial motion component. This direction of movement is brought about by the inner walls of the blades, which have an angle with respect to the radial plane. The fluid flows to another in a circular or elliptical path. This movement is caused by the deflections on the respective blade base. In principle, the surface of all scoop bottoms shows a spirally wound band. This is shown schematically in Figure 27, left, second illustration from below. In a tangential view, the bucket bottom can be seen from the inside (I-27), then from the outside (J-27), again the inside (K-27) and subsequently the outside (L-27), so the bucket bottoms show overall the course of a spiral winding band. However, a full circular arc of this band is divided into two halves, the blade of the rotor and the blade of the rotor. In between are the blade openings, so that instead of the circle there is approximately an elliptical shape of the path of all blade bases. This is shown again schematically in Figure 27, bottom left.

The fluid is received in the inclined blade inlet (M-27) and through the blade floor (N-27) deflected, here z. B. is redirected into the plane of the drawing. In the transfer area (0-27) the movement mainly takes place in the axial direction. Then the redirection by a Bucket bottom (P-27) take place, here z. B. from the drawing level. The fluid flow through this So machine represents circular movements, which are stretched along the jacket and also one have axial component. This movement is in contrast to almost all known turbine shapes a continuous movement in the same direction of harmony. This is a prerequisite for that too within the blades as there are constant flow conditions between the rotor and the housing.

Figure 28 shows other examples of constructive designs of this tangential turbine, above that of a river turbine. A turbine inlet according to Figure 10 is assumed.

A longitudinal section through a river turbine is shown schematically and as an example in Figure 28, top left. As stated above, the water in parabolically curved channels (A-28) of the housing (GE) should be fed to the rotor (RO), which is rotatably mounted in the housing about its axis of rotation (RA). According to the criteria set out above, in the case of a flow, which is in principle tangential to the jacket of the rotor in the blades (B-28), the water should first be deflected in the axial direction, then in the radial direction. If there is a corresponding free fall height, this deflection can total around 180 degrees. If this free-fall height is not given, the water at the rotor outlet must still have a movement, ie the deflection will then only be 135 degrees, for example.

In Figure 28, top right, a cross-section or a top view of this river turbine is shown schematically and in sections. As shown above, the inlet channels (D-28) in the housing (GE) should also have a parabolic path from this point of view and should lead the water to the jacket of the rotor in an almost tangential direction. The water flows into the rotor through a blade inlet (E-28) and is deflected in the blade pocket (F-28), but by less than 180 degrees. The water flows out of the rotor through the blade outlet (G-28). The speed of the water is significantly reduced here compared to the speed in the tangential direction in the blade inlet, but not to zero.

It should be emphasized that this tangential turbine in connection with this turbine inlet area without any tail unit or baffle works. All known tail units do more harm than good. It it is much more sensible, for example, to regulate the volume throughput of a water turbine at the very back.

Regulation in the inlet channels by conventional sliders and tail units is not permitted. In the pipe invention, on the other hand, tail units and throttle valves were introduced, which upright Maintain a swirl or potential swirl flow without harmful effects.  

These considerations apply to the construction of a river power plant, and to an even greater extent to storage facilities power plants. As soon as water in pipes is brought up to a rotor, the flow must have swirl or should represent potential swirl flow. The control of the volume throughput must again at the very back, where the water flows into the area of the pipes for the first time. In pipe invention a construction element container outlet or pipe inlet was described in detail. Through adjustable The volume flow rate can be without baffles on the housing of this container outlet or pipe inlet any resistance and without any harmful influence can be optimally controlled.

Another example of this tangential turbine is shown in Figure 28, below. The fluid is brought here, for example, through housing screws (H-28 or I-28) of the housing (GE) to the casing of the rotor (RO), or is discharged again through corresponding housing screws (J-28 or K-28). The inlet area of the turbine can be realized according to the principles detailed above. The representation here is by no means true to scale. In principle, a flow with strong swirl must exist in the housing screws, which is practically brought tangentially to the rotor through a nozzle of extremely elongated cross section. It will also be useful to organize a swirl movement in the machine outlet.

The rotor is rotatably mounted in the housing around its axis of rotation (RA). In this exemplary embodiment, the blade is arranged on the jacket of a cylindrical rotor. The fluid flows into the rotor through the blade inlet (L-28) and is deflected by almost 180 in the blade pocket (M-28). The fluid in turn exits the rotor almost tangentially through the blade outlet (N-28). Here it is shown schematically that this process can be repeated by correspondingly shoveling the housing with the shovel inlet (0-28) arranged in the opposite direction, shovel pocket (P-28) and shovel outlet (Q-28). In contrast to the corresponding illustration in Figure 26, right, center, the blade openings are not made parallel to the axis of rotation. The fluid experiences a greater deflection to the axial direction. A labyrinth seal between the rotor and housing or between the individual process sections is thus practically achieved. An additional, non-contact seal on the webs in the middle and on the side of the blades could still make sense. This makes this principle of repeated redirection of the fluid by almost 180 degrees also applicable for use as gas or steam turbines.

The blades are again only shown schematically here and in no way to scale. Real are one Attach a variety of blades to the circumference of the rotor, e.g. B. according to the number of blades known gas or steam turbines. Instead of the basically cylindrical design of the rotor can this also have a conical design in principle. As usual, this turbine can handle a high pressure and have a low pressure part. The volume of the Blades are each created larger, so that a continuous relaxation of the gas or steam is given when passing through this turbine.  

Special advantages

Based on theoretical considerations, basic requirements for the optimal implementation of the Energy of a fluid set up in mechanical energy. By designing and arranging blades According to the design principles of this tangential turbine, these requirements are completely met.

The fluid is only passed between the rotor and the housing almost in the tangential direction. By relatively small cross-sectional areas of the individual fluid jets becomes the energy of a large part of all fluid parts Deliver as directly as possible to parts of the rotor. The blades have no suction side. The force will transmitted only by print. Fluid always flows in or out on the inside of the deflection. There are always given continuous currents. There is therefore a constant adhesion. The redirection always takes place at about 180 degrees. The force component points exclusively in the tangential direction. The fluid can never move sideways in the shovel pockets during deflection. The particularly effective Technology of known free jet turbines is further improved as a result. The process of energy conversion can be done by a single redirection. However, such a process section can also be repeated. In order to this effective technology of deflection by almost 180 degrees will also be used in gas and steam turbines bar. The fluid always has the same sense of motion during the throughput through the turbine This ensures constant flow conditions through the entire turbine, even with different ones Volume flow. The design of turbine blades requires enormous effort in the construction, during construction and through the necessary practical tests. Despite all theory, empirical values are often crucial. With the above theoretical considerations such as the construction derived from it principles are new aspects for turbines with high efficiency and wide range of applications.

3.21. Axial turbine function

This construction element is suitable for the kinetic energy or the pressure energy of a fluid to transfer mechanical rotary movement, the fluid flow being in principle axial.

Construction principles

The fluid flow flowing into this axial turbine should preferably have swirl. The fluid should be the Axial turbine preferably flow in an annular channel of the housing in the tangential direction. At the rear, the swirl is to be straightened first by appropriate deflection, so that in channels of the rotor there is only one fluid flow parallel to the axis of rotation, that is to say in the axial direction. This rotor Channels are shaped so that a swirl is formed, causing an angular momentum in the direction of rotation of the rotor results. This swirl is then set up again, pressure being generated only in the radial direction, ie only is given on the axis of rotation. After setting up the swirl is the basic direction of the fluid flow again parallel to the axis of rotation. This process can therefore be repeated.  

The fluid mass is gradually shifted from the back to the front against the direction of rotation of the rotor. Accordingly, an impulse is given in the direction of rotation of the rotor. The fluid flow can start in the front of the axial turbine the front wall of the rotor can be discharged to the outside parallel to the axis of rotation or the fluid flow can completely redirected against the direction of rotation at the front and discharged tangentially to the outside.

Constructional execution

Figure 29, top left, shows three basic options for redirecting a fluid flow in a rotor. In a free jet turbine, for. B. the fluid flow (A-29) in the rotor by accordingly shaped blades (B-29) deflected by almost 180 degrees. The rotor (RO) reaches almost half the speed of the incoming fluid jet. The fluid jet (C-29) emerges to the rear at about half the speed. The rotor speed and the remaining fluid speed cancel each other out, the "free jet" only falls from the machine. Not all fluids can use their energy sufficiently in a single conversion process. Or z. B. in jet engines in front a remaining flow parallel to the axis of rotation is desired. Then only a maximum of 90 degrees can be deflected in the back of the turbine.

In Fig. 29, top display line, in the middle, a section of a cross-section is shown schematically. A rotor (RO) rotates clockwise around the axis of rotation (RA). A fluid flow (D-29) is guided tangentially to the rotor through the housing (GE). In channels (E-29) of the rotor, this flow is deflected parallel to the axis of rotation. In Figure 29, top line of illustration, on the right, it is shown schematically that this deflection should take place with the same cross-sectional area, i.e. only by pressure.

If the fluid flow flows obliquely at the rear end of the rotor, only one can do so there is little deflection, the distances between the rotor channels are relatively small. If the fluid flow flows tangentially on the jacket of the rotor, a deflection of 90 degrees can occur, the distances between the rotor channels are then relatively large. The fluid flow can be the rotor in these two Opportunities flow or in a combination of both possibilities. In any case, this should Axial turbine after a corresponding deflection of the fluid flow, a remaining flow in rotor channels be given parallel to the axis of rotation.

The main principles of this axial turbine are shown schematically in Figure 29, middle line on the left. A rotor (RO) is supposed to turn clockwise on a rotation axis (RA). The following serves as a theoretical basis: In a tube (F-29) of the rotor, a fluid flow is to be guided parallel to the axis of rotation. Baffles should be installed in this tube in such a way that they cause an anti-clockwise swirl. The fluid experiences an increase in its kinetic energy, while a corresponding pressure is exerted on the guide plates. This pressure on the parts of the guide plates outside the longitudinal axis of the tube results in an angular momentum on the rotor in its direction of rotation. This area is identified by the thick dashed arc line. This pressure on the parts of the baffles within the tube longitudinal axis, however, cause an angular momentum on the rotor against its direction of rotation. This area is identified by the thin dashed arc line. It therefore makes sense to create a swirl in a tube of the rotor, but only outside the swirl axis of rotation.

If the twist is to be set up again, the force effects are reversed. The force effect is only neutral if the swirl is set up by a guide plate with tangential alignment. Only then works the pressure of the fluid in the radial direction, i.e. without affecting the direction of rotation of the rotor. So it does it only makes sense to form a twist in the outer area of the above tube (F-29) and set it up again if its direction of movement points to the axis of rotation. This swirl movement may only be partially Cover areas of this outer area of the above pipe. So this is the mental starting point.

The fluid is transferred to the rotor from a basically annular inlet area of the housing flows there into rotor channels, the cross-sectional area of which is basically the shape of ring segments (G-29). This cross section could be converted into a square cross section. When a If the rotor channel has a square cross section and is wound around the above twist rotation axis (H-29), it forms for this Part of a corresponding swirl path. So the rotor channel is not wound around its central axis, the swirl axis of rotation is rather at the corner that initially points against the direction of rotation of the rotor of the square cross section. A spiral with an axis of rotation outside the center of each The cross-sectional area is called "asymmetrical winding" in the following. The rotor channel can do the above have a square cross section or, for example, a cross section in a rectangular shape (I-29) or have a round cross-section (J-29) or other shape. The cross-section is always a partial area the outer area of the above tube (F-29).

At J-29, a round cross-section rotor channel is schematic in different situations from back to front shown. The rotor channel is coiled around an axis of rotation against the direction of rotation of the rotor by a little more than 180 degrees. This movement is called a "spiral phase" in the following. In the beginning as in the end one In spiral phase, the fluid flow is in principle parallel to the axis of rotation.

A new spiral phase can therefore be added after each spiral phase. The shift is shifting point of asymmetrical winding against the direction of rotation of the rotor (from I-29 to K-29). The fluid mass is thus approximately semicircular, each outward path sections against the direction of rotation of the rotor. Accordingly, the rotor experiences an impulse in its direction of rotation.

Figure 29, middle line on the right, shows schematically the directions in which the forces act. The rotor (RO) rotates clockwise around the axis of rotation (RO). A rotor channel (L-29) has, for example, a square cross section. After an asymmetrical spiral (M-29), all walls of this rotor channel are curved surfaces. The fluid flow from the back to the front is basically parallel to the axis of rotation, so it flows from situation L-29 to situation M-29.

The fluid is through the downward-facing wall surface and the inward-facing wall Surface deflected upwards and outwards by suction. Accordingly, there is a counterforce in that Fluid sucks these wall surfaces downwards and inwards. This results in a force component in the Direction of rotation of the rotor.

The pressure effects from this deflection of the fluid flow are more important. The fluid is flowing through the bottom wall surface and the outward wall surface upwards and further out distracted. The corresponding back pressure of the fluid on these surfaces points downwards and inwards, which means also gives a force component in the direction of rotation of the rotor.

The effect of the suction sides is considerably less than that of the pressure sides, since the cross-sectional area in the Principle remains constant. The deflection of the fluid takes place on the pressure side of the rotor channels, which accordingly receding suction sides only give room for this change of direction.

Figure 29, bottom, right, shows the direction in which the force components act during a spiral phase. Instead of the above cross-sectional areas, here some radii are drawn around the swirl axis of rotation (N-29), on which the center points of a rotor channel are located during the asymmetrical winding. The arrows point in the direction of the back pressure of the fluid due to its deflection through the curved walls of the rotor channel. The corresponding effective radius to the axis of rotation (RA) of the rotor (RO) is shown for each force action arrow. There is always a force component in the direction of rotation of the rotor throughout the entire spiral phase. Only at the very end of the spiral phase (0-29, analogous to the above twist in tube F-29) does the direction of the fluid pressure change abruptly by 180 degrees and now points in the radial direction.

The rotor channel thus represents a path of forming and setting up a swirl flow. The fluid is in it constantly redirected. These deflections always produce a positive torque in relation to the direction of rotation of the rotor. The deflection at the end of the spiral phase, however, causes a pressure perpendicular to the Rotation axis, is therefore neutral with respect to the direction of rotation of the rotor. After this abrupt installation of the A new spiral phase can be initiated.

There is therefore no redirection by a strator or housing part for repeating a process section required. The deflection of the fluid flow back into the original direction of movement takes place here by Pressure against the axis of rotation. The fluid does not have to be transferred from the rotor into the housing, but remains in the rotor during this deflection.  

Figure 29, bottom left, shows schematically how the center of mass (P-29) shifts outwards (Q-29) during the asymmetrical winding. The higher path speed on the outside is more than compensated for by turning against the direction of rotation of the rotor. In the first half of the turn, the fluid loses speed in the direction of rotation of the rotor, in the second half of the turn the fluid returns to its original speed in the direction of rotation of the rotor, as parallel to the axis of rotation. The aspect of different path speeds must be taken into account when designing the spiral, but is of no importance with regard to the torque as a whole.

The radial component of this movement from the inside out results in a braking of the rotor rotation that a corresponding acceleration from the outside in. The tangential component of the Movement. In this, the fluid is shifted against the direction of rotation of the rotor. This is done e.g. Belly in the above-mentioned free jet turbine. There, however, the rest of the flow is no longer usable. The asymmetrical spiral, on the other hand, connects this tangential component of motion with one Movement parallel to the axis of rotation. As a result, the starting situation always arises again, the process can repeated in a controlled manner. The sequence of movements consists of a harmonious training a swirl path movement, followed by an abrupt change of direction when the spiral phase ends. However, this abrupt change of direction can be made more harmonious by various measures.

In Figure 30, top, left, there is for example a rotor channel with a basically rectangular cross-section, but with rounded ends and a longitudinal axis that curves in the course of the spiral phase. In this drawing, the rotor is supposed to move from top to bottom, the rotor casing is drawn in a simplified line, the fluid flow runs from back to front, here into the plane of the drawing, the rotor channel (B-30) is coiled from bottom to top Axis of rotation in the range of A-30. The fluid flow at the lower end of the rotor channel is redirected to the outside (here to the right), the corresponding side of the counter pressure is drawn as a thick line. With the further winding, this printed page becomes wider and therefore more effective. In the middle of the spiral phase, the rotor channel longitudinal axis is a straight line in order to achieve the greatest possible torque there. With further winding, the inner part of the rotor channel leads the rotation, while the outer part, acting on the longer lever, rotates more slowly. While this outer end of the rotor channel still has an effective pressure side, the inner end is already pivoted in the tangential direction. This is associated with the beginning of a new spiral phase, with the axis of rotation shifting from A-30 to the area of C-30 and the rotor channel (now referred to as D-30) again having the course described above. This ensures that the individual spiral phases begin and end smoothly.

A corresponding illustration, for example a rotor channel with a round cross-section, is shown in Figure 30, top, center. The curve drawn shows the mass centers, which have a perfectly harmonic course. The pressure side of the respective situation is drawn as thick lines, which swings outwards and back again. Despite the relatively smooth transition from the end to the beginning of a spiral phase, the pressure side jumps very quickly in the neutral, radial direction.

The flow of fluid in a pipe or channel is associated with friction. This is necessary to z. B. to cause a torque on the pressure sides of the channels. Unproductive friction can be reduced by not only flowing the fluid in the direction of the longitudinal axis but also with swirl. Figure 30, top right at E-30, shows schematically how the flow z. B. will form within a round rotor channel of this axial turbine. Inside, in the picture on the left, the web speed, in the picture down, is lower than outside. Outside, however, the spiral movement takes place against the direction of rotation of the rotor. Fluid parts inside therefore have a higher overall speed in the direction of rotation of the rotor than fluid parts outside. Within a rotor channel with a round cross-section (but also other cross-sections), a twist against the direction of rotation of the rotor will form. The flow of the fluid in these rotor channels will therefore in no way be an optimal potential swirl flow. But there will always be a swirling flow. This significantly reduces the friction in the rotor channel and a flow with swirl significantly reduces the losses when a fluid flow is deflected.

Figure 30, middle line of the illustration, schematically shows a section of a rotor shell or the view in the direction of the axis of rotation and different situations are shown in different sections. The rotor (RO) moves from top to bottom. In section (F-30) on the left, the rear area of this axial turbine with the inlet area, there is either a fluid flow (J-30) in the tangential direction or the fluid flow (K-30) already has a movement component parallel to the axis of rotation. In any case, the twist of this movement is first set up, so that there is only movement (L-30) parallel to the axis of rotation. This is followed by sections of different spiral phases.

At G-30, a curve is initially shown as an example, which shows the path of the cross-sectional mean point of a rotor channel. The first part of the spiral phase (M-30) with the formation of the swirl path course will be longer, while the second part of the spiral phase (N-30) with the Setting up this twist at a shorter distance takes place. A subsequent second spiral phase is here drawn.

Another section (H-30) shows the development of an elongated rotor channel as shown in Figure 30, top left, schematically. The end (O-30) of the rotor channel that initially points against the direction of rotation of the rotor represents the swirl axis of rotation and therefore initially remains parallel to the axis of rotation in principle. The end (P-30) of the rotor channel, which initially points in the direction of rotation of the rotor, swivels outward (here from the plane of the drawing) and thus forms a swirl path. Even before this swirl is set up again, the end that now points in the direction of rotation of the rotor begins its spiral phase. The sloping auxiliary lines indicate that both spiral phases overlap.

The right section (I-30) shows how the outlet area can be designed. Either one Spiral phase led so far that the fluid flow (Q-30) emerges tangentially against the direction of rotation of the rotor. Compared to an initially tangential fluid flow (J-30), this meant a deflection of about 180 degrees. Or the fluid flow (R-30) is discharged at the rear end of the axial turbine, so that the Fluid flow still has a speed component in the axial as well as in the radial direction. Combinations of both options are of course possible.

A longitudinal section through an axial turbine is shown schematically and as an example in Figure 30, below. The rotor (RO) rotates around the axis of rotation (RA), which is mounted in the housing (GE). The fluid enters the rotor channels (S-30) in the inlet area (left), which here have a round cross-section, for example. In the drawing, circles are drawn as cross-sections for simplicity, because of the curvature these would have to be drawn partially elliptically. Due to the asymmetrical spiral, the rotor channels (S-30) initially have increasing, then decreasing radii from back to front. Two such spiral phases are shown schematically. At the front, for example, the fluid flow (T-30) is discharged tangentially into a round channel in the housing.

In this illustration, the rotor (RO) is only executed at the rear and from the solid, while in the middle only the Axis of rotation is drawn. Rotor channels could be formed as cavities in a solid rotor be, or like a normal pipe only consisting of a relatively thin outer wall. Just one Bundle of individual tubes, all bent identically in an asymmetrical spiral, then practically represents that essential part of this axial turbine. The individual rotor channels are for reasons of stability Part of be connected. There are gaps between the individual rotor channels, which e.g. B. can be used for cooling. The housing is used at the back and front to support the rotation axis. Cooling medium can be brought to the rotor channels through openings in the housing wall.

An important aspect is that the problem of the seal between only in the inlet area Housing and rotor is given. The problem of the accuracy of fit with regard to the gaps between Rotor blades and housings as with conventional axial turbines are not available here.

Special properties

In conventional axial turbines, the fluid flow through tail units must always be returned to the original be deflected in the axial direction. A laminar flow is difficult to achieve or goes earlier or completely lost later. In this axial turbine, the fluid rotates with the rotation of the rotor, it turns inside the coil and it has swirl inside the rotor channels. Such a triple nested rotation is considered an ideal form of fluid movement. In comparison, appear the movements of conventional axial turbines are chaotic. The behaves accordingly Efficiency in converting the energy of the fluid into mechanical rotary motion.  

The elimination of all tail assemblies in the housing results in a significantly simpler construction and The problem of the accuracy of fit between the rotor blades and the housing is completely eliminated. The problem of The seal between the rotor and the housing is only provided at the inlet area, as is the cooling is accomplished. Overall, this results in significantly lower manufacturing costs as well as lower costs Weight and more compact dimensions. The design principle of this axial turbine is conventional in many Thinking about concerns will therefore prove to be the best in a variety of applications.

3.22. Jet engine function

This construction is suitable for generating propulsion for aircraft.

Construction principle

A jet engine can be constructed using various construction elements described above.

Constructional execution

An example of such a jet engine is described below using the longitudinal section in Figure 19. This illustration shows various construction elements in sections A-19 to F-19. This representation is only schematic and exemplary, but in no way to scale. The functions are only briefly described here, details of the individual construction elements are described above. In principle, a rotor (RO) rotates about its axis of rotation (RA), stored in a housing (GE).

Section A-19 represents a pre-swirl generator. The inflowing fluid (G-19) is in a main stream (H-19) transferred with swirl flow, while a side stream (I-19) also by suction Has swirl flow, both together already form a potential swirl flow here.

Section B-19 represents a potential swirl pump. In the channels of the rotor, both the Main flow as well as the secondary flow detected and experience a substantial acceleration of their Rotary motion. The outer wall of the bypass ducts is represented by the housing. By Friction at this side stream also undergoes a swirl movement within the rotor channel. The inner wall of the main flow channels is represented by an acceleration rotor (K-19). This due to the gearbox (L-19) rotates at a higher speed than the rotor, preferably at double speed Rotational speed. The main flow also experiences a swirl movement within the rotor channel. The Flows within the rotor channels thus represent extremely strong potential swirl flows in two ways. First, the currents rotate around the axis of rotation. On the other hand, they pose machine-generated tornadoes that rotate about the longitudinal axis of the rotor channels.  

Section C-19 represents a pressure lock and the combustion chamber. That from the previous potential swirl pump outflowing fluid is received in housing screws (M-19), here for example the main flow and the secondary flow separately in two housing screws. The fluid flows in tangentially, with which in the Casing screws maintain the potential swirl flow or is amplified because the principle Direction of movement of the fluid has only a small axial component. The front of this housing also represent the combustion chamber, with fuel being fed and ignited (here only shown schematically at N-19). Here, for example, the fuel is only fed into the bypass Housing screw fed. The flow is accelerated by the addition of heat, again practically only in the direction of rotation of the rotor.

Section D-19 represents an area of an afterburning chamber. In the main as well as in the secondary flow Casing screws have a potential swirl flow, both in the direction of rotation of the rotor, but in opposite directions Twist direction around the longitudinal axis of the housing screws. Both flows emerge tangentially, mix accelerate or accelerate again. The outlet openings (O-19) of this housing screw is included directed almost perpendicular to the outer wall of the afterburner. This will make the twist Flow in the augers completely set up and without any tail unit. Afterburn area (P-19) there is an extraordinarily strong rotational movement of the fluid in the direction of rotation of the rotor. This area can already be part of the rotor, so that only a small amount on the rotating walls There is friction, or this friction is already productive in the sense of the downstream turbine.

Section E-19 represents the area of the turbine, shown here for example and only schematically in Shape of previous axial turbines. The fluid of the afterburning chamber becomes tangential in many rotor channels (Q-19). In a first phase, the movement component is in the direction of rotation of the rotor set up so that in principle there is only one movement component in the axial direction. This can In other phases of asymmetrical winding controlled torque is given to the rotor to be sufficient to get power for the pump function. The rotor channels of this axial pump are only here represented schematically as a circle. The basic shape of the rotor cylinder is shown here conically. The Fluid is released in the tangential direction at the front. The flow rate is still essential there higher than the rotational speed of the rotor there. So the fluid still has a large remaining one Energy.

Section F-19 describes the area of pulse conversion. It is part of the housing and serves to achieve the best possible propulsion. This impulse converter eliminates any twist from the Fluid flow taken so that only movement in the axial direction results from it. Here this energy is used to accelerate the greatest possible mass in the axial direction. As be accelerated total mass (R-19) are not only available for the fluid mass of the inlet area (G-19) Available, but also fluid masses (J-19) of the outer area of the jet engine.  

This secondary flow (J-19) can be passed through the outer walls of the housing. Between these outer and the inner parts of the jet engine baffles (S-19) will be attached, at least as far as they are required to hold the jet engine on other parts of the aircraft. The function and construction of the pulse converter is described in detail in the invention "Constructional Elements for Improving the upward and forward propulsion of aircraft and watercraft ".

Special properties

The concept of a jet engine described above is only one example of how Combination of various structural elements of this invention makes particularly effective constructions possible become. This jet engine makes it clear, for example, how the fluid is increasingly rotating is shifted, not only within a construction element, but also from a process section to next one. A rotary movement is built up in the inlet area, which is then gradually strengthened becomes. The fluid is directed in the axial direction only to the extent required by the sequence of functions. In contrast, the swirl movements are repeatedly promoted in the same direction of rotation. There are no abrupt ones Change of direction, but only a steady acceleration of the fluids, mainly its swirl movements. It is only at the very end of the functional sequence that the energy built up in this way becomes extremely strong movement of the fluid is deflected in the predominantly axial direction insofar as it is required for the pump function is real. However, the remaining available energy is not simply released in the axial direction like with conventional jet engines, but again specifically for maximum implementation of the Energy in the sense of propulsion used by the pulse converter (see invention mentioned above).

4. Summary

In conventional pumps and turbines, the fluid is constantly redirected in the axial direction, mostly in an abrupt manner. The previous example of a jet engine, on the other hand, does the universal logic of everyone constructive elements shown here clearly. It shows how a movement is initiated and in always same direction of rotation can be amplified and only at the end of the process the movement in the direction and Form is brought into conformity with the ultimate objective. The essential aspect is always that the special advantages of a motion sequence in the sense of a potential swirl flow are used.

In many construction elements it has been achieved that the fluid flows as a whole have the ideal forms optimal flow. So here the form of movement rolling in and then rolling out in one machine closed circuit. In another construction element, the course of the path of a ring vortex. In several constructs there is a multi-nested rotary movement realized. The well-known flow technology tries to avoid vortex formation in the best possible way The swirl movements are deliberately triggered, promoted and used in a variety of ways.  

The piston machines represent a completely separate topic from the known fluid dynamics. Here It has been shown that fluid flow is also of major importance for piston machines comes to. From the considerations regarding the rotating vertebrae, the corresponding one emerged in analogy Mechanics of a new type of crank gear. The rotary piston engine above represents a symbiosis of Reciprocating engine and fluid machine.

The effect of the tornadoes is known, but it is theoretically controversial what the triggering moments are are and what maintains their dynamism. A useful theory was presented in the basic invention. With some construction elements here it was shown how the typical form of movement of a tornado can be simulated mechanically and how the effects can be made technically usable.

Claims (23)

1. The claim relates to the invention of a construction element "pre-swirl generator", which is characterized in that

• a rotor is installed in a funnel-shaped inlet area, which basically has the shape of a tube,
• the diameter of this rotor tube is increasing from the back to the front, but is always smaller than the diameter of the inlet area,
• the jacket of this rotor tube is subdivided one or more times in a straight or curved line and in each case the edge pointing against the direction of rotation of the rotor is spirally curved inward, so that fluid between these blades of the rotor can flow into the rotor tube in a basically tangential direction,
• baffles can be attached between these blades with a basically spiral course, so that fluid between the blades is accelerated in the axial direction,
• so that the twisting movement of the main flow of the fluid is generated by the rotation of the rotor in the rotor tube,
• baffles with a basically spiral course can also be attached to the walls of the inlet area,
• so that the swirl movement of the secondary flow of the fluid is generated between the walls and the rotor tube,
• - The main and the secondary flow of the fluid can be used separately or are available together in an outlet pipe.

2. The claim relates to the invention of a construction element "pipe pump", which is characterized in that

• - it corresponds to the features of the construction element according to claim 1,
• - However, the diameter of the walls of the inlet area at the outlet tapers to the diameter of the rotor tube, so that no secondary flow is formed.

3. The claim relates to the invention of a structural element "centrifugal pump", which is characterized in that

• a rotor has a round inner wall and a round outer wall, the diameters of which are designed such that the cross-sectional area available to the fluid decreases from the inlet to the outlet,
• baffles are attached in principle in the radial direction between this inner and outer wall, which form a large angle to the axis of rotation at the inlet and run almost parallel to the axis of rotation at the outlet,
• the fluid flow of the rotor is directed at the outlet into a transfer channel of the housing, from which the fluid flow is introduced tangentially into a housing screw,
• this housing screw has an increasing cross-section from its inlet to the outlet,
• - The housing screw can accept the fluid flow of the full circular arc or several housing screws each only the fluid flow of corresponding circular arc sections.

4. The claim relates to the invention of a construction element "pressure lock", which is characterized in that

• a housing screw basically has the features of the housing screw according to claim 3,
• - but has a section without openings on its jacket after its inlet area,
• - Then the housing screw in its outlet area again has openings on the casing such that fluid can flow out in the tangential direction and the diameter of the housing screw tapers accordingly.

5. The claim relates to the invention of a construction element "potential swirl pump", which is characterized in that

• chambers are arranged in a rotor in principle in the radial direction and the cross-sectional area does not increase from inside to outside,
• three wall sides of these chambers are imaged by the rotor and one wall side of these chambers is imaged by the housing,
• or alternatively two wall sides of these chambers are imaged by the rotor and one wall side of these chambers is imaged by the housing and one wall side of these chambers is imaged by an acceleration body which rotates about the axis of rotation at a higher speed than that of the rotor,
• - Where one or more levels of such chambers can be created in the rotor.

6. The claim relates to the invention of a construction element "suction pump", which is characterized in that

• a rotor has only a round cross section and its diameter is increasing from the inlet to the outlet,
• the housing wall is shaped such that an increasingly smaller cross-sectional area is available to the fluid from the inlet to the outlet,
• grooves are provided on the housing wall, which have a spiral course from the inlet to the outlet, corresponding to the direction of rotation of the rotor,
• - In principle, the grooves have a round or rounded cross section, but their two edges point in the direction of rotation of the rotor, that is, they form a tear-off edge.

7. The claim relates to the invention of a structural element "vortex container", which is characterized in that

• - it corresponds to the basic structure of a suction pump according to claim 6,
• - However, the fluid at the outlet is returned to the inlet, so that there is a circulation with an intensive swirling of the fluid,
• alternatively, this vortex tank corresponds to the basic structure of a potential swirl pump according to claim 5,
• - Here, too, the fluid is returned to the inlet at the outlet.

8. The claim relates to the invention of a structural element "ring vortex container", which is characterized in that

• a round and symmetrical container is formed between an outer wall and an inner wall,
• the cross-section of such a container is U-shaped or V-shaped overall at the bottom, while the container may be rounded and flattened at the top,
• baffles are attached between the outer wall and inner wall with a curved course, so that channels are formed in the container,
• - or alternatively, the container has the shape of only one such channel,
• these containers are rotatably mounted about their axis of symmetry and a plurality of such containers are mounted on a rotor, this axis of symmetry being at an angle to the rotor axis,
• - Is achieved via a gearbox that the rotation of the rotor leads to a rotation of the container in the same direction.

9. The claim relates to the invention of a construction element "pressure pump", which is characterized in that

• a rotor has an increasing diameter from the inlet to the outlet and tooth-shaped blades are arranged on its surface,
• these blades are shaped such that one side principally points in the radial direction, the other side principally points in the tangential direction,
• channels are formed between the blades with a triangular cross section in principle, two sides being formed by the blades, one being open,
• - However, these channels form closed chambers in the further course, all four sides of the wall being represented by the rotor and the shape of the cross section being converted into the shape of a ring segment.

10. The claim relates to the invention of a structural element "combustion chamber", which is characterized in that

• - The cross-sectional area is expanded in a pipe by first increasing the diameter of the pipe, on the other hand a round body is installed on the pipe axis, which is pointed from the rear (hereinafter referred to as "island"),
• - after reaching the largest pipe diameter, fuel is introduced into the pipe and ignited,
• baffles are attached in the tube in the area of the fuel supply, which have the shape of tube sections of smaller diameter than that of the tube and the diameter of which is increasing from the rear to the,
• - between the tube and previous guide plates, guide plates are attached in the radial direction, which have a spiral course,
• - Only a subset of the total fluid flow can be fed to a combustion chamber for the purpose of mixing this accelerated partial flow into another partial flow in the tangential direction.

11. The claim relates to the invention of a structural element "inlet area of turbines", which is characterized in that

• - In a hydropower plant water is fed tangentially to a rotor, channels being formed between the walls by the inner and outer walls of the inlet area and by baffles, which have a parabolic shape horizontally and vertically, have a ring-shaped cross-section on the outside with a greater length than width, inside have in principle a rectangular cross section with a greater height than width.
• - Or the inlet area of a turbine has an annular cross-section and a fluid is fed to this inlet area through an inflow pipe with potential swirl flow or swirl flow, this inflow pipe is spirally wound outside around the inlet area or inside in the inlet area, the fluid is tangentially discharged from the inflow pipe and almost is introduced into the inlet area perpendicular to the wall thereof.

12. The claim relates to the invention of a structural element "exhaust gas turbocharger", which is characterized in that

• the inlet area of the turbine is designed in accordance with claim 11,
• - The pump is designed according to claim 9,
• - The combustion air is fed to the inlet area of the engine cylinders in pipes with potential swirl flow.

13. The claim relates to the invention of a structural element "rotary valve tube", which is characterized in that

• a round recess is made in the cylinder head of a reciprocating piston engine parallel to the longitudinal axis of the engine, in which a tube is rotatably mounted and this tube rotates at half the engine speed,
• the recess in the cylinder has openings in the direction of the recess in the tube in the cylinder head,
• - The tube has openings on its jacket, which are arranged so
• - That in the period of the intake stroke from the tube through the openings in its jacket and through the openings of the cylinder recess, the combustion air can flow into the cylinder, or in the period of the exhaust stroke from the cylinder through the openings of the cylinders and through the openings on the jacket exhaust gases can flow into the pipe,
• - That in the tube of the combustion air, the combustion air flows preferably in potential swirl, which z. B. is generated by a pressure pump according to claim 9 or z. B. is generated by means of a pre-swirl generator according to claim 1,
• that the exhaust gases are in a swirl movement in the tube of the exhaust gases and their kinetic energy can be used by a turbine,
• that partial quantities of the combustion air, such as the exhaust gases, are returned and partial quantities of the exhaust gas can be returned to the combustion air circuit,
• - This rotary valve tube is used in an analogous manner in a pump.

14. The claim relates to the invention of a structural element "inlet and outlet rotary valve tube", which is characterized in that

• - It meets the criteria of claim 13, however
• the functions of supplying fluid to a cylinder are combined with the function of discharging fluid from a cylinder in a tube,
• - for which the cross-sectional area of the tube is divided into two areas by a coiled partition, so that two channels are formed,
• - Wherein the channel of the fluid supply from the back to the front has decreasing cross-sectional area and the channel of the fluid discharge from the back to the front has increasing cross-sectional area.

15. The claim relates to the invention of a structural element "reciprocating gear", which is characterized in that

• - A round disc, hereinafter referred to as "eccentric disc", is firmly connected to an axis of rotation, with a distance between the axis of the axis of rotation and the axis of the eccentric disc, which is referred to below as "eccentricity", ie the eccentric disc is eccentric to Axis of rotation is firmly connected to this,
• the eccentric disc, on the other hand, is rotatably mounted in a further disc, which is referred to as "connecting rod disc" in the following, a distance being given between the axis of the eccentric disc and the axis of the connecting rod, corresponding to the above eccentricity,
• - the connecting rod is rotatably mounted in the center of a piston,
• - This piston is mounted in the housing so that it can carry out a linear stroke movement, the central axis of this stroke movement intersecting the axis of rotation.

16. The claim relates to the invention of a structural element "four-stroke rotary piston engine", which is characterized in that

• a crankshaft is mounted in the housing and is rotatable about its axis, this axis being referred to below as the "axis of rotation",
• an integral part of this crankshaft is an eccentric shaft and the axis of this eccentric shaft runs parallel to the axis of rotation, but there is a distance between the axis of rotation and the axis of the eccentric shaft, this distance being called "eccentricity" in the following,
• a rotor is mounted in the housing, which can be rotated about the axis of rotation and which is called "cylinder rotor" in the following,
• recesses are made in the cylinder rotor on one diameter from one side of the cylinder rotor to the other side of the cylinder rotor,
• - so that a piston can move in these recesses,
• - A round disk is rotatably mounted in the center of this piston, which is referred to below as the "connecting rod disk",
• the eccentric shaft is rotatably mounted eccentrically in this connecting rod, the distance between the axes of the connecting rod and the eccentric shaft corresponding to the above eccentricity,
• is controlled by a gearbox that the crankshaft and the cylinder rotor rotate at the same speed but in opposite directions about the axis of rotation,
• - Several cylinder recesses can be created in an engine, ie also correspondingly several pistons, connecting rods and eccentric shafts.

17. The claim relates to the invention of a structural element "rotary piston transmission", which is characterized in that

• a shaft is rotatably mounted in the housing, which is called "eccentric shaft" below,
• a disk is firmly connected to this eccentric shaft, hereinafter referred to as "eccentric disk",
• the eccentric shaft and the eccentric disk are arranged in such a way that a distance is given between the axis of the eccentric shaft and the axis of the eccentric disk, hereinafter referred to as "eccentricity",
• a piston is rotatably mounted in the center of the eccentric disc,
• this piston can move linearly in recesses in a rotor, so that the longitudinal axis of the piston movement passes through the axis of the rotor,
• this rotor is rotatably mounted in the housing about its axis of rotation,
• there is a distance between the axis of the rotor and the axis of the eccentric shaft which is the same size as the above eccentricity,
• a gear synchronizes the movements of the rotor and the eccentric shaft so that both rotate in the same direction, but the eccentric shaft at twice the speed of the rotor,
• - This gear can be designed so that a gear is firmly connected to the eccentric shaft or the eccentric shaft is formed in a partial area as a gear and this gear is in engagement with an internal ring gear, which is firmly connected to the rotor and the radius of the gear is half the radius of the internal ring gear.

18. The claim relates to the invention of a structural element "rotary piston machine", which is characterized in that

• this machine is based on a rotary piston transmission according to claim 16,
• the openings of the cylinders are smaller than the cross-sectional area of the cylinder cross-section, but can extend almost over the entire width of the cylinder in the direction of the axis of rotation, do not have to be arranged centrally to the cylinder cross-section, but are arranged in the direction of rotation thereof,
• the housing openings of the inlet are relatively small in the case of a pump and the housing openings of the outlet are dimensioned relatively large, conversely in the case of a turbine,
• several cylinders can be arranged in one machine,
• - In the case of a turbine, the surfaces of the pistons can be shaped in whole or in part in the shape of a blade.

19. The claim relates to the invention of a structural element "rotary piston engine", which is characterized in that

• - This motor consists of a functional element of a pump corresponding to a rotary piston machine according to claim 18,
• - This motor consists of a functional element of a turbine corresponding to a rotary piston machine according to claim 18 and
• - A combustion chamber can be arranged between the two according to claim 10.

20. The claim relates to the invention of a construction element "tangential turbine", which is characterized in that

• Blades are arranged on the jacket of a basically cylindrical rotor,
• the blades are formed by principally flat inner walls which point inwards from the surface of the casing at an acute angle to the tangential direction,
• these inner walls on the jacket partially overlap, the non-overlapping area being referred to as "scoop opening" in the following, the overlapping area being referred to as "scoop pocket" below,
• the area of the blade openings is thus formed by an inner wall which is inclined to the surface of the shell and by side walls which in principle are perpendicular to the surface of the shell and always extend from the inner wall to the surface of the shell,
• these blade openings are divided in the axial direction into a region of the inflow of fluid, which is hereinafter referred to as "blade inlet", and a region of the outflow of fluid, which is hereinafter referred to as "blade outlet",
• the area of the blade inlet and the area of the blade outlet can be separated by a web running on the jacket,
• - In the area of the blade pocket, the inner wall of one blade also represents the outer wall of the blade adjacent in the direction of rotation of the rotor,
• this inner wall and outer wall in the area of the shovel pocket are connected to one another by a wall, which is called "shovel bottom" in the following,
• this blade base has a cross section which is in principle semicircular, ie the above side walls merge into the blade base or are connected to it, the blade as a whole thus has a generally U-shaped cross section,
• - With which the fluid flowing in through the blade inlet is deflected in the blade pocket through the blade bottom by approximately 180 degrees and leaves the rotor again through the blade outlet,
• the blade inlet, like the blade outlet, can be arranged on the outside of the jacket of a basically cylindrical rotor or, alternatively, a basically ring-shaped cylinder can be used as a rotor and the blade inlet can be arranged on the outside of the rotor and the blade outlet on the inside of the rotor or vice versa,
• the blade inlet is always located on a different axial plane of the rotor shell than the blade outlet,
• these blades are not arranged on the casing of a rotor, but instead as an alternative and in an analogous manner in the outer region of a basically disk-shaped rotor,
• - Again, the blade inlet and the blade outlet can be arranged on one side of this rotor disk or preferably the blade inlet on one side of this rotor disk and the blade outlet is arranged on the other side of this rotor disk,
• the blade inlet is always located on a different radial plane of the rotor disk than the blade outlet,
• in each of the above variants, corresponding blades can be arranged in the housing, the generally U-shaped cross section of which points in the opposite direction to the blades of the rotor,
• - In the case of an arrangement of the blades on a basically cylindrical jacket surface, these housing blades are in principle offset by half a blade width with respect to the rotor blades in the axial direction, with several blade rings of the rotor and corresponding blade rings of the housing in the axial direction in each case in the rotor and in the housing can be arranged side by side,
• - With an arrangement of the blades on a basically disc-shaped rotor in a corresponding manner, several rotor disks and corresponding housing disks can be arranged next to one another in the axial direction.

21. The claim relates to the invention of a structural element "axial turbine", which is characterized in that

• in the inlet region of the turbine, the fluid is first deflected in a direction that is basically parallel to the axes of rotation,
• is guided in rotor channels which can have any shape of cross-section, but preferably will have a round cross-section or a rectangular cross-section with rounded corners,
• these rotor channels represent integral parts of the rotor and, in principle, run from the rear to the front on the jacket of a rotor and are coiled in such a way that they represent the path of a swirl movement,
• - By guiding the rotor channels outward and counter to the direction of rotation of the rotor and back inward up to the radius of the swirl axis of rotation, i.e. in principle in the axial direction of view, describe a circular arc of somewhat more than 180 degrees, which in the following is described as a " Spiral phase ",
• - At the end of this helical phase, the rotor channel can again describe a helical phase, the renewed helix being carried out about a new swirl axis of rotation, which is shifted relative to the previous swirl axis of rotation about the diameter of the previous circular arc against the direction of rotation of the rotor.

22. The claim relates to the invention of a structural element "jet engine", which is characterized in that

• - It is composed by various construction elements according to the preceding claims, for example a pre-swirl generator, a potential swirl pump, a combustion chamber, a tangential turbine or an axial turbine.

23. The claim relates to a combination of two or more construction elements according to the preceding claims, which fulfill another objective as mentioned in claim 22.