NO137966B - ANALOGICAL PROCEDURE FOR THE PREPARATION OF ANTIBACTERIAL ACTIVE 5-OXOPYRIDO- (2,3-D) -PYRIMIDINE DERIVATIVES - Google Patents

Abstract

Analogous process for the preparation of antibacterial active 5-oxopyrido- (2,3-cQ-pyrimidine derivatives.

Description

Fluid driven control system.

The present invention relates to multistable fluid-driven control systems or units that use a fluid flow for the system to perform functions that have hitherto been performed by electronic components and systems.

Electronic systems and components can perform such functions as detecting and amplifying signals. However, it may be desirable to perform the same or analogous functions using systems other than electronic ones, i.e. without requiring a source of electrical energy or electronic components. Although known mechanical systems can perform functions analogous to functions performed by electronic systems, these systems require a large number of moving parts. Failure of a part usually causes the system to function incorrectly or not function at all.

The present invention relates to fluid-driven control systems or amplifiers of the type that have no moving parts and where the amplification is a function of the size of the deflection of a main fluid jet or stream produced by the impact of a. transverse fluid pressure distribution or gradient.

The state of the art which forms the basis of this invention is thus represented by a fluid-driven control system comprising a nozzle for directing a deflectable fluid flow under pressure through an area of influence towards at least one outlet passage or channel, and a control device for optionally create a pressure gradient across the stream but in the area of influence to deflect the fluid flow and thereby vary the amount of fluid received by each outlet passage. What is unique and new according to this invention is primarily characterized by the fact that the area of influence is delimited by at least one side wall which is positioned so that mutual influence between the fluid flow and the side wall produces a pressure gradient across the fluid flow and causes it to seek to approach the side wall.

The side walls also perform the function of forming a compact restriction for the movement and flow of fluid particles within the area of influence. Due to the mutual influence between the side walls in the impact area and the fluid flow and in the surrounding fluid, fluid amplifiers or control systems according to the invention can perform amplification and switching functions which are analogous to the functions which, in a known manner, have so far only been possible in electronic circuits, or to a limited extent fluid systems with moving fixed parts.

In systems of the kind to which the invention relates, a fluid jet or flow precisely limited in space is deflected as mentioned above by means of a pressure difference which is produced across the fluid circulation. The pressure difference created across the fluid flow can be used in such systems to deflect the flow to an outlet passage or outlet passages that lead to areas in which load devices are placed. These devices can, in a known manner, convert part of the energy in the fluid flow into useful work, e.g. mechanical movement. Alternatively, the energy, pressure or mass flow in the deflected flow can be used as an input signal for a further fluid amplifier or a fluid control system to increase the overall gain or to perform the aforementioned coupling functions. The amplification can be achieved in such fluid amplifiers by introducing a relatively small flow of a control fluid to introduce a relatively small flow of a control fluid to deflect a main high energy fluid flow and to provide a relatively large change in the energy, pressure or mass flow which is delivered to an output or load.

Theoretically, fluidic control systems or amplifiers can be divided into two general classes: I. Systems or devices with mutual current influence or impulse exchange, and II. Systems or devices with boundary layer control. The operation of the first class of fluid amplifiers, class I, is described in more detail in Swedish patent no. 191 961, and shall not be explained in this connection.

The present invention relates in particular to a fluid-driven control system which belongs to class II of fluid amplifier or control systems, i.e. boundary layer control units. This second class of fluid amplifier or control systems includes units in which the main fluid flow and the surrounding fluid interact in such a way with the side walls in the area of influence that the resulting flow patterns and pressure distributions within the area of influence are highly dependent on the shape and location of the side walls. In this class of devices, the fluid or power flow can come close to or come into contact with the side walls of the impact area. The effect of the shape of the sidewalls on the flow patterns and the pressure distribution that can be achieved with single or multiple streams depends on the following conditions: The width of the impact chamber in the vicinity of the power nozzle, the width of the power nozzle, the location of the centerline of the power nozzle in relation to the side walls (symmetrical or asymmetrical ), the angles between the sidewalls and the centerline of the power nozzle, the length of the sidewalls or their effective length equal to the distance between the power nozzle outlet and the separators or devices, the shape of the sidewalls and their change of direction and the specific weight, viscosity, compressibility and homogeneity of those in the impact chamber used fluids. The said effect also depends on the ratio between the width and depth of the power nozzle outlet and therefore to some extent on the thickness of the amplifier or control system in the case of two-dimensional devices. The mutual relationship between these parameters is very complicated and will be described later. The reaction time or time constant is a function of the unit's size in the case of similar units or systems.

Class II amplifier and control systems that utilize boundary layer effects, i.e. effects that depend on the design and location of the sidewalls, can theoretically be further divided into three sub-types: (a) boundary layer units without locking effect, (b) boundary layer units with significant locking effect, (c ) boundary layer units in which the pinning effect predominates and which have memory properties, (a) Boundary layer units without pinning effect. Such a device has an increased gain as a result of the boundary layer effect. However, this effect does not dominate the control signal, but instead combines with the control currents and provides a continuously variable output signal determined by the amplitude of the control signal. In such a Meter, the power flow remains deflected from the original direction only if there is an uninterrupted inflow or outflow of fluid in one or more control nozzles. (b) Boundary layer units with significant pinning effect. In these units, the branch-six layer effect is sufficient to maintain the fluid or power flow in a particularly deflected flow pattern by the influence of the pressure distribution due to the asymmetric boundary layer effect and does not require other flows than the power flow to maintain the flow pattern. In this type of unit, an uninterrupted pressing of the control signal can of course also be used to create

keep the flow pattern of power flow-but. However, such flow patterns can be changed to a new stable flow pattern either by introducing or by removing fluid through one or more control nozzles, or by means of a control signal introduced by pressure changes in one or more outlet passages or channels, such as e.g. . by blocking the output channel to which the power flow is directed. (c) Boundary layer control devices having memory properties, i.e. where the latching properties dominate over the control signals produced by complete blocking of the outlet to which the current has been directed.

In boundary layer units of the memory type, the flow pattern can be maintained by the influence of the power flow alone, without the use of another current or without the uninterrupted use of the control signal. Also in these units, the flow pattern can be modified by introducing or removing fluid through one or more suitable control openings or nozzles. However, certain parts of the power flow pattern, including locking onto a particular sidewall, are maintained even if the pressure distribution in the outlet channel to which the current is delivered is modified, and even if this occurs to such an extent that the outlet channel is completely blocked.

The force flow deflection phenomenon in boundary layer units is produced by the impact of a transverse pressure gradient due to the difference in the effective pressures that exist between the fluid or force flow and the opposite side walls in the area of influence and for this reason the term "boundary layer control" is used. In order to explain this effect, it must initially be assumed that the main fluid flow or the power flow from the power nozzle is directed towards the tip of a centrally arranged separator. During the passage through the impact area or chamber, the fluid coming from the power nozzle will take with it a part of the surrounding fluid in the adjacent areas and remove this fluid from there. If the power flow is located e.g. slightly closer to the left side wall than the right side wall, it more effectively removes fluid in the area of influence between the flow and the left wall than fluid between the flow and the right wall, as the latter area is smaller. Therefore, the pressure in the left influence area between the left side wall and the power flow is lower than the pressure in the right influence area, and a pressure difference is created across the power flow which deflects it towards the left side wall. When the flow is deflected further towards the left side wall, it will take fluid from the left impact area with it even more effectively, and the effective pressure in this area is further reduced. In such units which exhibit locking properties, this feedback effect is self-reinforcing, and it produces the effect that the power fluid flow is deflected towards the left wall and that it is mainly led into the left receiving opening and exit channel. The flow adheres to and is then deflected by the left side wall when the power flow effectively touches or meets the left side wall at a certain distance downstream from the outlet of the power nozzle, as this location is normally referred to as the "contact point". These phenomena are termed boundary layer locking. Systems of this type can function completely symmetrically, because if the flow has initially been slightly more deflected towards the right sidewall than towards the left sidewall, the boundary layer locking will occur towards the right sidewall.

Control or control of these units can also take place by varying the control fluid flow to the boundary layer area from the control openings to such an extent that the pressure in the associated boundary layer area becomes greater than the pressure in the opposite boundary layer area located on the opposite side of the power flow, and the flow becomes deflected towards this opposite side of the device.

Instead of a control flow to the boundary layer area controlling the device, fluid can alternatively be removed from the "opposite" control opening to effect a similar control or control, by lowering the pressure on the "opposite" side of the fluid circulation instead of increasing the pressure on the first side . The control flow can have such a speed and volume that it partially deflects the fluid or power flow by impulse exchange, so that a combination of these two effects can be used.

Only a small amount of energy is required in the control signal fluid to change the path of the power flow so that all or part of it is intercepted by the load device or the output channel. For a continuous control signal, the power gain in fluid control systems can be considered as corresponding to the ratio between "the change in the power delivered by the amplifier to the output channel or the load", and "the change in the control signal power" which is necessary to provide the change in the emitted or delivered power to the output channel or the load. In a similar way, the pressure gain can be considered as corresponding to the ratio between the "change in output pressure" and the "change in control signal pressure" necessary to provide the change in output pressure, and the mass flow gain can be considered as corresponding to the ratio between "the change in the mass flow in the output channel and "the change of mass flow but of the control signal".

Power, pressure and mass flow amplifications of 50 times can be achieved with an amplifier stage of the type described. A particular device does not normally produce gains of this magnitude for all three parameters, and the devices are usually designed to provide the optimum gain for a particular parameter.

It is thus clear that the boundary layer effect provides a feedback effect in a fluid amplifier system and thus has an important influence on its gain, sensitivity to input or control signals, sensitivity to control signals introduced by loading (affecting the pressure at the receiving ports or output channels), the system's response time, frequency characteristics and memory. This feedback action can, as in electronic systems, be used for data processing or digit operations, logical operations, memory operations and also to provide continuously variable output signals. Each of these types of operations or modes exhibits sensitivity to fluid control signals that change the ratio of net fluid flow to and from the area of influence near the main power flow.

For simplicity, a two-dimensional system is described above. However, the invention can also be realized as three-dimensional systems, such as e.g. rotationally symmetric units resulting from rotation of a two-dimensional system's ground plan about an axis that coincides with the centerline of the power nozzle, rotation of the right or left half of a plan about an axis that is parallel to, but offset from, the above-mentioned center line, or rotation of a floor plan about an axis perpendicular to the center line, but lying in the plane of the floor plan so as to provide a toroidal construction of the unit.

Although symmetric units are discussed above, it is also clear that

the invention also relates to asymmetric units of the described types and combinations of these types. For example a two-dimensional unit can comprise a right half belonging to type (c) and a left half in which the length of the left side wall is less than the distance between the outlet of the power nozzle and the front edge of the separator. For such a unit, the left half of the unit acts as a boundary layer unit of type (b), while the right half acts as a boundary layer unit of type (c).

It will be understood that this second class of pure fluidic amplifiers and systems includes devices that can be connected to other devices (eg, as well as Class I as well as Class II devices), where the output signal of one device can provide a fluidic or power flow for the second unit, hereinafter referred to as a series connection, and alternatively where another unit may be used in such a way that its output channels provide a control fluid signal flow in either the former or the second unit, hereinafter referred to as a parallel connection. Alternatively, the output signal of a Class II unit may be fed back to its own control nozzle system as an additional control signal through external feedback circuits in a manner described in Swedish Patent No. 197 158. It should be noted that pure fluid amplifiers do not require amplifiers using pure fluid. The term "pure fluid amplifier" applies to such amplifiers in which the amplification is achieved exclusively through the use of a fluid without the need for moving mechanical parts. The fluid used can be pure, or a mixture of fluids, or contaminated fluids, or fluids with entrained or suspended solids, and the term "fluid" applies to both compressible and non-compressible fluids.

Other purposes and advantages of the invention will be apparent from the following description and attached drawings, where: Fig. 1 is a ground plan of a fluid-driven system according to the invention. Fig. IA is an end view of that in fig. 1 showed a system with means that supply fluid to the system. Fig. 2 is a ground plan of another embodiment of the one in fig. 1 shown system. Fig. 2A is an end view of the one in fig. 2 showed an embodiment with means that supply fluid to the system. Fig. 3 schematically shows a device that uses the system shown in Figs. 1 and 2. Fig. 4 shows another fluid-driven unit that uses the system according to the invention. Fig. 5 shows another embodiment of the fluid-driven system according to the invention. Fig. 6 is a plan view of a multistable fluid memory system according to the invention. Fig. 6a is a partial plan view of fig. 6. Fig. 7 shows a fluid driven unit using that of fig. 6 showed multistable fluid memory system, and

fig. 8 shows a plan view of an asymmetric boundary layer unit.

Fig. 1 and IA show an embodiment of the multistable fluid-driven system according to the invention. The fluid-driven system denoted by 10 consists of three flat plates 11, 12 and 13. The plate 13 is placed between the plates 11 and 12 and is tightly sealed between these two plates by means of machine screws 44. The plates 11, 12 and 13 can consist of a any metal, a plastic material, a ceramic or other suitable material. In the present example, the plates 11, 12 and 13 consist of a clear plastic material. It is obvious that the plates can be joined by means of adhesives or other suitable means.

Patterns or cavities cut in the plate 13 provide an impact area or chamber 14, a power nozzle 15, a control nozzle 16 and outlet passages or pipes 17 and 18. The power nozzle 15 and the control nozzle 16 are located close to each other and at right angles to each other. The total fluid pressure delivered by the power nozzle 15 shall be denoted in the following as Psii. The nozzles 15 and 16 respectively form the narrowed power or main fluid nozzle neck 15a and the control nozzle neck 16a which form openings in the chamber 14. The term "neck" used here means openings with parallel, converging or diverging walls or with which preferably conventional form. The inlet ends 15b and 16b of the nozzles 15 and 16 are in connection with the bores 20 and 21 (fig. IA) in the plate 12. The outlet ends 17b and 18b of the passages or pipes 17 and 18 are in connection with the bores 22 and 23 in the plate 12.

The openings 17a and 18a form mouths for the outlet passage or pipes 17 and 18 can lie symmetrically at a distance from the power nozzle 15. The separating device or member 120 can be arranged symmetrically or asymmetrically between the openings 17a and 18a and the passages 17 and 18. The leading edge of the separating member 120 defines the inlet to the openings 17a and 18a. Both openings 17a and 18a have equal cross-sectional areas in this out-

form of execution. Two opposite divergent side walls 19 and 19a which partially delimit the impact chamber 14 continue as the outer walls of the outlet passages 17 and 18 and form together with them a smooth, uninterrupted surface.

The bores 20, 21, 22 and 23 are internally threaded so that the pipes 25, 26, 27 and 28, which are externally threaded, can be placed

tightly fitting in their respective bores.

The end of the pipe 25 extending from the plate 12 is connected to a pressure fluid source. This source is denoted by 31. The pressure fluid can be air or another gas, or water or another liquid. It has been found that a gas with or without solid or liquid particles works very satisfactorily in the system 10. The gas can be used in the control nozzle 16 to influence the flow of liquid from the power nozzle 15, or the control nozzle can be supplied with liquid and the power nozzle supplied with a gas. The liquid may also contain solid particles or gas bubbles. A fluid control valve 62 may also be used in connection with the source 31 to ensure an uninterrupted flow of fluid at constant pressure. Such fluid control valves are of course known.

The reference numeral 35 similarly to 31 represents a pressurized fluid source.

The reference number 33 schematically represents a means which causes a fluctuation or change of the fluid pressure in the pipe 26, i.e. that 33 represents a source for a control signal. Considered together, the combination 35 and 33 can be understood as an input system that causes a change in the amount or pressure of fluid in the pipe 26.

To explain the operation of the control system according to the invention, reference should be made to fig. 1. When pressure fluid is delivered to the power nozzle 15, a flow takes place through the power nozzle which provides a fluid flow which is also designated as power flow. Initially, the fluid or power flow passes through the impact area or chamber 14 substantially undeviated. Due to the mutual influence between the power-flow fluid and the surrounding fluid, the surrounding fluid is accelerated in the direction of the power flow as a result of the impulse exchange. By this entrainment of fluid surrounding the power flow, fluid on either side of the power flow is led out of the impact chamber or area 14. This effect lowers the pressure on either side of the power flow, and fluid from the outlet passages 17 and 18 flows back through the receiving openings 17a and 18 in parallel with the walls 19 and 19a in the impact area 14 to replace the fluid entrained and removed by the power flow.

The power flow through the impact area 14 creates turbulence in this area and thereby pressure disturbances will occur, i.e. uncontrolled, rapidly varying changes in the pressure across the power flow. These pressure disturbances deflect the power flow slightly so that it obtains an asymmetric flow pattern, as this effect becomes more pronounced the greater the effective length of the side walls 19 and 19a. The effective length of these side walls can be regulated by limiting the length of the side walls or by changing the direction of the side walls as shown in fig. 1, so that the angle between the side walls and the power nozzle's axis of symmetry or center line C-C increases or decreases as desired, or by placing the front edge of the separator 120 in such a way in relation to the distance from the neck or the outlet 15a of the power nozzle that the separator forms a screen between the power flow and a of the side walls 19 or 19a. This tendency to asymmetry or deflection of the force flow is reduced by shortening the effective length of the side wall 19 or 19a, or by leading the side walls more at an angle outwards, or by placing the front edge of the separator 120 closer to the outlet of the power nozzle neck 15a. The above asymmetry can exist in the absence of a control fluid flow either into or out of a control chamber 16 through the control nozzle orifice or throat 16a. Further explanation of the relationship between the effective length of the sidewalls and the system's operation or characteristics will be given later.

Now assume that the deflection occurs in the direction of the side wall 19. This deflection reduces the area between the power flow and the side wall 19 and prevents and reduces the backflow from the opening 17a to the right boundary area which is limited by the right side wall 19, the end wall of the impact area and the power flow, which boundary area is evacuated by entrainment due to the power flow. In a similar way, the backflow along the side wall 19a in the left boundary area is facilitated by simultaneously increasing the area between the side wall 19a and the power flow, through which area fluid can flow into the left boundary area when it is evacuated by the power flow. The extent to which this transverse pressure difference is self-sustaining depends on the fluid flow in each of the two opposing boundary areas. In fig. 1 is e.g. the distance between the leading edge of the separator 120 and the side walls 19 and 19a large in relation to the width of the power nozzle neck 15a. As a result, there will be a gap or a space between the power flow and the side walls 19, resp. 19a. A similar situation exists when the side walls 19 and 19a terminate closer to the nozzle neck 15a than the leading edge of the separator 120. In such cases, fluid can flow through this gap to increase the pressure in the boundary region in the same way that a control flow in the right boundary region through the control opening 16a will increase the pressure in this border area. A flow from the area at the openings 17a or 18a to the boundary area is referred to as backflow or counterflow. In this example, this backflow or counterflow reduces the tendency for a further reduction of the effective pressure in the boundary region. In certain systems or devices, this effect of the boundary layer effect can be used to limit the feedback effect and provide a continuously variable control or control of the power flow deflection and thereby of the amplitude of the output signal.

As regards the system of fig. 1, it is clear that when the gap between the side wall 19 and the power flow is further reduced, the backflow to the right boundary layer region is further modified or reduced. This modification produces a reduction in the effective pressure on the right side, while the effective pressure in the left boundary area increases to the pressure level of the surrounding fluid, as in the one in fig. 1 is the back pressure in the outlet passage or channel 18. The resulting transverse force deflects the force flow towards the side wall 19. When the side walls 19 and 19a are sufficiently close to the leading edge of the separator 120, the force flow eventually touches the wall 19 in a "touch" -place". When this happens, the power flow produces a "closed" boundary area or a layer limited by the end wall of the impact area, the side wall 19 and the power flow. The flow to the closed boundary area from the receiving opening 17a is now essentially finished, and the pressure in this boundary area is further reduced by entrainment caused by the power flow. This causes the point of contact to move closer to the throat 15a of the power nozzle 15.

It is possible to change the effective pressure in the right boundary area (near the side wall 19) by introducing control fluid through the control nozzle 16, so that the effective pressure in the right boundary area is increased and the power flow is deflected towards the side wall 19a. It is also possible to remove fluid from the right boundary area through the control nozzle 16 and thereby reduce the effective pressure in the right boundary area and to deflect the power flow towards the side wall 19. Such control signals can be introduced by conventional means, or as a signal from another pure fluid amplifier unit (which signal acts as a change in the fluid's pressure, mass flow, or power), and which is delivered to the control nozzle 16.

Assume that a control signal is introduced through the control nozzle 16 and its neck 16a, so that it deflects the power flow towards the side wall 19a. A larger part of the power flow will flow to the opening 18a than to the opening 17a. If the back pressure in the outlet passage 18 is increased, e.g. by blocking the pipe 23, a resulting pressure increase will be carried back along the side wall 19a to the left boundary area and increase the effective pressure in the boundary area. Depending on the current strength of the control fluid circulation from the control nozzle neck 16a, such a back pressure can be used, e.g. as a result of the blocking, that another type of control effect is provided, whereby the power flow will be deflected away from the wall 19a by the influence of the back pressure control signal.

In fig. 2 is the curved or curved design of those in fig. 1 sidewalls modified to provide flat, diverging sidewalls between the neck 15a of the power nozzle 15 and a point at a level with the leading edge of the separator 120. Furthermore, another, or left, control chamber 32 is arranged with a control opening 32a so that, in addition to the control signals that act in the control chamber or nozzle 16, and in the opening or neck 16a, oppositely acting similar signals can appear in the control chamber 32 and the control opening 32a. It is clear that more than one control opening and corresponding control signal can be arranged in one or all boundary areas, and this is shown in fig. 5.

Figs. 2 and 2A show a modification of the multistable fluid driven control system shown in Figs. 1 and IA where like reference numbers correspond to like parts or elements. This modification is denoted by 10a. In the system 10a, another control nozzle or a chamber 32 is placed horizontally just opposite the control nozzle 16. The control openings or nozzle necks 16a and 32a have approximately the same diameter and mouths

out into the area of influence 14. The inlet end 32b of the control nozzle 32 is connected to the pipe 47 which is threaded into the bore 34. The numbers 33a and 35a denote means which are equivalent to the means denoted by 33 and 35. A fluid control valve 62 ensures that the system 10a gets a constant fluid pressure from the source 31.

In fig. 2, the leading edge of the separator 120 is placed at a distance of approximately eight "discharge widths of the power nozzle 15" from the outlet or neck 15a of the power nozzle 15. The angle between the center line c-c of the power nozzle and the side wall 19 is approximately 12°. The system is essentially symmetrical about the centerline of the power nozzle. These conditions provide a system that exhibits "stuck", whereby the power flow touches one or the other of the side walls 19 or 19a as a result of the asymmetric entrainment, in the absence of a control signal or under the influence of a control signal, and remains in this state of flow even though all control signals cease. Upon impact of an oppositely acting control signal of sufficient strength, the power fluid flow will change its path to the opposite outlet passage so that a bi-stable or "flip-flop"-like effect is provided. When the power flow is deflected, e.g. against

the side wall 19 of a transverse effective

pressure difference between the boundary areas, the power flow is curved and often has a velocity component which is directed towards the side wall at the point of contact. When the power flow hits the side wall 19, in such cases a local pressure distribution occurs which modifies this velocity component of the local power flow. This

local pressure increase acts back on the adjacent boundary area and makes the pressure

in the boundary area higher than it would have been if the local power flow ran parallel to the side wall at the point of contact. This effect, and the previously described mutual influence of the different currents, limits the minimum distance of the point of contact from the power nozzle throat for any particular system construction and power current impulse.

It is clear that if e.g. the discontinuity in the demarcation of the area of influence or the lateral displacement (the transverse distance between the power nozzle throat and the side wall) of the system in Figure 1 is reduced to e.g. that shown in Figure 2, the point of contact will be closer to the power nozzle neck for a given amount of movement or impulse of the power flow because the transverse distance that the flow must be deflected is reduced.

It is also clear that for a certain lateral displacement the distance to the point of contact from the power nozzle neck in the one in fig. 2 showed system design to increase with increasing divergence angle for the side wall, i.e. the angle between the center line c-c and the tangent to the side wall. Although fig. 2 shows divergence angles of 12°, and fig. 3 shows divergence angles of 0°, it is clear that other angles can also be used. This divergence angle, the lateral displacement S, the width of the power nozzle throat (TWI<+><T>W1!) and the effective length of the sidewall 19 or 19a (see Fig. 1), provide interdependent effects on the power flow. For example constitute the previously described dimensions or parameters for a specific fluid type, fluid speed and thermodynamic state of the fluid, parameters that determine the performance of the system or unit. Consider e.g. a unit having a left side wall with zero lateral displacement, a divergence angle equal to zero for the left wall, and zero effective length of the right side wall, i.e. a divergence angle equal to 90°. When the power flow begins to flow, it will lock onto the left side wall 19a. Assume for the sake of clarity that this side wall 19a is turned slowly in a clockwise direction about the connection point with the end wall in the impact area 14. The power flow will remain locked to the side wall 19a until a maximum divergence angle is exceeded, where the power flow will detach from the side wall 19a. For an angle greater than the maximum, power flow can be deflected to a locked flow pattern at the side wall 19a by means of a control signal, but it will detach when the control signal ceases. Let's then reduce the divergence angle to the aforementioned maximum angle. In this case, the power flow will not be locked again in the absence of a control signal. The divergence angle must decrease further to a minimum value at which value the power flow will be locked again without a control signal. For an angle less than the maximum and greater than the minimum, the power flow can therefore be deflected to a locked state by the influence of a control signal and will remain locked when the signal ceases.

What is stated above mainly concerns submerged currents, e.g. a liquid stream surrounded by a liquid, or a gas stream surrounded by a gas. The parameters of the power flow and the surrounding fluid determine the entrainment properties or effect. These parameters thus affect what happens in the area of influence. An extreme effect of these parameters occurs when the power flow is a liquid and the surrounding fluid is a gas or steam. This extreme condition is known as a "free beam". The final values of the minimum and maximum divergence angles are usually different for a free and for a submerged jet, and the lock-in angle or minimum divergence angle is usually significantly less for a free jet than for a submerged jet or stream. For given functional requirements or properties, it is thus important to know that the detailed form of the influence area depends on the parameters of the surrounding fluid and of the power flow fluid.

A further effect is the direction of the side walls at the point of contact of the power flow. A rotation of the side wall in the same direction as the deflection of the power flow reduces the change in the local static pressure due to the contact of the power flow with the side wall compared to the pressure when touching at the same place on a side wall that is parallel to the center line of the power nozzle 15 This variable size enables the generation of an even lower effective pressure in the adjacent boundary region.

With reference to fig. 2 and 2a, it is important that a control signal can be applied by a combination of control currents through the control nozzles, where each control current can flow into or out of the boundary area. Also, the control flow influences the power flow path, although the control flow has no impulse component across the original direction of the power flow as the control fluid flows out or in through the control nozzles. However, a control fluid having a transverse impulse component can interact with the boundary layer's steering or control properties to improve the system. These systems can thus use a combination of the branch-six-layer control effect and the impulse effect.

Some of these control systems include an impulse exchange between the power flow and the surrounding fluid. The impulse exchange or entrainment takes place to varying degrees when a fluid flow passes through a region whose pressure is not zero. Such entrainment together with the losses due to friction etc. impairs or weakens the power flow as it moves away from the power nozzle neck 15a. These losses increase with the distance from the power nozzle neck, and therefore it is generally desired, for reasons of output pressure and output power, to place the receiving openings as close to the power nozzle neck as possible. The location of the openings 17a and 18a in fig. 2 is dependent on the location of the leading edge of the separating member 120 as the tip of the separating member 120 to provide a locking should be relatively close to or slightly past the point of contact of the power flow on the side walls. Thus, it is advantageous for the locking devices or systems of the one in fig. 2 shown type to cause contact to occur close to the power nozzle neck.

As mentioned earlier, the operation of a particular design of the system depends on the pressure in the power flow. The operation of the one in fig. 2 and 2a shown unit is dependent on the power flow not simultaneously touching both side walls 19 and 19a, when it flows out from the power nozzle 15. In the case of a compressible fluid and the pressure of the power flow is increased to the extent that the flow expands and at the same time both side walls 19 and 19a touch, the power flow will equally effectively lower the pressure in the boundary layer between the flow and each side wall. In the absence of a control signal, the pressure on each side of the flow is reduced to the same extent, and there is little or no effective transverse pressure difference. The current is thus not deflected, and if the separator 120 is placed symmetrically between the side walls 19 and 19a, the current is distributed equally on each side of the separator 120 between the openings 17a and 18a.

Under these flow conditions, a sufficient control flow is now introduced, e.g. through the control nozzle neck 16a to increase the pressure in the right boundary layer area. The main fluid or power flow releases itself from the side wall 19 and is deflected towards the opposite side wall 19a. The fluid flow will now much more effectively remove fluid from the left than from the right boundary layer area, and a large part of or all of the flow then flows to the opening 18a which is opposite to the control flow but from the nozzle neck 16a. When the control flow from the neck 16a ceases, the fluid or power flow again touches both side walls 19 and 19a and regains its original symmetrical flow pattern.

By using this type of boundary layer control, a small control flow can deflect a very strong main fluid flow or power flow. Using control and power nozzle throats of the same cross-sectional area and shape, a 0.14 kg/cm2 change in control air pressure on one side can produce a sufficient change in control air flow to deflect the largest portion of an air power flow by 6.3 kg/cm2 pressure from the symmetric flow form to an asymmetric flow form.

To give an example of the application of that in fig. 2 shown system, this can be used for comparing fluid signals for both pressure, mass flow and effect in a fluid. A signal of a certain amplitude may act on the control nozzle 16, causing the power flow to initially become stuck on the left side wall 19a. If now a signal acts on the control nozzle 32, the power flow is deflected to the right side wall 19, but only when the latter signal with a certain strength or amplitude exceeds the signal acting on the nozzle neck 16a. Thus, when the power flow is deflected to the outlet passage 17, the signal acting on the nozzle neck 32a exceeds a certain value which is dependent on the strength of the signal acting on the nozzle neck 16a. This is a typical comparison effect. A change in the signal acting on the nozzle neck 16a makes it possible to choose the comparison level as desired. The signals described above can be produced by adding or withdrawing fluid from the area of influence through the control nozzles.

As shown in fig. 1, the side walls 19 and 19a in the impact area 14 diverge in the opposite direction and their extension forms walls for the outlet passages 17 and 18. The side walls 19 and 19a can also be parallel along their entire length. The wall 19 is shifted aside a distance SK from the edge at the intersection between the control nozzle neck 16a and the power nozzle neck 15a. ST represents a corresponding distance between the left edge of the power nozzle neck 15a and the side wall 19a.

The power fluid stream flows out from the power nozzle 15 under a total pressure Pfc]i, where P is indicated in kg per cm<2>. The dimensions XR and X, in fig. 1 and 2 denote the respective horizontal distances between the center line C-C and the nearest point on the walls 19 and 19a. The center line C-C lies in the middle of the nozzle neck 15a, between the opposite side walls 19 and 19a in the impact area 14, and the openings 17a and 18a. TW]( is the horizontal distance between the center line C-C and the closest point on the right wall of the power nozzle neck 15a. The dimension TWL is the horizontal distance between the center line C-C and the closest point on the left wall of the power nozzle neck 15a. aK and aL are for-

SK (cm) SL (cm)

hold between , respectively

TWR (cm) TWL (cm)

As the opposite side walls 19 and 19a are offset aside from the control nozzle neck 16a, an area where the fluid velocity is less than the velocity of the power fluid flow from the nozzle 15 will be found next to the walls 19 and 19a between the front part of the side walls and the openings 17a and 18a . This area where the fluid moves at a lower speed than the power flow from the nozzle 15 will be referred to below as an artificial boundary layer or area. This area works in such a way that fluid from the nozzle 15 is locked onto the side walls 19 and 19a when fluid flows out of the nozzle 15. If a fluid is introduced into this area from a suitable source, e.g. a control nozzle, it will bring the locking effect to zero or reduce it. This feature provides a boundary layer control of power fluid flow.

In fig. 1 and 2, the separator 120 is placed with its leading edge at a distance of approximately 8 neck diameters from the nozzle neck 15a. Furthermore, the separator 120 is placed so that it divides the area 14 into two equal parts, so that the openings 17a and 18a are symmetrical and a is 2. If a has this value or is lower, and the values for Psn are greater than 5.6 kg/ cm<2> overpressure, the power flow will flow symmetrically or in equal amounts to the outlet passages 17 and 18. The flow is then in the so-called "neutral state" because it is distributed equally between each opening. For the above-mentioned value of a and P.,n, the flow state is stable. If the values of a are greater than 2 and the values of P,n are less than 4.2 kg/cm<2 >overpressure, the "neutral state" becomes unstable, and the flow will easily change to an asymmetric flow pattern by a small disturbance or force acting on it.

In the absence of a fluid flow from the control nozzles, when the values of a are too small, i.e. less than 2, and the values of Psn are greater than 5.6 kg/cm<2> overpressure, and aL is equal to (xK, the ratio of the fluid quantities flowing to the outlet passages 17 and 18 will be approximately equal to one.Thereby the fluid flow will be in a stable neutral state and the flow will be symmetrical.

When the values for a are greater than 2 and the values for PK1| less than 4.2 kg/cm<2>

overpressure, and aL is equal to alf, a random small disturbance will immediately cause an asymmetric flow to one of the outlet passages. For larger values of a, the power flow's tendency to lock onto the side wall 19 which is opposite the side from which the disturbance acts,

increase up to such values for a where current cannot be locked due to the large distance between the side walls 19 and 19a.

When the values for a are small or large and a, is not equal to aK and the separator 120 is shifted in relation to the center line C-C, so that one opening is not smaller than the other, the flow will not be symmetrical and there will take place a boundary layer control or control which will cause the power fluid flow to be locked to the side wall 19 or 19a which is located at a greater distance from the separator 120, unless this distance is so large that the flow cannot be locked due to the large distance between walls 19 and 19a.

When the separating member 120 and the side walls 19 and 19a are placed symmetrically with respect to the power nozzle neck 15a, the power flow will be symmetrical when « is less than 2, P;.n is greater than 5.6 kg/cm2 overpressure, and when there is no flow from one of the control nozzles 16 or 32. If a fluid flow under these conditions is introduced from a control nozzle, e.g. from the nozzle 16, the main or power fluid flow from the power nozzle 15 will, due to the boundary layer control, change its main flow path to the outlet passage 18 which is located opposite the control nozzle 16. When there is no flow from the control nozzles, the power flow will return to the neutral or equally distributed flow pattern. If a simultaneous flow were to occur from both control nozzles 16 and 32, the control nozzle which provides the largest amount or proportion of fluid to the boundary layer for the power flow from the nozzle 15, will cause the flow to move with a clear deflection effect to the opening located opposite to the nozzle which produces the dominant control fluid flow. Successive alternating increases in the amount of fluid from the respective control nozzles will cause successive, alternating stable movements of power fluid flow from one opening to the other. This effect is referred to in the following as "multi-double path change".

If the separator 120 is placed asymmetrically in relation to the nozzle 15, and when a is greater than 2 but lower than the limit value for locking and P„„ is less than 4.2 kg/cm<2> overpressure, the entire power flow in the absence of fluid from the control nozzles pass through the outlet passage that has the largest inlet opening. The flow from the control nozzles can be steady or pulse-shaped. The power flow will remain deflected to the opening to which it last spoke directed by the control nozzle even if there is no further flow from the control nozzle. When fluid flows from both control nozzles at the same time, and if the flow from one control nozzle is sufficiently much greater than the flow coming out of the other control nozzle, the nozzle with a larger fluid flow will deflect the power flow flowing out of the nozzle 15 by causing a change in the boundary layer pressure distribution. This causes the power flow from the nozzle 15 to be completely deflected due to the boundary layer control effect. Furthermore, successive, alternating and sufficiently large increases in the flow from the respective control nozzles will cause successive deflection of the power flow coming out of the power nozzle 15.

As small pressures from the control nozzles 16 and 32 cause large changes in the movement of the power flow with higher energy from the nozzle 15, the effect of the fluid from each control nozzle is amplified in each embodiment.

The values of a and PSM will vary depending on the requirements for each particular embodiment. The invention is therefore not limited to particular values of a and P_H.

Those skilled in the art will realize that for certain specific widths of the separator 120 and distances between the walls of the openings, modifications of the systems 10a and 10b are provided, in which the power fluid flow can be locked onto one of the walls of the separator 120 in addition to the walls 19 and 19a. This feature is termed "multistable switching" because the fluid flow can be stable in any of four possible positions, i.e. it can be stuck on any of four possible walls against which it is directed by fluid pressure from one or both control nozzles .

Fig. 3 illustrates a possible embodiment that uses that in fig. 2 showed system where the openings 17a and 18a and the outlet passages 17 and 18 are arranged symmetrically in relation to the line C-C. As shown in fig. 3, 40 denotes a projectile equipped with a rocket motor 41. When the projectile is launched, a small part of the exhaust gas from the motor 41 enters the opening 42 on the side of the rocket motor. These gases pass through the pipe 25, so that the nozzle 15 delivers hot compressed gas in equal quantities to the outlet passages 17 and 18. The ends of pipes 47 and 26 are connected through valves 62a and 62b to a source of compressed gas, e.g. nitrogen, 44. A gravity control unit 43 is able to open and close the valves 62a and 62b depending on the course change of the projectile 40.

The source 44 supplies fluid to the control nozzles 16 and 32 which are connected to the tubes 47 and 26.

As those skilled in the art will understand, a course shift of the projectile 40 will be detected by gyroscopes or other conventional devices in the control unit 43, and this unit will then mechanically open or close one of the valves 62a and 62b, so that the tube 47 or 26 is inserted connection with the source 44. As a result, one of the control nozzles 16 or 32 will deliver a nitrogen jet or .

current, and the hot gases flowing out from the nozzle 15 will be sent out of the opening 45 or 46 in the side of the projectile 40. If

e.g. the projectile changes its trajectory in the direction of the arrow Y, the unit 43 will detect this trajectory change and open the valve 62a, so that the power flow from the nozzle 15 will pass through the passage 17 and out through the opening 45. Hot gases emitted in such a way provide a reaction force which is sufficient to allow the projectile 40 to rotate about its center of gravity until the projectile is once again in its correct path.

That in fig. The system shown in 3 can also be used to regulate the pitch of the projectile by suitably arranging further openings which lie directly opposite each other and so that they open into the outer surface of the projectile. A conventional pitch angle sensing gravity control unit can be used to open valves similar to valves 62a and 62b and connected to the control nozzles so that directional deviation is compensated by the reaction force provided by the hot gases from the engine 41 which flows more tangentially from the surface of the projectile 40.

Fig. 4 illustrates a fluid driven element 100 using that of Fig. 1 and 2 showed system, but where the passages 17 and 18 and the openings 17a and 18a are asymmetrical. One way of producing asymmetry consists in

to move the flow distributor or separator 120 closer to the passage 17, so that the power flow from the nozzle 15 will not be distributed equally between the outlet passages 17 and 18.

In this embodiment, a pair of rollers 50 and 51 are rotatably mounted and feed a continuous strip 52 of metal or other material, in the direction of the arrow to the punch press cylinder 54. In order to operate the punch press safely and efficiently, two conditions must be met. The first condition is that there is a strip 52 that is fed under the perforating or punching member 59, and the second condition is that the worker removes his hands from the punch 59 before separating the material from the strip 52. As shown, the punch 59 is fixed on and driven by a piston 156 in the cylinder 54. The punch 59 is usually brought out of contact with the strip 52 by means of the coil spring 55. To ensure that both conditions are simultaneously fulfilled, before the punch 59 comes into operation, they are in fig. 1 and 2 shown systems combined, and all passages or openings are arranged asymmetrically in relation to the power nozzles and nozzle necks therein, by means of an asymmetrical arrangement of the separator 120. The systems are combined into a single unit 56, and it comprises the same layered construction as the individual systems shown in fig. 1 and IA and in fig. 2 and 2A.

The unit or system 56 comprises a pneumatic pressure source 57 which is capable of continuously supplying compressed air to the four pipes 58, 59, 60 and 61. The pipe 61 is connected to a storage container 62. The pipe 63 which extends from the container 62 , pressurized fluid escapes to the atmosphere at a very slow and constant rate when the strip 52 blocks the end of the pipe 63. Rollers 53 cause the strip 52 to provide a relatively tight and uninterrupted cover for the end of the pipe 63. When the strip 52 no longer covers the pipe 63 because the material from the roll 50 is used up or because the strip 52 is interrupted, the pipe 63 will be able to momentarily release all the air from the container 62 into the atmosphere. The pipe 63 has an extension 64 which extends from the container 62, and is in connection with the control nozzle 16. The control nozzle 16 is essentially identical to the control nozzles 161, 162, 163 and 164, the latter nozzles constituting the other control nozzles for the unit 56. The pipe 60 connects the pressure source 57 to the power nozzle 15. The power nozzles 151, 152 and 153 are similar in their construction to the nozzle 15 and form the various power nozzles in the unit 56. The pipe 58 connects the control nozzle 164 through the valve 65 to the pressure source 57. The passage 17 and the passages 171, 172 and 173 are all asymmetric with respect to the passage 18 and the respective passages 181, 182 and 183 due to the asymmetric location of the separators 120. The tube 67 connects the passage 17 with the control nozzle 161, while an identical tube 671 connects the passage 171 with the nozzle 162, as shown.

Initially, the entire airflow, except from the power nozzle 15, will flow into the passage 18 due to the asymmetry between the passages 17 and 18. Air entering the passage 18 and the similar passages

181 and 182, escape from unit 56 into the atmosphere. When the control nozzle 16 delivers an air flow due to the strip 52 covering the pipe 63, the flow from the nozzle 15 will change its path from the passage 18 to the passage 17. Thus the former condition, namely that the pipe 63 is covered by the strip 52, must be fulfilled before the power nozzle 151 gets air.

Part of the air that enters the passage 17 passes through the tube 67 and into the control nozzle 161. The tube 68 connects the nozzle 161 to the opening 69 in the side of the punch cylinder 54. If the opening 69 is opened (as shown), air from the pipe 67 pass through the pipe 68 and out of the opening 69 to the atmosphere. Thus, if the opening 69 is not covered by the worker's one hand, no air will flow out of the nozzle 161 against the power flow, with the result that the remaining air or power flow coming out of the nozzle 151 will pass through the pipe 181 and out of the unit 56 If, however, the opening 69 is covered by the worker, the pipe 68 will be blocked, and air from the pipe 67 will introduce additional air to the control nozzle 161, whereby the nozzle 161 will supply a control flow and deflect the power flow from the nozzle 151 to the passage 171.

If the worker with his other hand does not similarly cover the opening 69a, air from the pipe 671 will escape from the unit 56 through the pipe 681, but when the opening

69a is closed, the tube 681 will be blocked, and the control nozzle 162 will deliver an air flow sufficient to cause air from the power nozzle 152 to enter the passage 172 and not the passage 182.

The power nozzle 153 receives air from the pressure source 57 through the pipe 59. Air coming from the passage 172 out of the control nozzle 163 will force the power flow from the nozzle 153 to enter the passage 173 instead of the passage 183 which is connected to the atmosphere. The pipe 70 is connected to the end of the passage 173 and is connected to the piston 156, so that air from the nozzle 153 will press down the punch 59 against the action of the resilient spiral spring 55, whereby the punch 59 separates the material from the strip 52.

The control valve 65 provides an additional safety, because if the worker's foreman detects a dangerous situation, he can momentarily open the valve 65, so that a jet of air with considerable pressure will escape from the control nozzle 164. This jet will cause the air to change its path from the passage 173 to passage 183 where it exits unit 56.

Fig. 5 illustrates another embodiment that uses multiple control flows to deflect the power flow exiting nozzle 15. Control nozzles 184 and 185 are similar to control nozzles 16 and 32, and control nozzles 184 and 185 can respond to any additional fluid cones. -control currents or signals, so that they provide a further control or control of the fluid flow coming out of the power nozzle 15.

It should be clear that more than two control nozzles and receiving apertures may be in communication with the impact area 14. The nozzles and apertures may be so arranged that the power flow may be switched to any one of these apertures.

Fig. 6 illustrates a multistable fluid system 10b according to the invention, which system has memory properties. Same reference number on fig. 6 means corresponding parts as in fig. 2 and 2A. The system 10b consists of the same layered plate construction as the systems 10 and 10a, and is provided with bores which are in connection with the input ends of power and control nozzles. Suitable pipes can be threaded into these bores.

The system 10b is provided with side walls 19 and 19a, which, as explained earlier, are offset laterally. However, the side walls 19 and 19a do not form smooth uninterrupted surfaces between the walls 17d and 18d in the passages 17 and 18, as in fig. 2 and 2A. The side walls 19 and 19a are instead led to intersect or cross with the walls 17d and 18d to produce a sharp change in the wall direction at the edge 51, respectively 51a. The sudden change in wall direction is shown as approximately chin-shaped in the drawing. Although the change in wall direction shown is chin-shaped, any sudden change in wall direction will be sufficient when it leads to the formation of a fluid vortex system, whereby boundary layer feedback over the sharp change in wall direction is avoided. In addition to the sharp change in wall direction at the edges 51 and 51a, it is assumed in the system 10b that the passage formed by the wall 19 and the separating member 120, and by the side wall 19a and the member 120, is larger than the minimum size required for flow through this of the entire fluid flow from the power nozzle 15.

In short, the system 10b allows the power or fluid flow to flow into the openings 17a and 18a along the walls 19 and 19a, and that after a partial complete reversal of the flow, as a result of the back pressure in one of the passages, it flows out of the opening 17a or 18a along the separator 120 and around the end thereof and into the opening 18a,

respectively 17a. Partial or complete reversal of the current in these openings is

caused by a partial or complete closure of either outlet 17b or 18b from the outlet passage.

If an equal sensitivity to control signals from the right and left control nozzles 16 and 32 is desired, the separator 120, the walls 17d and 18d, the side walls 19 and 19a and the power nozzle neck 15a are preferably arranged symmetrically in relation to the center line C-C. The outlet ends 17b and 18b of the passages 17 and 18 normally release air to the atmosphere or are connected to a suitable load.

The system 10b has memory properties. The term "memory" means that the power flow attempts to flow out into the orifice through which it is initially directed by the control fluid flow from one of the control nozzles, even after the control fluid flow has ceased and despite a partial or complete blocking the outflow from the relevant opening.

The system 10b differs from the systems 10 and 10a because in the latter two systems the power flow can permanently change its path by means of the back pressure in an opening in the absence of a control signal from one of the control nozzles. For example the control fluid flow from nozzle 16 in systems 10 and 10a will cause the power flow from nozzle 15 to flow out through passage 18. When control fluid flow has ceased and the static pressure in outlet passage 17 is only slightly different from the static pressure in outlet passage 18, the power flow will continue out through the passage 18. If, however, the static pressure in the passage 18 in the systems 10 and 10a is significantly greater than the pressure in the passage 17 due to narrowing of the fluid flow from the outlet end 18b, this pressure will act back along the side wall 19a, and increase the boundary layer pressure and cause the fluid flow to change its path and flow out through the opening 17a. As a result, the pressure in the passage 18 will decrease. Although the blockage of the passage 18 is then removed, power flow will continue to flow out through the opening 17a until the control fluid flow is introduced by means of the nozzle 16. Thus, when the systems 10 and 10a are loaded downstream of the opening 18a, it is necessary to continue with an introduction of the control fluid flow through the nozzle 16 and to maintain the flow of power flow in the opening 18a.

In the system 10b, it is not necessary to continue introducing the control fluid flow through the nozzle 16 to maintain the flow of the power flow to the opening 18a, when the outlet end 18 is blocked so that the static pressure in the passage 18 is significantly greater than the static pressure in the passage 17. Thus, system 10b allows intermittent or stationary loading of a system controlled by pulse-like input signals or currents instead of continuous currents.

The operation of a particular device or system of the boundary layer control type, such as a device with latching or memory properties, depends in part on the distance between the separator and the throat or outlet of the power nozzle. The location of the separator affects the unit's properties depending on the relationship between the pressures at the inlet and outlet end of the power nozzle as well as on the pressure drop in the power nozzle and on the pressure drop in the power nozzle, as well as on the overall design of the impact area. As described above, the effect of the impact area design on the device properties depends on the average angle of divergence between each sidewall and the centerline C-C of the power nozzle, on the distance between the centerline of the power nozzle and the nearest point on each sidewall, and on the curvature or shape of the sidewalls. To explain the effect of the separator's location, a unit must be described in which the side walls are flat and diverge at an angle of 12° in relation to the center line of the nozzle, and where the lateral displacement between the center line of the nozzle and each side wall is equal. At the outlet of the power nozzle, the side walls are separated by a mutual distance of approximately three widths of the power nozzle outlet or neck.

The following description of the relationship between the position of the separator 120 and the system's operation is, for the sake of clarity, limited to the use of the fluid "air" introduced under a pressure of up to 3.9 kg/cm- absolute, while the outlet channels or passages are directly connected with a ambient pressure of approximately 1 kg/cma absolute. The relationships described in detail also depend on the type of fluid, on the thermodynamic state of the fluid and on the minimal local pressures in the system. The latter parameters are particularly important when using liquid fluid which causes local cavitation formation. The following description relates to systems operating in the absence of control signals, unless otherwise stated.

If the separator is located 0-2 power nozzle throat widths from the outlet of the power nozzle, the power flow will be distributed approximately equally in the absence of control signals, but the power flow can be forced to deliver a larger portion of the current to one or the other side of the separator by using a suitable control signal difference. When the separator is located 0-2 power nozzle neck widths from the power nozzle, the effect of the side walls in the absence of a control signal is insufficient to deflect the power flow, because the forces due to the pressure distribution over an effective length of the side walls of 0-2 times the width of the nozzle neck are very small. However, a pressure difference over this length will have some significance. Even such a small effective length of the side walls allows a greater deflection as a result of a control signal than that obtained by means of a pure current influencing unit. Therefore, the aforementioned forces are not without significance during the presence of the control signal. In addition to the above-mentioned factors, the current is split by the separator before the aforementioned small forces can become effective in the absence of a control signal. As a result, there is practically no deflection of the power flow in this symmetrical unit, where the simple separator is placed centrally, and the flow in the absence of a control signal is distributed essentially equally between the two outlet passages formed by the separator and the side walls extensions.

Completely different properties are provided when the separator is placed between three to four nozzle throat widths from the power nozzle outlet. In this case, the current is significantly affected by the boundary layer, so that even in the absence of a control signal, a larger part of the power current will flow to one side of the separator than to the other side. However, for this location of the separator, the effect of the side walls is insufficient to deflect the entire power flow to one side of the separator in the absence of a control signal difference. This happens because the separator is located relatively close to the outlet of the power nozzle, and the flow must be deflected at a large angle in order to reach all the way on one side of the separator. The corresponding forces that can be provided with the help of the available pressure distribution over a length of 3-4 times the nozzle neck width are still small due to the fact that there is only a relatively limited area of the side walls and power flow, where the available pressure difference can seem.

Yet another mode of operation is achieved if the separating member is placed between 5 and 2 nozzle throat widths from the power nozzle outlet. In this embodiment, the boundary layer acts on the power flow in such a way that, even in the absence of a control signal, it will flow completely into one of the passages formed by the separator. If, however, the outlet of outlet passage one is blocked in this case, the power flow will change its path to the opposite passage due to the resulting back pressure.

In this case, the surface area of the power flow over which the pressure difference can be effective is relatively large. The power flow is deflected close to the side wall slightly below or close to the front edge of the separator, and will therefore block off a boundary layer area which is evacuated by entrainment of the power flow on one side and which is limited on the other side by the adjacent side wall. This causes an increase in the effective pressure difference across the power flow. The increased pressure difference acting on a relatively large surface of the flow deflects it to a sufficient extent that it can flow into an outlet channel or passage, i.e. to one side of the separator and can become stuck at the adjacent side wall.

When the outlet channel or passage is blocked, an increased pressure builds up through this channel in the flow direction from the leading edge of the separator and in the area where the power flow touches the side wall. Furthermore, since the channel outlet is blocked, additional fluid flowing into the channel must reverse its flow direction in the channel and flow out through the inlet vent and around the separator to the opposite outlet channel. As a result, two areas are formed in the fluid flow where the flow movement in one occurs in counter-current to the flow in the other area, and considerable turbulence is provided. This turbulence occurs near the contact area of the flow with the wall. This turbulence destroys the seal between the power flow and the side wall to such an extent that the local high pressure at this point forces further fluid into the previously closed boundary layer area. As a result, the pressure difference across the flow is reversed, and this is now deflected to the unblocked outlet channel. This effect can be used in addition to or instead of the control effects provided by the control fluid flows. Such redirection or switching can be carried out intentionally by blocking the outlet passage towards which the flow is directed, to cause the fluid flow to be deflected to the other outlet channel.

When the separator is placed 12 nozzles

outlet widths or more from the power nozzle outlet, a contact of the flow with the side wall will occur in the direction upstream (upstream) from the leading edge of the separator. When the outlet passage through which the current flows is blocked, the resulting increase in turbulence and back pressure therefore occurs in the downstream direction (downstream) from the point of contact of the power flow. As a result, turbulence and back pressure do not influence the contact area to the same extent as when the separator is closer to the power nozzle outlet. However, the back pressure can cause a reverse flow along the boundary layer to the point of contact between the power flow and the side wall. At the contact area between the power flow and the wall, the flow is deflected by the wall, and consequently a sudden deceleration of fluid occurs in the part of the flow that actually touches the wall. This deceleration results in a large increase in the fluid's static pressure at the point of contact, accompanied by a changed velocity distribution through the power flow. The increased static pressure and the viscosity effects that occur due to the changed further velocity advantage<g>. strengthens the force flow's contact with the side wall by counteracting the tendency for fluid to flow backward into the enclosed <g>cleaning layer area. so that the direction of the effective pressure gradient across the flow is not reversed, and the flow remains locked to the same side wall even if no control signal is applied. Then lean the outlet passage towards which the flow is directed now due to the <g>cleaning layer locking device. remains blocked, fluid in the power stream that has entered this passage is forced to. i give one to leave this salary passage. flow around the separator and pass into the opposite outlet passage. as dvnamic trvkk is maintained in the riet blocked salary. However, when the blockage is removed by this beli<gg>unit of the separator. even without any persistent control signal. the power flow will flow back to its original outlet outlet, and will begin to flow around the separator to the opposite outlet. The memory properties of this type of system can be promoted by arranging for a sudden change in direction of the side wall or by bending the side wall, so that it seeks to move away from the current, as shown now fiff. 6 and 6A.

The different limits for the beli<gg>unit of a separating organ<g>an in a certain mode of operation are even exact in what is mentioned above. There is a transition area at each boundary where the unit can perform both modes, and is therefore sensitive to other parameters in the system, such as the type of fluid, pressure in the power flow, exact angles of the side walls, lateral displacement, etc. It must also be expressly mentioned that the above-mentioned limits relate to a specific design of the system and that they can therefore vary with changes to other parameters in the system.

In both latching and memory systems, a control signal can change the direction of a fluid or power flow with greater effect and thereby provide a fluid amplifier.

In order to explain how the system 10b works, it must be assumed that a power fluid flow from the power nozzle 15 has been locked to the side wall 19a as a result of a previous control fluid flow from the control nozzle 16, and that there is now no flow from either the nozzle 16 or the nozzle 32 The reason why the power flow is locked to the side wall 19a is that the boundary layer effect which occurs along the side wall 19a produces a lower local pressure than that which exists on the opposite side of the power flow. This effect is reinforced by the lateral displacement S, and the shape of the side wall 19a (fig. 2). When the power fluid flow flows into the opening 18a, it passes a discontinuity in the form of a sharp edge 51a. A small portion of power flow passing edge 51a diverges outward from one side of the power flow after passing edge 51a and forms a vortex, as shown by arrows V at a curved surface formed by wall 18d (Fig. 6).

A vortex indicated by arrows V is also formed between the wall of the separator 120 and the adjacent side of the power flow. If the outlet end 18b of the passage 18 is blocked, the current cannot flow freely through the opening 18a. If the blocking of the passage 18 is sufficiently effective, the power flow will reverse and flow back around the separator 120 and into the second opening 17a, as shown in fig. 6A. There must be sufficient space between the separator 120 and the side walls to be able to accommodate a vortex V<2> in this case, the inflowing power flow and the returning flow. The sharp edge 51a and the vortex V limit the pressure which from the channel 18 affects the boundary layer at the wall 19a. The vortex V2 that occurs between the power flow and the wall 19 forces the flow towards the side wall 19a. The power flow therefore remains locked to the wall 19a. The pressure in the outlet passage 18 is thus kept much higher than the pressure in the passage 17 due to the kinetic energy, i.e. the dynamic pressure of the power flow, even if the flow flows over around the separator 120. If the (not shown) blocking or clogging of the passage 18 is removed, the entire flow will change its path back to the passage 18 (Fig. 6), because a part of the power flow remains stuck to the side wall 19a, and is stuck to the side wall 19 in the absence of a control fluid flow from the control nozzle 32.

As will be understood from what has been described above, the vortices V and V2 also promote the memory properties. Each of these vortices has a velocity component transverse to the direction of flow of the force stream. Due to the impulse exchange between fluid in the vortices and fluid in the power flow, the power flow is deflected towards a boundary or side wall, and the locking is therefore increased.

The vortex V which is produced due to the formation of a bend or edge 51a on the side wall 19a also enhances the memory properties. The flow direction of fluid in the vortex V is such that the counter-flowing fluid in the area to the left of the power flow in the passage 18 flows into the vortex area and assumes the desired flow pattern, i.e. flows in a counter-clockwise direction. Fluid in the vortex near the power flow flows in the same direction as this, and this fluid is accelerated in the direction of the power flow due to impulse exchange. The vortex V thus prevents pressure feedback and a return flow along the side wall 19a into the closed boundary layer area.

The above relates to a fluid or power flow that is deflected to the opening 18a by means of a control fluid flow from the control nozzle 16 and by a plugging or blocking of the outflow from outlet passage 18 by any means. , but the operation is similar when the flow is deflected to the opening 17a by means of the control flow from the control nozzle 32 and by a partial or complete blocking of the outflow from the passage 17.

Fig. 7 schematically illustrates how the system 10b can be used in connection with a fluid-driven element 200 in the form of a conventional pneumatic hammer. Compressed air is introduced into the system 10b through a line 201. The line 202 is connected to the line 201 and is connected to a valve 204. The valve 203 regulates the air flow through the line 201.

The hammer comprises a cylinder 205 with a piston 206 which is axially movable in the cylinder, and a piston rod 228. The coil spring 207 is placed between the cylinder head 208 and the piston 206, and forces the piston 206 to contact the opposite cylinder head 209. The wire 247 stands in connection with the valve 204 and with the control nozzle 232. The line 226 connects the control nozzle 216 with an opening 211 in the cylinder wall, while the line 227 connects a passage 217 with the cylinder through an opening 213. The opening 211 is located at a slightly greater distance from the cylinder head 208 than the length of the piston 206, so that it is not covered when the piston 206 hits the cylinder head 208.

The piston rod 228 is provided with an annular groove 219 which cooperates with the valve 204 and with the open ends of lines 202 and 247, so that the valve 204 allows a flow from the line 202 to the line 247 only when the piston 206 is at the end of its stroke, i.e. when the piston 206 hits the cylinder head 209.1 other positions of the piston 206, the piston rod 228 will block the flow between the line 202 and the line 247. When the piston 206 hits the cylinder head 209, air will flow from the line 202 to the control nozzle 232 because the groove 219 will bring the line 202 in connection with the line 247. The control nozzle 232 will cause the power flow coming from the power nozzle 215 to penetrate into the passage 217. This causes the line 227 to deliver compressed air to the cylinder 205 between the cylinder head 209 and the piston 206. This air will drive the piston 206 towards the spring 207 until the piston 206 comes close to the cylinder head 208.

Although the pressure in the cylinder 205 increases between the piston 206 and the cylinder head 209 and thus in the passage 217, the power flow from the power nozzle 215 "remembers" that it was last directed to the passage 217 and it therefore tries to deliver air to this passage. And this applies even if the bar 228 blocks the air flow to the line 247.

As the piston 206 approaches the cylinder head 208, the opening 211 will be exposed to the high air pressure in the cylinder 205. A fluid flow or pulse will be received by the conduit 226, which will cause the control nozzle 216 to deliver a current and deflect power flow from the passage 217 to the passage 218. The passage 218 releases air into the atmosphere, and this air is therefore removed from the system 10c. As air is no longer supplied to the cylinder 205, the spring 207 can drive the piston 206 towards the cylinder head 209, until the groove 219 is just opposite the open ends of the lines 202 and 247. The described cycle will repeat itself until the valve 203 is closed. ket.

Although the multistable fluid memory system 10b is shown used as a control system for a pneumatic hammer in FIG. 7, it is clear that the system can also be used for other different applications where the system's properties and effects are necessary or desired.

Although the system 10b is shown with two opposite control nozzles, a single control nozzle can also be used. The memory properties of the system are not changed when increasing or decreasing the number of control nozzles.

An embodiment of the system can be constructed so that when an air jet begins to flow, in the absence of control signals, it will flow into one particular passage. This phenomenon can be exploited to force the power flow to flow back to this outlet passage after the power flow has been diverted during operation to another outlet passage or when its position has not been determined. This mode of operation is known as "resetting". There are several features or parameters in such systems which individually or together can contribute to the fact that the power flow will be reset when it ceases and starts again. The separating member can be arranged symmetrically in relation to the center line of the power nozzle. The power nozzle neck can be inclined or can lie so that the power flow is directed towards or located closer to one side wall than the other. The edge of the power nozzle outlet or neck can be rounded in the direction in which you want to deflect the power flow. The divergence angles of the sidewalls can be different to provide an asymmetry.

A unit or system of this embodiment having reset features is shown in fig. 8. In this unit, a power nozzle neck 251 and a separator 252 are arranged, the tip of which lies along the center line c-c of the power nozzle in the unit. A left side wall 253 has its lower end in line with the left side of the power nozzle neck 251 and forms a predetermined angle p with the center line c-c. A right side wall 254 has a lateral displacement of approx. three power nozzle neck widths and forms a greater angle y with the center line c-c than the side wall 253. The control nozzles 256 and 257 are led through the side walls 253 and 254.

In this unit, in the absence of a control signal, the power flow will more effectively reduce the pressure in the left side of the impact chamber than in the right side due to the fact that the power flow is closer

the side wall 253 at the beginning of the flow

place because there is no lateral displacement of this wall, and because the angle (3 is min-

dre than the angle y of the wall 254 during the entire movement of the flow towards the separation

the body 252. Thereby, the power flow, when it starts to flow, will be locked on

the left side wall 253 in the absence of a control signal. The control signals work on

the same way as in a symmetrical unit,

except that a larger signal must be used in control nozzle 256 than in control nozzle 257

to cause a path change for the power flow.

The one in fig. 8 device shown can be used

for comparison in a similar manner to that of fig. 2 shown device. In such a unit fly-

ters the control currents of both limit-

areas, and the power flow enters the outlet opening or passage which is located opposite the largest control flow-

nothing. In the case of symmetrical units up-

such a hysteresis effect occurs that the control-signal difference must exceed a minimum size in order to cause a trajectory

change. Using the reset effect-

then a bias or bias is introduced

lance in the comparison system, it can e.g. causes a deflection to take place

ning to the left side wall 253 as soon as a signal difference occurs. instead of the signal difference having to exceed a certain value for this deflection to take place.

The side walls of the impact chamber

or area 14 does not have to be flat as shown in fig. 2, 3, 5, 6, 7 and 8, but may have a curved surface as shown in fig. 1

and 4, or a series of planar surfaces at different angles to the centerline of the power nozzle. Consider e.g. a flow that is locked onto an inclined side wall and that flows parallel to this side wall

wall downstream from the point of contact. The power flow's ability to follow a further change in direction of the side wall downstream from the point of contact, as in the one in fig. 3

shown embodiment, depends on the same type of parameters that determine the original deadlock. Each directive

change actually forms a further pre-

stronger, and can be supplied with its own control nozzles that determine whether power

but becomes stuck or released or whether it is to lie in an intermediate flow

pattern at this new direction of side road-

gen.

Although, for example, the described sys-

topics are selected for reasons of clarity,

because they are carried out in a plan, are provided

there are also applicable systems by rotating the systems in figures 1, 2 and 6 about any one of several axes, the fluid flow in the resulting systems acting in the same way as in the described systems.

Such a system is what emerges

by rotation of the ground plan for the unit or system in figures 1, 2 and 6 about the center line c-c, the control nozzles 16 and 32 being replaced by a plurality of control openings. Another possible axis of rotation lies parallel to and at a distance from the sen-

terline c-c.

Other axes about which they in fig. 1, 2 and

6 shown contours or ground plan can be

write surfaces of revolution, can lie angular

right on the center line c-c and be located outside the outlet passage one or behind the power nozzle. These embodiments are mentioned here because they enable a convenient construction

tion and location of the inlets and outlets,

and does not entail changes in the

written basic operation of the system

mean.

Claims (22)

1. Fluid-driven control system re- comprising a nozzle for directing, under pressure, a deflectable fluid flow through an impact area towards at least one outlet passage or channel, and a control device for optionally creating a pressure gradient across the flow in the impact area to deflect the fluid flow and thereby vary the amount of fluid that is received by each outlet passage, characterized in that the area of influence (14) is delimited by at least one side wall (19) which is positioned so that mutual influence between the fluid circulation and the side wall produces a pressure gradient across the fluid flow and causing it to seek to approach the side wall. 2. Fluid-driven control system according to claim 1, characterized in that the control device provides a complete discontinuity in the boundary of the affected area between the aforementioned nozzle (15) and the side wall (19). 3. Fluid-driven control system according to claim 1-2, characterized in that the side wall (19) is a surface of revolution about an axis parallel to or coinciding with the center line of the nozzle. 4. Fluid-driven control system according to claims 1-2, characterized in that the area of influence (14) is further delimited by two approximately flat and parallel walls (11, 12) which limit the spread of the fluid flow in a direction normal to the plane in which it is deflected . 5. Fluid-driven control system according to claims 1 and 4, characterized in that there is arranged a separating member or structural element (120) positioned downstream with respect to the fluid flow in relation to the nozzle (15), which separating member (120) together with the side wall ( 19) forms a first outlet passage (17) or (217). 6. Fluid-driven control system according to claim 5, characterized in that the end or tip of the separator (120) is located at a distance of from 3 to about 11 times the width of the nozzle (15) neck (15a) from the nozzle to provide a control system in which the fluid flow can be deflected away from an outlet passage (17 or 18) by loading or blocking the outlet passage (17 or 18). 7. Fluid-driven control system according to claim 5, characterized in that the end of the separator (120) is placed at a distance of at least 12 times the width of the nozzle neck (15a) from the nozzle (15) in order to produce a system in which fluid the circulating current is not deflected from an outlet passage (17 or 18) when the outlet passage (17 or 18) is loaded. 8. Fluid-driven control system according to claim 5, characterized in that another side wall (19a) is arranged, which together with the separator (120) forms another outlet passage (18 or 218). 9. Fluid-driven control system according to claim 7, characterized in that at least one of the side walls has a discontinuity (51, 51a) with respect to the fluid circulation downstream of the end or the tip of the separator (120) in order to strengthen the locking effect on due to the boundary layer effect. 10. Fluid-driven control system according to claim 8, characterized in that the separator (120) is arranged symmetrically in relation to the mentioned side walls (19, 19a). 11. Fluid-driven control system according to claim 8, characterized in that the separator (120) is arranged asymmetrically in relation to the mentioned side walls (19, 19a). 12. Fluid-driven control system according to claim 8-11, characterized in that the side walls (19, 19a) are placed at mutually independent distances (X1{, X,) from the center line of the nozzle (15). 13. Fluid-driven control system according to claim 8-12, characterized in that the side walls (19, 19a) near the nozzle (15) form mutually independent angles with the nozzle's center line. 14. Fluid-driven control system according to claims 12 and 13, characterized in that the mentioned independent distances and angles for the side walls in relation to the center line of the nozzle are chosen so that the space or area between the center line and one of the side walls is smaller than the corresponding space or area between the center line and the other side wall, whereby the absence of a pressure difference provided by the control device causes the fluid circulation to be directed towards the outlet passage on the same side of the center line as the aforementioned one of the side walls. 15. Fluid-driven control system according to claim 8, characterized in that the control device comprises a means to at least partially block one of the outlet passages. 16. Fluid-driven control system according to claim 1, characterized in that the control device comprises a control nozzle (16) which is passed through one of the side walls (19) to introduce fluid into or discharge fluid from the area between the side wall (19) and the fluid flow. 17. Fluid-driven control system according to claims 1--2 and 4-16, used in connection with a fluid-driven element, characterized by a first outlet passage (173 or 217) which is connected to a cylinder (54 or 205) (the cylinder in element 100 or 200) on one side of a piston (156 or 206) mounted to reciprocate the cylinder (54 or 205), which piston is moved in a first direction when a fluid flow is supplied to the first outlet passage (173 or 217), a first control device for optionally creating a pressure gradient over the fluid flow to deflect this to the first outlet passage (173 or 217), as well as another control device for optionally creating a pressure gradient over the fluid flow to deflect it away from the first outlet passage, and a means (55 or 207) for driving the piston in another direction when the fluid flow is directed away from the first outlet passage. 18. Fluid-driven control system according to claim 8-13, characterized in that the control device comprises two control nozzles which are each guided through a side wall to introduce fluid to or remove fluid from the area between the respective side walls and the fluid flow, and means to vary control fluid flow-but through the control nozzles. 19. Fluid-driven control system in accordance with ge claim 18, adapted to be used for comparison of flow or fluid parameters, e.g. pressure, mass flow or power, for two fluids, characterized in that means are provided for the simultaneous supply of the two fluids through which control fluid flows through each of the aforementioned control nozzles, and measuring devices to determine which outlet passage receives the largest proportion of fluid flow but directed at himself. 20. Fluid-driven control system according to claim 8, characterized in that the control device comprises a control nozzle (16) which is passed through the side wall, a fluid receiving space (62) connected to the control nozzle, a pipe (63-64) connected to the fluid receiving space, where the end of the pipe (63-64) opposite said space is arranged to be at least partially blocked to cause fluid to be passed through the control nozzle into the area of influence to deflect fluid flow from one exit passage to the other. 21. Fluid-driven control system according to claim 20, characterized in that the said end of the pipe (63-64) is arranged to sense the presence or absence of an exemplary web-shaped body (52) which is moved by means of a propulsion device in a path close to the said end. 22. Fluid-driven control system according to claim 20, characterized in that the said end of the pipe (63-64) is positioned so that an operator can block it with part of the hand.