US3384164A - Fluid supply system with pump operated forced turbulence - Google Patents

Description

May 21, 196s H.-WALD 3,384J64 FLUID SUPPLY SYSTEM WITH PUMP OPRATED FORCED TURBULENCE Filed Jan. 26, 1965 CON STAHT TOTAL Ill/1111111111 United States Patent O 3,384,164 FLUTD SUPPLY SYSTEM WITH PUMP OPERATED FORCED TURBULENCE Herman Wald, 97-11 Horace Harding Expressway, Queens, N.Y. 11368 Continuation-impart of application Ser. No. 33,237,

June 1, 1960. This application Jan. 26, 1965, Ser.

5 Claims. (Cl. 165-109) This invention relates generally to further improvements in heat `transfer by foro-ed turbulence for pump appiications. This invention is a continuation-in-part application of my co-pending application Ser. No. 33,237 led J une l, 1960, now abandoned.

The extension of the principles of this invention is concerned especially, but not exclusively, with liquid operated pumps of any type or gas operated pumps.

The basic characteristic feature of the invention is of providing two uid displacing channels of equal area to discharge the fluid through a periodically variable fluid displacing device to produce an oscillatory shifting of the fluid distribution resulting in a constant total discharge in spite of the oscillatory or pulsating delivery through said respective individual displacing channels. The pulsating delivery serves the purpose to substantially destroy the film-layer adhesive between the contacting surface or mediums.

The importance of said constancy of the instantaneous total discharge through both channels lies in the fact that it makes possible an eicient, vibrationless operation of the pump system.

All the pulsating type systems of the present art fail to secure such an instantaneous constant discharge and are rather concerned with the provision of two extreme positions of the pulsating or revolving means so that when one is closed the other shall Open and during the intermediate positions, however, the total discharge is largely fluctuating, vibrating, or producing a modulating total ow causing a vibrating and uneflici-ent operation.

This invention, therefore, has special provision for a dual discharge channel system allowing to subdivide the discharging total fluid into two phase displaced ows and with such a functional variability that a constant total discharge is secured under any intermediate position of the fluid displacing means.

The mentioned revolving means in this application may comprise oscillating fluid-displacing elements having means to vary the cycling rate or period of oscillation as well as the pulsation-ratio or magnitude of fluid-pulsations requiring an operation of predetermined phase-relationship between both fluids flowing into the respective channels with simultaneous operation.

The word fluid herein referred to as being pressurefluid means a liquid or gas of higher pressures.

It is, therefore, the main object of the present inn vention to apply the forced-turbulence principle to pumps and is mainly referred to the various ldualdischarge methods having a 180 degrees phase-displacement between the fluid flows in the respective channels being accomplished by an oscillating duid-displacing means of any preferred reci-procable vane or piston arrangement for obtaining a continuous constant total discharge output in view of securing a vibration-less and eicient operation of the pump.

This object is mainly accomplished by providing a fluid receiving space communicating with the discharge region of the pump containing two separate chambers leading to the respective discharge ports. A movable body provided with two vanes of predetermined space relationship for oscillating movement such that the fluid-displacing 3,384,164 Patented May 21, 1968 ICC vanes are slidably supported and move with reciprocating movement within or along the ports of the chambers cooperating with said moving vanes carried thereby. These sliding vanes operate in reciprocation for alternately affecting the instantaneous quantity of fluid delivered into the dual channel system. It performs the function of diS- placing the uid in an oscillatory manner into the dual discharge channels since both vanes upon which the uid pressure acts are subjected to reciprocating movement within and conform to the contour of the two separate channels.

At one extreme position when the said receiving port of one chamber is in' full communication with the discharge region of the pump, the corresponding vane aS- sumes a full open position, whereas the other vane assumes a fully closed position with respect to the other port of the other chamber. As the fluid-displacing vane system continues Ito move in the slot spaces, the vanes are successively moved out of communication with the said one port of the respective chamber and are successively moved into communication with the second port of the chamber until the full opening position with the second chamber is established, thereby t-o become fully filled with the whole fluid discharge by the pump into the common receiving chamber. As a result, it will produce an oscillatory shifting of the ow distribution by displacing the total ow alternately into the respective discharge channels since the -two vanes are disposed side by side in fixed space-relationship and are constrained to move equally and oppositely by the conventional synchronizing mechanism of the piston type or alike arrangements.

The above described oscillating-uid-displacing means may be adopted to any conventional centrifugal or turbine type pump or compressor discharging the fluid through said displacing means into two separate conduits of equal cross sectional area producing the required oscillatory shifting into `the respective discharge conduits.

A still further object of the invention is to produce the necessary reciprocating movement effecting the desired fluid-displacement means by a magnetic vibrating-plunger actuating same with additional provisions to vary the pulsation ratio and cycling rate.

It is another specific object of the invention t-o provide a dual-discharge pump assembly providing two independent fluid deliveries of the pulsating character in such a manner as to maintain the total constant discharge through both outlets as required for an efficient operation of the pump system. Such a dual discharge pump assembly is especially adaptable for using its method of operation in feeding and cooling the combustion chamber of a rocket power plant as it will be fully described in connection with this particular application.

According to the above objects of the invention, two oscillating fluid-displacement devices cooperate with the two separate discharge channels. However, a plurality of conduits may be employed or arranged in parallel combination to form two independent group of conduits constituting two separate discharge passages of equal total area of each group, thereby to provide the desired oscillatory shifting of the ow distribution into the respective group of conduits. Both groups may constitute a heat transfer surface or coil for improving the inside coeicient of heat transfer by the forced turbulent action of the pulsating uid flowing inside pipes. This may be extended to serve for improving heat transfer to fluid flowing Outside pipes by using a suitable arrangement of the coil.

Thus it is an additional object to provide a heat exchanger apparatus to promote the overall heat transfer between two iluids being separated by a transfer surface.

This invention possesses many other advantages and has several other objects which may be made more easily apparent from a consideration of some of the embodiments of the invention. For this purpose there is shown some representative forms in the drawings accompanying and forming part of the present invention. These forms will be now described in detail, illustrating the general principles of the invention; but it is to be understood that this detailed description is not to be taken in a limiting sense.

To the accomplishment of the foregoing and related ends, said invention then comprises the features hereinafter fully described and particularly pointed out in the claims, the devices, combinations and arrangements of parts hereinafter set forth to form various complete uid supply systems and also include the various combinations and subcombinations of elements and their interrelation.

For fuller understanding reference will be made to the drawings, in which:

FIGURE 1 is a diagrammatic view of the principal embodiment of the invention applied to pumps using a fluid-displacing device to provide the oscillatory shifting of the flow distribution into the respective dual-channel system.

FIGURES 1A, 1B, 1C represent the different phasepositions of the fluid-displacing device.

FIGURE 2 illustrates the plot of the time-displacement diagram of the fluid displacement device.

FIGURE 3 represents a diagrammatic view of an electro-magnetic plunger type driving means to actuate the fluid-displacing device.

FIGURE 4 represents a diagrammatic view of a preferred application of the pulsating-dual-discharge pump arrangement to effectively pump liquid fuel combustion agents into the rocket-combustion chamber to provide more eflicient cooling of the walls and also to promote combustion efficiency.

FIGURE 5 is a diagrammatic representation of a general configuration of the principles involved herein as applied to a pair or group of parallel conductive means.

FIGURE 6 is a general diagram of a dual-discharge system of the invention where one of the pulsating discharge flows is recirculated into the main inlet or shortcircuited.

FIGURE 7 shows the operating phase-characteristics of two fluids operating with forced turbulence on either Side of the transfer surface to improve the Overall heat transfer.

FIGURE 8 shows another embodiment of the invention as applied to steam supply systems with forced turbulence.

Referring more particularly to FIGURE l, there is shown a diagrammatic view of an oscillating fluiddisplacing device generally indicated at 1 comprising a receiving chamber 2 being supplied by the pressure fluid 3 of any pump system 4 through the conduit 5, a horizontally slidable piston-vane assembly denoted by reference character 6 is rigidly connected with piston rod 11. The opposite sides of the vane-assembly 6 are provided with slotted guides adapted to engage slidably the inner edges of the slots 9, 10 slidably supporting the fluid-displacement varies 7, 8, respectively. The vane assembly 6 is constrained to move equally and oppositely with respect to the discharging ports 12, 13, by a conventional crank or synchronizing mechanism denoted by reference numeral 14. The vanes 7, 8 are rigidly secured in a predetermined spaced relationship with respect to each other to conform to the location of the discharge ports 12, 13 and constantly engage the wall of the receiving chamber 2 during their reciprocation by the piston rod 11. In this manner the receiving chamber is constantly in communication with the discharge ports in a cyclic operation, thereby an oscillatory shifting of the fluid-flow distribution takes place into the discharge conduits 15, 16, respectively, being due to the alternate closing and opend ing of the respective discharge ports to be effected by the reciprocation of the vane assembly 6.

Since the constructive feature of the crank-piston mechanism is rather conventional, therefore need not be dwelt upon in more further detail. So much is to be noted that the piston is reciprocated by the conventional crank arrangement to be driven by any type of driving means or motor, and the extent of eccentricity determines the length of the stroke as required for the fully actuated fluid-displacement into the respective discharge conduits. In this manner the piston-vane assembly is rapidly reciprocated and provides an alternate pulsation in the fluid flowing into the respective discharge outlets.

In order to analyze the characteristic of the oscillating flow-displacement, we determine the motion or displacement of the piston-vane assembly vs. time as produced by the continuously rotatable crankshaft. Such a motion may be represented by a harmonic curve as illustrated on the time-displacement diagram shown on FIGURE 2 and defined by the expression, x=r cos wt as being a cosinusoidal variation with the time. It is a projection on the x axis taken along the axis of the stroke and 0 is the midway between the two extreme positions of the pistonvane assembly 6. Thus during rotation of the crank a pin may slide in a horizontal slot (not shown) so that the vertical displacement x of the piston is equal to the vertical projection of the crank. Thus it will readily be seen that the time required for the piston to make one complete oscillation along its paths is the same as that required for the uniformly rotated crank to make one cornplete revolution. The points A, B, C on the curve 17 denote the corresponding positions of the piston-vane displacements. It is seen that the curve gradually changes from minimum to maximum or inverse, thereby the sliding vane assembly engaged with the crank will be gradually accelerated or decelerated without shock in changing their direction of oscillation and therefore produces the desired velocity-fluctuations in the fluid flowing therethrough.

FIGURES 1A, 1B, 1C represent the different vanedisplacement positions corresponding to the points A, B, C on the curve 17. FIGURE 1A indicates the position A on the curve when the vane-assembly allows the fluid a full communication or opening into the discharge port 12 cooperating with vane 7 and fully closed position with discharge port 13. FIGURE 1C represents an inverse condition when vane 8 cooperates with discharge port 13 in a similar manner. FIGURE 1B illustrates the condition at the midpoint G on the curve when both discharge ports are half-way open.

It is clear that due to the predetermined fixed spacing of the varies 7, 8 with respect to the cooperating discharge ports 12, 13, they are constrained to move simultaneously causing an inverse variation/of the free area of both discharge ports during each cycle of the vane-oscillation. A ccordingly the flow rate of fluid discharged from the discharge ports varies from zero to maximum and the other varies inversely. As a result, the sum of the fluid quantities discharging from both ports is constant at any time-moment of the fluid-displacement obtained by the simultaneous sliding of both vanes. This is true despite of the cosinusoidal variation of the vane-displacement vs. time as shown by the curve 17 and dashed line curve 18 Accordingly, the variation of the free area through port 12 is at any time proportional to cos wt, whereas through port 13 is proportional to (l-cos wt), thereby we obtain a constant total free passage area through both points at instantaneous time-moment as desired. It will thus readily be seen that by properly selecting the design of the crank driving means similar to a cam prole or curvature, any desired time-velocity characteristic could be produced. In a preferred embodiment, not shown here, the profile may assume a sine-squared form in which case the profile of an other cooperating crank driving means of the same curvature will produce a cos-squared curve when a 90 degrees phase-displacement exists between both driving means. Now if we assume that both sliding varies are driven by the corresponding driving means, the total instantaneous discharge llow through both ports becomes constant as given by the form:

where C is a factor depending on the rod connections, wt angular velocity.

The pulsation ratio may preferably be controlled by varying the magnitude of the slots on the sliding vanes 7, 8, whereby the oscillatory flow rate fluctuations of the uid can be made from any minimum to maximum. Any outside control lever means 19 can be adopted to carry out this adjustment.

Any driving means to be applied to the crankshaft must have provision to control the cycling-rate as required according to the principles of the invention to assume any desired functional relationship to fluid velocity entering the fluid-displacing vanes.

By way of example, the simplest type of driving means would be a separate motor drive of variable speed type or it may be driven by the pump motor itself using some interconnecting means of variable speed ratio as required in accordance with the invention.

By way of example, a preferred application is shown on FIGURE 1 when the fluid-displacing device 1 controls the oscillatory shifting of the flow distribution of forced turbulent character flowing into the respective discharge conduits 15, 16 leading into two independent portions of a heat transfer apparatus 19 comprising two coil arrangements 20, 21. Both flows after leaving the discharge passages of the transfer surface may be joined together and recirculated through conduit 22 into pumpinlet 23 to be treated again. Thus the sum of the lluid-ows discharged from both passages is constant at any instantaneous time-moment and a uniform, pulsation-free flow is returned to the pump inlet. This method secures a quiet and vibration-free, eicient operation of the pump despite of the fluctuating supply into the individual respective conduits. This method of application being only indicative of but a few of the various ways in which the principle of dual-discharge pulsating supply of the invention may be employed.

FIGURE 3 represents a diagrammatic view of an electromagnetic plunger type driving means to actuate the fluid-displacing device. It mainly consists of a non-magnetic cyclindrical structure generally indicated at 37 wherein a hollow magnetic plunger is slidably mounted and carrying rigidly secured therewith the vane-assembly 6 actuated by the rod extension of the plunger. Basically it comprises, in combination, an electrically actuated vibrating plunger member 38 having disposed on and surrounded by a solenoid-electromagnet to be actuated by A.C. voltage or ilux so that the vbratory movement of the plunger member is effected by the rapid variation in the direction of the magnetic flux of any given frequency.

Accordingly the herein described preferred embodiment comprises a U-shaped electromagnet 39 embedded in insulating material and equipped with a core 40 having an aperture 41 to allow the sliding back and forth of the plunger. In order to vary the rate of oscillation or reciprocation, the A.C. source may consist of a rectilied D.C. source feeding an electric vibratory-means to produce an alternating flux of any given self-oscillating frequency or it may consist of a timed condenser-discharge circuit of any conventional type not shown here, and no further details are given. In the latter case the frequency of thealternating ux may be controlled by varying either the resistor or the condenser determining the desired frequency.

It is to be noted that this modified design using an electromagnetic means to actuate the reciprocating plunger of FIG. 1, is rather preferred in `high pressure applications using discharge outlets of relatively small cross sectional area necessitating a correspondingly small pulsatory displacement of the pulsating plunger to perform the required oscillatory shifting of the fluid ow into the respective branch conduits or outlets 15, 16 by alternately closing said respective discharge ports 11, 12.

The general embodiment of the pulsating dual-discharge supply may preferably be employed Very eiectively in pumping liquid fuel combustion agents from a separate storage container into the rocket combustion chamber. FIGURE 4 represents a diagrammatic view of such a preferred application. Usually a rocket power plant includes a turbine driving the pumps with dual discharge provision generally indicated at 77, however, a sliding vane type is shown for the sake of illustration. With the usual design of the rocket chamber 78, the liquid combustion agents are pumped through spiral grooves 79, 79A formed along the walls S0, 80A, which in turn intercommunicates with the chamber by a plurality of nozzles 81, 81A symmetrically disposed on opposite sides for the purpose of cooling the wall of the combustion chamber. Similarly along the wall of the auxiliary chamber 76 there are spiral grooves 82, 82A disposed for the same reasons. Since the rocket chamber itself forms no part of the present invention, no further description is deemed necessary.

In this connection, the lprinciples of the invention may be applied to good advantage by pumping the liquid cornbustion agents iiowing through said spiral grooves with 4a special pulsating and Iforced turbulent character having two independent discharge outlets in delivering liquid agents through conduits 83, 83A to both independent symmetrical sides of the rocket-chamber and similarly branched-olf conduits 84, 84A to the auxiliary chamber through the respective nozzles disposed on each side of said chambers. Accordingly, in this application the chamber wall serving as transfer surface is subdivided into two symmetrical sections and thus two independent groove arrangements are disposed in accordance with the invention to employ heat transfer surfaces in two symmetrical parts being subjected to the forced turbulent flow of opposite p'hase with respect to each other.

Therefore each conduit delivers -oscillatory forced turbulent flow of the combustion agents through nozzles on each side, providing a considerable increase of the cooling-effect on the walls as being high-ly desired to effect a substantial destruction of the film-layer at the inner `surfaces of the grooves serving as transfer surface. Also the branched-off turbulent flow may serve to cool the wall of the `auxiliary chamber by sending the liquid agents through the grooves formed along its wall.

rPhe supply of the liquid combustion agents into the rocket chamber with pulsating character is especially suitable since it may further contribute to increase the combustion efficiency caused by the special forced turbulent ycharacteristic injected through the nozzles. In addition to the foregoing advantages, the combustion efficiency is also greatly enhanced by applying a tuned-ignition to the highly turbulent mixture in such a manner that the spark shall always occur at the instantaneous time-moment of maximum amplitude of the pulsating mixture. This may easily be accomplished and controlled by a synchronizing means not shown here Iand driven by the same shaft rotating the pumps. The continuous applicati-on of the spark to the pulsating turbulent mixture of the combustion agents will produce repeated-detonations for a better overall combustion e'liciency.

IFIGURE 5 is a diagrammatic represen-tation of an alternate and general configuration of the principles of the invention as applied to a group of parallel conductive means in such a manner that each group is considered as one independent branch conduit of the dual-discharge system. Referring to this figure, there is shown a heat transfer surface denoted by reference numeral composed of two groups of parallel conductive means 141, 142. The dual discharge conduits 143, 144 are connected to the respective inlet of the respective groups, thereby to deliver through each group of conductive means a pulsating fiow of forced turbulent character operating in phase opposition with respect to each other of said groups. Since all other considerations are lotherwise identical to that of the double conduit system, no further description of this embodiment is deemed necessary.

FIGURE 6 is la diagrammatic representation of an alternate configuration and embodiment to be generally applied to all embodiments of the present invention employing dual-discharge outlets of forced turbulent and pulsating character. This consists mainly of recirculating the iiuid fiow through one of the discharge conduits 145, 146 into the common intake 23, shown with dashedlines, in case of one single discharge conduit is `applied leading into the transfer surface. This recirculation is necessitated for maintaining the desired constant fiow through conduits at any instantaneous time-moment as required for efficient operation of the pump system.

The recirculation may be formed through a by-pass 147 inter-connecting said outlet to the inlet so as to serve as short-circuit to the common inlet 23 of the pump. A control valve means 148 is adopted to effect this cont-rol any time it is desired. Thus one part of the fluid which would normally 'be fiown into the other part of the transfer surface, is short circuited to the common suction inlet. Since the kinetic energy of the returning fiow is imparted on the intake fiow providing a corresponding reduction of the necessary pump-energy supply of the total incoming fiow.

H eut transfer' between two fluids of forced turbulence Generally the various apparatus proposed for causing the heat interchange between two iiuids, liquid or gas, usually require the expenditure of abnormal heating or cooling energy. The rate of heat transfer from one to another iiuid depends primarily on the magnitude of contact area, the difference in temperature of Iboth fluids and finally the heat transfer coefficient. The unsatisfactory operation of such heat exchangers is Idue to a large extent to the restriction of the `contact area between both fluids, which in turn limits the manner in which heat or cooling effects of both fiuids are associated with one another. In another aspect, the rate of heat transfer is greatly limited by the film layer adhesive to the inside and outside of the separating transfer surface. In other words, this invention contemplates the destruction of both film layers and to provide an efficient overall heat transfer despite of limited transfer surface or flow rate of any particular application.

It is generally known that the overall heat transfer between two -ffuids is greatly improved by the application of a counter-flow arrangement as being due to the tendency of increasing temperature difference along the outflow direction. With this thought in the mind this invention contemplates the provision for a counter-phase operation of the forced turbulent fiows at the inside and outside of the separating transfer surface. Accordingly, it is to be assumed that the overall heat transfer efficiency is still further enhanced by establishing a predetermined phaserelationship of both fluids operating in counterflow.

Generally the forced turbulence produces a periodical variation of the momentum transfer perpendicular to the fiow direction followed -by a radial diversion being due to the excess of kinetic energy released with a resulting shock effect to destroy the film-layer. In order to get a maximum instantaneous shock effect destroying the film-layer on either side of the transfer surface contacting both fluids in counterow, the mentioned momentum transfer shall take place simultaneously. To this end the maximum velocity in the flow of the fiuid 150 and the minimum velocity `of the fiow of the fiuid 151 shall take place simultaneously as shown on FIGURE 7. With this operation of opposed phase characteristic the instantaneous over-all heat transfer coefficient on both sides of the transfer surface 152 and over-all logarithmic means temperature differential will greatly increase, which, in turn, results in a proportionate increase of the overall heat transfer effect in accordance with the general expression for counterfiow given by:

where U1, U2 are the over-all coefficients at the respective ends and AtbAtZ are the over-all temperature differentials at the respective ends and lne is the natural logarithm. As above explained, this expression contains products of t at one end and the U at the other end, consequently the overall heat transfer Q is greatly enhanced by this counter-phase operation since it causes greater differentials on the above values resulting in a proportionate increase of the overall heat transfer effect.

This synchronization in the operation is accomplished by an interlocking means, not shown here, between the fluid-displacing of both fluid flow. This interlocking means may be set in such a manner as to obtain any desired phase-relationship. However, it is to be noted that the above opposed phase arrangement will give the best heat transfer results.

It is, of couse, to be understood that in practical applications one fluid may represent a liquid flowing inside pipe and a gas ow'ing outside for heat interchange, or it may represent liquids flowing in either sides of the transfer surface.

Application to steam supply with forced turbulence FIGURE 8 is a diagrammatic view showing an arrangement as applied to steam supply in Iaccordance with the invention. In order to develop forced turbulence with following velocity fluctuations or pulsations through any type of steam generator, it is imperative to produce the required oscillatory volume fluctuations at the discharge of the condensate pump as shown in the diagram.

In accordance with the invention, the oscillating fluid displacing device generally indicated at is connected to the discharge line 161 of the pump 162 leading to the dual-discharge conduits 163, 164 to be connected to oppositely located points 165, 166 of the steam-generator apparatus denoted by the reference character 167. Thereafter the pulsating steam flows into the heat-transfer surface 168 with its condensation returned to the pump inlet 169 through return conduit 170. The pulsations along the return line will appreciably be damped or some dampening provisions may be employed at the inlet of the pump to allow a uniform yback-how to enter into the pump.

In case of two steam generator apparatus operating in parallel, not shown here, each discharge conduit leads to the respective transfer surface 'and both return flows are joined together to form a constant total flow to allow a uniform fluid-fiow back into the inlet of the pump as required for an efficient operation.

It is to ybe understood that in this application, any of the dual-discharge pumps described in this invention may be employed to ygood advantage to serve as condensation pump with dual-pulsating discharge outlets, thereby the separate fluid-displacing device may be eliminated.

It is further to be noted that in this lapplication we assume a zero velocity of the condensate at the wall of the heat transfer surface and maximum velocity at the liquid-vapor interface. However, when the velocity of the uncondensed vapor is substantial compared with the velocity of the condensate at the vapor-condensate inter-face, because of the friction between vapor and condensate-film, the vapor velocity influences appreciably the haar h: 0.9LufAT where k is the thermal conductivity of condensate, p is the density, and A is the latent heat of condensation, uf is the Iabsolute viscosity of condensate.

Thus it may readily be seen that the heat transfer coefficient h is mainly proportional to the factors k, p and A, of the condensate and film-condensate, consequently the destruction of this film-condensate greatly promotes the heat transfer by the effect of turbulence caused by the shock-action of the forced velocity fluctuations in the layer of condensate in accordance with the principles of this invention as described in above mentioned copending applications.

The forced turbulence method may also be considered as a promoter since it frees the surface from condensate, whereby we obtain a much higher rate of condensation than with a wettable surface that is insulated with a continuous film-condensate.

As further advantages of this forced turbulence may be mentioned the general promotion of condensate-flow, the purging of the system from air and gases and thereby the over-all improvement of the heat-transfer efficiency of the whole system.

While in the foregoing there has been shown and described some of the preferred embodiments of this invention it will, of course, be understood that various details of construction, combinations and arrangements of parts may be resorted to without 'departing from the principles of the invention including its spirit and scope, it is, therefore, not the purpose to limit the patent granted thereon otherwise than necessitated by the scope of the appended claims.

What I claim las new and desire to secure by Letters Patent of the United States is:

1. A uid supply system with forced turbulence for improving heat transfer rates comprising, a fiuid supply source under pressure, a chamber having a uid receiving portion and a fluid discharging portion,

a heat transfer apparatus having a heat transfer surface divided into two equal areas,

said uid discharging portion divided into two equal areas communicating with respective areas of the divided areas of the heat transfer surface,

said fluid receiving portion communicating with said uid source,

means comprising in part slideable valves positioned in the divided areas of the discharging portion of the chamber,

said means causing one of the areas of the discharging portion to have a flow area proportional to a sinusoidally varying time function and the other area of the discharging portion to have a flow area proportional to the co-function (cosine) of the sinusoidally varying time function,

thereby to cause a total flow through said discharging portion of said chamber which remains constant and also to subject each of the divided areas of the heat transfer surface to an oscillating fluid flow to substantially reduce the thickness of any stagnant film layer at said surface.

2. The structure as defined in claim 1 wherein each of the divided areas of said heat transfer surface being Icomposed of a `group of parallel conductive means, each of said divided areas of said fluid discharging portion communicating with respective areas of said group of parallel conductive means.

3. The structure as defined in claim 1 wherein each of the areas of said discharging portion to have Ia flow area proportional to a sine squared time function and the other area of said discharging portion to have a flow area proportional to a cosine squared time function.

4. The structure as defined in claim 1 wherein said uid supply source comprising a steam generating apparatus, said heat transfer surface having condensation conductive means disposed therewith., said Iboth discharge ports being disposed in fluid communication with oppositely located points on said steam generating apparatus, thereby to produce a pulsating steam supply system to substantially destroy the said film layer at said heat transfer surface.

5. The structure as defined in claim 1 wherein the two said areas of said heat transfer surface constituting the respective portions of the combustion chamber wall of a rocket type power plant, each of said respective portions including a group of passageways being in heat exchange relation to said combustion chamber, thereby to deliver through each said group of passageways a pulsating fluid flow.

References Cited UNITED STATES PATENTS 280,346 7/1883 Canaday 137-625.11 1,835,557 12/1931 Burke 257-1.5 2,050,597 8/1936 Younger 34-191 2,351,163 6/1944 Thomas 257-15 2,514,797 7/ 1950 Robinson 257-73 2,585,626 2/1952 Chilton 60-35.6 2,960,314 11/1960 Bodine 257-73 FOREIGN PATENTS 562,089 11/ 1957 Belgium.

622,024 6/ 1961 Canada.

846,950 9/ 1960 Great Britain.

MEYER PERLIN, Primary Examiner.

ROBERT A. OLEARY, Examiner.

A. W. DAVIS, JR., N. R. WILSON, Assistant Examiners.

Claims (1)

1. A FLUID SUPPLY SYSTEM WITH FORCED TURBULENCE FOR IMPROVING HEAT TRANSFER RATES COMPRISING, A FLUID SUPPLY SOURCE UNDER PRESSURE, A CHAMBER HAVING A FLUID RECEIVING PORTION AND A FLUID DISCHARGING PORTION, A HEAT TRANSFER APPARATUS HAVING A HEAT TRANSFER SURFACE DIVIDED INTO TWO EQUAL AREAS, SAID FLUID DISCHARGING PORTION DIVIDED INTO TWO EQUAL AREAS COMMUNICATING WITH RESPECTIVE AREAS OF THE DIVIDED AREAS OF THE HEAT TRANSFER SURFACE, SAID FLUID RECEIVING PORTION COMMUNICATING WITH SAID FLUID SOURCE, MEANS COMPRISING IN PART SLIDEABLE VALVES POSITIONED IN THE DIVIDED AREAS OF THE DISCHARGING PORTION OF THE CHAMBER, SAID MEANS CAUSING ONE OF THE AREAS OF THE DISCHARGING PORTION TO HAVE A FLOW AREA PROPORTIONAL TO A SINUSOIDALLY VARYING TIME FUNCTION AND THE OTHER AREA OF THE DISCHARGING PORTION TO HAVE A FLOW AREA PROPORTIONAL TO THE CO-FUNCTION (COSINE) OF THE SINUSOIDALLY VARYING TIME FUCNTION, THEREBY TO CAUSE A TOTAL FLOW THROUGH SAID DISCHARGING PORTION OF SAID CHAMBER WHICH REMAINS CONSTANT AND ALSO TO SUBJECT EACH OF THE DIVIDED AREAS OF THE HEAT TRANSFER SURFACE TO AN OSCILLATING FLUID FLOW TO SUBSTANTIALLY REDUCE THE THICKNESS OF ANY STAGNANT FILM LAYER AT SAID SURFACE.

Images