NON-INTRUSIVE AGITATION OF A FLUID MEDIUM

Abstract: Impeller means (4 and 5) is provided in a container (2) for agitating fluid. The impeller means is movable to effect fluid flow. The impeller means includes an impeller (4) which is separate from a wall portion of the container to a point of which the impeller (4) is connected by supporting means (5). Movement of the impeller means relative to the wall portion is achieved by making the impeller means flexible. A vibrator (6) may be provided to cause movement of the impeller means. The characteristics of the components can be chosen so that when the vibrator is activated the impeller vibrates with a greater amplitude than the wall portion (3). This can be achieved by vibrating the wall portion at a frequency approximately equal to a resonant frequency of the impeller means.

Description: NON-INTRUSIVE AGITATION OF A FLUID MEDIUM Field of the Invention The invention relates to apparatus and a method for agitating fluids, for example to effect mixing of two or more fluids without the intrusion of agitating means through the wall of a container enclosing the fluid medium. Background Art Known apparatus for agitating a fluid medium comprises a container for the liquid medium; and means movable within the container to effect fluid flow. Movement of this means is effected by driving means which may form part of the apparatus. In this apparatus, the means extend between internal and external parts respectively disposed inside and outside the container. However, there are occasions where it is desirable and/or necessary to intimately mix two or more fluids in a sealed container without any moving parts entering the container enclosing the fluids. Thus, non-intrusive mixing such as this is required where the contents of a sealed container have to be mixed immediately before use. This might arise, for example, when materials that are stored in sealed containers for prolonged periods separate out into their constituent components. Another application would be the mixing of materials that are toxic, explosive or otherwise dangerous when in contact with air. The mixing apparatus would then have to operate in such a way as to avoid any sealing problems inherent in conventional mixing apparatus involving the use of impellers. Disclosure of the Invention It is the object of the present invention to provide a method and apparatus for this non-intrusive mixing as hereinbefore described. According to the invention, there is provided apparatus for agitating a fluid medium, for example: to effect mixing of two or more fluids, O PI comprising a container for the fluid medium and impeller means located within the container and movable to effect fluid flow; the container has a wall portion and the impeller means comprises an impeller separate from the wall portion and supporting means connect- ing the impeller to a point on the wall portion, the impeller means being flexible such that a point on the impeller is movable relative to said point on the wall portion. The movement of the impeller means from its flexibility is a useful arrangement to effect fluid flow. Flexing of the impeller means can be caused for example by shaking the container as a whole or by connecting a vibrator to said wall portion, the characteristics of the vibrator, the wall portion and the impeller means being chosen so that when the vibrator is activated, the impeller vibrates with a greater amplitude than the wall portion. This can be achieved by arranging for the frequency of vibration of the wall portion to be approximately equal to a resonant frequency of the impeller means, not necessarily the lowest resonant frequency of the impeller means. In another aspect, the invention provides a method of agitating a fluid medium in a container which has a wall portion on which flexible impeller means is mounted within the container, the impeller means comprising an impeller separate from the wall portion and supporting means connecting the impeller to a point on the wall portion, the method comprising causing the impeller means to flex such that a point on the impeller is movable relative to said point on the wall portion. Examples of the invention will now be described with reference to the accompanying drawings in which: Figure 1 is a central section through agitation apparatus, Figure 2 is a plan of the apparatus of Figure 1, Figure 3 is a schematic diagram of agitation apparatus to indi¬ cate the symbols used in the theory of operation, Figures 4 and 5 are central sections of modified agitation apparatuses, Figure 6 is a plan of the apparatus of Figure 5, and Figures 7 > 8 and 9 represent frequency responses of the base wall portion and the impeller plate to the applied vibration. A fluid medium 1 to be agitated is held in a container 2 having a bottom wall portion 3« An impeller plate 4 is separate from the wall portion 3 and supported from the centre thereof by a supporting spring 5 at its centre. The plate 4 is provided with a plurality of holes 7 arranged in a circle on the plate 4 as can best be seen from figure 2. Each hole is bevelled so as to provide greater resistance to fluid flow therethrough in the down¬ ward direction than in the upward direction. The rim 10 of the plate 4 is bevelled in the opposite direction to the holes 7 > so that the annular regionn between the rim 10 and the side wall 12 of the container presents a greater resistance to upward fluid flow than downward fluid flow. Thus, when the plate 4 is oscill¬ ated vertically, fluid will tend to flow upwardly through the holes 7 and downwardly through the region 11, thus circulating within the container 2 to effect mixing. Mien the container 2 is small, it may be possible to effect this mixing by shaking the container, causing flexing of the plate 4 and spring 5 combination to cause circulation of the fluids, but when the container is of large size, such as 200 litres capacity, then a vibrator 6 applied to the bottom wall portion 3 is a more convenient method of causing flexing of the impeller assembly. Vibrations are transmitted through the wall portion 3 to cause the impeller plate 4 to vibrate relative to the point of attachment of the spring 5 to the wall portion 3« The motion of the plate 4 will depend on the effective masses and stiffnesses of the bottom wall portion 2 > > the spring 5 and the plate 4j together with the damping characteristics of the fluid or fluids in the container and the frequency of vibration applied by the vibrator 6. The frequency of vibration is preferably chosen to cause maximum amplitude of vibration of the impeller plate 4 ( n order to achieve maximum agitation of the fluid) in relation to a given amplitude of vibration of the wall portion 3 (which is kept as small as possible in order to avoid failure of the wall portion 3). This frequency can be selected by experiment but it is believed to occur when the frequency of vibration of the wall portion 3 is approximately equal to a resonant frequency of the combination of the impeller 4 and supporting spring 5» these resonant frequencies depending on the effective sti fness of the supporting spring 5 and the effective mass of the impeller plate * The current theoretical understanding of this relationship is presented below. The wall portion 3 will have associated with it an effective mass, M, and an effective stiffness, K, which together govern its natural frequency , J\, since il =(K/M)? Similarly, the impeller means comprising the impeller 4 and the supporting means 5 has associated with it an effective mass, m, and an effective stiffness, k, which together govern its natural frequency, w = i n (k/m) 2 . An alternating force of frequency w acts on the wall portion 3 - let the amplitude of this force be denoted as F. Since the impeller 4 vibrates relative to the wall portion 3 through the fluid medium 2 it will experience a damping force - let this be represented by a viscous damping constant, c. Then as illustrated in figure 3, the combined system comprising the wall portion 3 and the impeller means comprising the impeller 4 and the supporting means 5 may be represented as a spring of stiff¬ ness attached to a rigid foundation, a mass M attached to this spring and acted on by a force of amplitude F and frequency w, a s^-ing of stiffness k and a dashpot of damping constant c both attached to this mass and a second mass, m, attached to both the spring of stiffness k and the dashpot of damping constant c. Denotin the displacement of the mass M by x and that of the mass m by x 2 , the equations of motion of the two masses may then be written as -Mx χ - Kx. + I'^- j ) + c ( - ) + Fe iwfc - 0 "(D -m 2 - k(x 2 -x ) - c (i 2 - 1 ) = 0 -(2) The displacements x x_ will also be alternating with the same 1* ^ frequency, w, as the force F - let their amplitudes be denoted as X.- and x 2nJ respectively and their phase angles as B and B , respectively. Thus differentiating and differentiating again -1 =- w x l x 2 =_w X 2 Substituting these expressions for x x„ rf x and x into equations (1) and (2), -Mw x + Kx + k(x_-x.) + iwc(x_-x.) = Fe -(la) 2 - mw + k(x -x ) + iwc (x -x ) = 0 -(2b) Collecting terms in X j and x„ [_- Mw 2 + K + k + iwcj Xj -[k + iwc,J ^ - Fe XWt -(lc) -j + iwc x + -mw + k + iwcj x - 0 -(2c) Equation (2c) yields an expression for x_ in terms of x n and other variables which, when substituted into ( lc) gives as an expression for OMPI . ξ$N A τ\c This expression may be re-written as Equation (2c) may also be used to yield an expression for j in terms of x~ and other variables which, when substituted into (lc) leads to an expression for x„, as K-mw 2 ) -(4) Since high x„ is required for effective mixing and low x 1 for Q long lifetime of the wall portion, it is convenient to consider their ratio k+ iwc 1 . Remembering that w = (k/m) 2 and introducing the critical damp- 5 ing constant, c = _mw , this may be re-written as 2iwc 1 , w c n c X l , 2 1-w + 2 iwc w c n c 0 This expression implies an amplitude ratio x„ n /x given by -δ- The expression for the amplitude ratio shows that x /x becomes 20 10 large for w close to w , i.e. when the natural frequency of the impeller means comprising the impeller (4) and the supporting means (5) is close to the frequency of vibration of the wall portion (3). It is important to note that this ratio is independent of the effective mass, M, and stiffness, K, of the wall portion 3. Equations (3) and (4) show that the absolute values of x 1 and x_ respectively are dependent on M and K: their rεti.o, x./x,, however remains independent of these parameters Equation(5) shows that, because of the term 4 2 in fact reaches a peak for w slightly lower than w . however, since c/c is in general small, a reasonable estimate of the peak value of x„_/x ιn may be made by setting w = w in the equation, when it is found that for small c/c -(6a) Equation (6) shci-.'s that the peak value of „ n /x ιr . depends on the damping ratio c/c and since the damping ratio is generally small, a large amplitude ratio may be achieved at w close to w . This is the main result sought by the theoretical presentation. As an illustration of typical amplitude ratios that might be realised; consider damping ratios of c/c = 0.05 (representing quite high damping) and c/c = 0.0125. The former value in equation (6) gives x„ /x _ = 10.05, the latter a ratio of x 2 /x j = 40.01. The theory may then be taken a stage further when it is remem¬ bered that the power P delivered to the fluid by the plate is given by and that effective mixing requires P to be high. Since the damping constant c depends on the size and geometry of the impeller, it is open to choice in the design. Thus, a given power input may be achieved either by a relatively high c and low x_- or a low c and a high x«~' Equation (6a) shows that assuming x... is fixed by consideration of stresses in the cont¬ ainer wall, high c implies low x_ n and vice versa. In fact, when equations (6a) and (7) are combined, it is found that P = (k 2 /2c)x 2 0 suggesting that c should be contrived to be as low as possible. To summarise the results of the theoretical discussion, it has been shown that to maximise the ratio of the amplitude of vibratior of the impeller 4 to that of the wall portion 3 , the frequency of vibration of the wall portion 3 should be close to the natural f equency of the impeller means ' comprising the impeller 4 and the supporting means 5 (or more precisely, the frequency of vibration should be such as to produce a naximum ratio of o/ x ιo as g ven in equation (5))« Th_ actual value of this maximum ratio χ 2o x iθ can ^ e adjusted by varying the damping ratio. c/c c of the impeller 4* which will be a function of its size and geometry. The absolute values of X-^Q and x~ 0 may then be'set by varying the stiffness K and mass M of the wall portion according to equations (3) and (4) 3 respect¬ ively. Figure 4 shows an alternative plate 4 formed with a first type of aperture which presents a lower resistance to flow from one side of the plate to the other side of the plate than to flow from said other side of the plate to said one side of the plate and a second type of aperture which presents a lower resistance to flow from said other side of the plate to said one side of the plate than to flow from said one side of the plate. In this embodiment, the circumferential edge of the plate is (optionally) shaped such that half of the annular hole formed by said edge and the container wall presents a lower resistance to flow from one side of the plate to the other side of the plate than to flow from said other side of the plate to said one side of the plate. The other half of said hole presents a lower resistance to flow from said other side of the plate to said one side of the plate than to flow from said one side of the plate to said other side of the plate. In Figure 4 ? the circular plate 4 has a concentric ring of holes 7 and 8. The holes 7 on one side of a diameter have greater resistance to fluid flow downwardly through the plate 4 than to upward flow. The holes 8 on the other side of the diameter are oppositely oriented. The rim 12 of the plate 4 on the first side of the diameter is bevelled to present greater resistance to upward flow than to downward flow and the rim 11 on the opposite side is oppositely oriented. When the plate has vibrations applied from the vibrator 6 through the wall 3 and the spring support 5, fluid will tend to flow down through the half-annular gap 14 and up through the holes J, down through the holes 8 and up through the half-annular gap 13, ensuring good mixing of fluid. In the embodiment of Figures 5 and 6, the support comprises a substantially rigid stem but the stem 5ais connected to the plate 4 by three equi-spaced spring leaves 5 D to allow the plate to vibrate transversely to its plane. It would be possible ftr the plate 4 itself to flex, if this were found preferable to the flexing of the support stem 5 or the provision of the spring leaves 5b• A 600mm diameter πiijing vessel 2 containing a process fluid 1 has a dished base portion 3 and is provided with an electro- O PI IΛ LPO *y magnetic vibrator 6 which operates at a frequency of 100Hz. The dished base portion 3 has an effective stiffness of K = 2.05,10 ° Nm -1 and an effective mass including the vibrator 6, of M=40.0kg and so has a natural frequency of Fn = iZ n /2τr of approximately 3 0 Hz. A plate is connected to the dished base portion 3 by supporting means 5a and 5b which consists of a rigid vertical member 5a and flexible horizontal strips 5b so as to allow vertical movement of the plate while preventing significant lateral movement of the plate 4« Radial cuts 16 in the plate 4 enable it to move vertically on the strips 5 without generating significant stiffness forces in the plate. The plate 4 is provided with nine first apertures 7 equiangularly spaced around a 500mm diameter pitched circle centred on the centre of the plate, which apertures are bell-mouthed so as to converge from the lower to the upper side of the plate ? each having a smaller diameter of 40mm and a larger diameter of 60mm and is provided with a single central aperture 8 bell-mouthed so as to converge from the upper to the lower side of the plate 4 > having a smaller diameter of 120mm and a larger diameter of l8θmm. The outer diameter of the plate i 590mm so that the flow through the annular aperture 14 bounded by the rim 12 of the plate 4 and the wall 15 of the container 2 is insignificant. The effective stiffness of the horizontal strips 5a is k = 7-90 x Nm and the effective mass of the plate 4 is m = 2.0kg so that the natural frequency of the impeller means comprising the plate 4 and the supporting means 5a and 5b is f n = ( n /2τr) = 100Hz and so is equal to the frequency of operation of the vibrator 6. The damping ratio, c/c c , of the plate 4 in the process fluid is c/c c = 0.025. The maximum safe amplitude, x ιn , of vibration of the base portion 3 to avoid fatigue failure is in this case approximately 0.25mm. The amplitude ratio, x 2 ~ / .Λ, achievable with the damping ratio quoted is x 20 / χ ιo = 20.02, giving a majimum allowable amplitude of vibration of the impeller of approximately X , Q = 5«0mm. With this amplitude and frequency of vibration and with the quoted damping constant c, the power input P to the process fluid 1 is found to be P = 310 watts, sufficient to provide very effective π xing. The frequency responses of the base portion 3 and the impeller plate 4 and the amplitude ratio x 2 o/ χ 10 are as se ^ ou * in equations (3), (4) and (5) respectively and are presented graphically in Figures 7, 8 and 9 respectively. The amplitudes x and x _ at lOOHz are found to be 1.0603 mm/kN and 0.0529 mm/kN respectively. In order to generate the required amplitudes of x 20 = 5•0mm and x, 0 = 0.25mm, a driving force must be provided by the vibrator 6 with an amplitude F given by 1.060 0.0529 or F = 4700N The motion of the impeller 4 and/or the wall portion 3 can be detected andusedtocontrol an active element which either changes dynamically the spring-mass characteristics of the impeller means comprising the plate 4 and the supporting means 5 or inserts an additional force on the wall portion 3. By these means, the ratio of the amplitude of the impeller 4 to that of the wall portion 3 may be better controlled compared to the case where no active element is used. The plate can be instrumented for any of a wide range of variables such as ' acceleration, temperature and flow rate through the apertures. Such variables could be used as a means of deducing the properties of the fluid under mix. Optionally, the fluid properties so deduced could be used as a means of controlling the processes taking place within the vessel. Where motionoftheplate is used as a means of deducing fluid properties, it may be necessary to measure the movement of the wall portion 3 as well. The detector for controlling the active element and the instruments can be connected to the exterior of the container by leads in a bore of the support 5 > thus avoiding entry into the fluid under mix. In the previously described eπ_.c<iiments, the frequency of vibration of the wall portion 3 has been chosen in order to achieve a maximum ratio of the amplitude of vibration of the plate 4 to that of the wall portion 3- When the ratio is unity, the plate 4 and the wall portion 3 vibrate in syncronism and there is no change in dimensions of the supporting means 5« This arrangement is described in our earlier application PCT/GB84/00102. The present invention coversetherarrangements, -_f.4- ) where the amplitude ratio is greater than one, α l also where the amplitude ratio is negative, so that the plate 4 and the wall portion 3 vibrate in antiphase. The supporting means 5 will flex to allow this antiphase vibration and the relative movement will cause considerable agitation of the fluid. The optimum frequency for this purpose can be selected by experiment, but is believed to occur when the frequency of vibration of the wall portion 3 is approximately equal to the higher (out of phase) natural frequency of the two-degree-of-freedom system comprising the wall portion 3 and the impeller means comprising the impeller 4 and the supporting means 5 which is illustrated in Figure 1 and the theory of which was discussed above. The relative motion of the plate 4 and the wall portion 3 can be found by subtracting equation 3 from equation 4 above and the frequency should be selected so that the difference is a maximum. Although the enfoodiments described above have been concerned with the mixing of fluid in a closed container, it would be possible to operate in a open container, and also to provide an inlet and an outlet for the container so that it can be used for continuous mixing. The support 5 and the impeller 4 could be provided as an add-on assembly to be fitted into a container. This might for example be connected to the existing lid of a container which would act as the wall portion 3- As an alternative the support 5 and the impeller 4 could be connected to a second lid which would act as the wall portion 3 and which would replace the existing lid when mixing of the container contents is required.

Claims: CLAIMS 1. Apparatus for agitating a fluid medium, for example to effect mixing of two or more fluids , comprising a container 2 for the fluid medium and impeller means 4 & 5 located within the container and movable to effect fluid flow, characterised in that the container 2 has a wall portion 3 and the impeller means 4 6 5 comprises an impeller 4 separate from the wall portion 3 and supporting means 5 connecting the impeller to a point on the wall portion, the impeller means 4 & 5 being flexible such that a point on the impeller is movable relative to said point on said wall portion. 2. Apparatus as claimed in claim 1 comprising a vibrator 6 for vibrating said wall portion 3 » the characteristics of the vibrator 6 the wall portion 3 a d the impeller means 4 & 5 being chosen so that when the vibrator is activated the im¬ peller 4 vibrates with a greater amplitude than the wall portion 3» 3. Apparatus as claimed in claim 1 comprising a vibrator 6 for vibrating said wall portion 3 at a frequency approximately equal to a resonant frequency of the impeller means 4 & 5 * 4. Apparatus as claimed in any one of claims 1 to 3 where the impeller is a plate 4. 5« Apparatus, as claimed in any one of claims 1 to 4 wherein the impeller 4 is provided with at least one aper- ture 7 or 8. 6. Apparatus, according to claim 5, in which each aperture 7 or 8 presents a lower resistance to flow from one side to the other side of the impeller 4. 7. Apparatus, according to claim 5, in which each first aperture 7 presents a lower resistance to flow from one side to the other side of the impeller 4 than to flow from said other side to said one side of the impeller 4 and each second aperture 8 presents a lower resistance to flow from said other side to said one side of the impeller 4 than to flow from said one side to said other side of the impeller 4. 8. Apparatus, according to either claim 6 or claim 7, in which the rim 11, 12 of the impeller 4 is shaped so that the aperture 13 » 14 bounded by said rim 11, 12 and the wall 15 of the container 2 presents a lower resistance to flow from the other side to the one side of the impeller 4 than to flow from said one side to said other side of the impeller 4. 9 * Apparatus, according to either claim 6 or claim 7, in which one half 11 of the rim 11, 12 of the impeller 4 is shap¬ ed so that the half 13 of the aperture 13 , l4 bounded by said half 11 of the rim 11, 12 and the wall 15 of the container 2 presents a lower resistance to flow from one side to the other side of the impeller 4 than to flow from said other side to said one side of the impeller 4 and in which one half 12 of the rim 11, 12 of the impeller 4 is shaped so that the half 14 of the aperture 13, l4 bounded by said half 12 of the rim 11, 12 and the wall 15 of the container 2 presents a lower resist- ance to flow from said other side to said * one side of the im¬ peller 4 than to flow from said one side to said other side . of the impeller 4. 10. Apparatus, according to any one of the preceding claims comprising sensor means to detect motion of the impeller 4 and 5 and/or the wall portion 3 * 11. Apparatus as claimed in claim10 wherein the support is hollow and contains in its hollow bore signal leads from said sensor to the exterior of the container. 12. Apparatus as claimed in claim 10 when dependent on claim 2 or 3 wherein said vibrator 6 is responsive to the output of said sensor means. 13. A method of agitating a fluid medium in a container which has a wall portion on which flexible impeller means is mounted within the container, the impeller means comprising an impeller separate from the wall portion and supporting means connecting the impeller to a point on the wall portion, the method comprising causing the impeller means to flex such that a point on the impeller is movable relative to said point on the wall portion 3- 14. A method as claimed in claim 13 comprising vibrating the wall portion 3 and selecting the characteristics of the vibrator 6, the wall portion 3 and the impeller means 4 and 5 so that when the vibrator is activated the impeller ά vibrates with a greater amplitude than the wall portion 3. 15- A method as claimed in claim 13 comprising vibrating said wall portion 3 at a frequency approximately equal to a resonant frequency of the impeller means. 16. A method as claimed in any one of claims 13 to 15 comprising directing the fluid flow in the container on movement of the impeller by providing holes in the impeller which present a lower resistance to flow from one side to the other side of the irnpellerthan to flow from said other side to said one side of the impeller. 17. A method άs claimed in Claim 13 wherein the impeller means is caused to flex by shaking the container bodily. l8. A method άs claimed in Claim 13 comprising vibrating the wall portion and selecting the characteristics of the vibrator 6, the wall portion 3 and the impeller means 4 and 5 so that when the vibrator is activated, the impeller 4 vibrates in antiphase to the wall portion 3« 19. A methodάs claimed in Claim 13 comprising vibrating the wall portion 3 at a frequency apprOximately equal to the higher mode natural frequency of the two-degree-of-freedom system comprising the wall portion 3 and the impeller means 4 and 5.

Inventors: POLLARD GEOFFREY JOSEPH, POLLARD, GEOFFREY, JOSEPH
Applicants: BRITISH HYDROMECHANICS, THE BRITISH HYDROMECHANICS RESEARCH ASSOCIATION
Application year: 1984
Main classification: B01F11
IPC codes: B01F11, B44D3