Machine based on inertial rotational forces operating as a turbine or a pump

Abstract

A machine based on rotational inertial forces operating as a turbine or a pump is described.

Description

[0001] The present invention relates to a machine based on rotational inertial forces operating as a turbine or a pump in accordance with the classifying part of claim 1.

[0002] The following description is divided in the following paragraphs:

[0003] A. characteristics and advantages of the turbopump,

[0004] B. construction details of the turbopump,

[0005] C. operation of the machine as a turbine or a pump,

[0006] D. valve opening and closing mechanism,

[0007] E. inertial forces employed in the liquid of the turbopump and balancing of the reactions transmitted to the supporting frame,

[0008] F. the turbopump connected to a filling tank and a drain tank,

[0009] G. control of the power exchanged between a motor and a user, and

[0010] H. claims.

[0011] A. Characteristics and Advantages of the Turbopump

[0012] 1. In operation of the machine as a turbine the latter with the increase of revolutions per second of the user shaft develops thereon a moment automatically decreasing continuously from a maximum to a null value. Therefore the machine can replace with great advantage the stepped velocity change controlled and based on toothed wheels.

[0013] 2. Change of the machine as a turbine or a pump is extremely simple because it is done only by changing the motor shaft rotation velocity or that of the user shaft.

[0014] 3. The machine's output is high. It is subject only to the hydraulic leaks due to the passage of the liquid in the tubes and to the mechanical leaks of the connecting shaft-connecting rod & crank system.

[0015] 4. When operating as a turbine the machine converts pressure energy subtracted from the liquid into mechanical energy yielded to the crankshaft. When operating as a pump the machine converts the mechanical energy absorbed from the crankshaft into liquid pressure energy.

[0016] 5. The hydraulic machine operating as a turbine develops on the crankshaft a moment decreasing with the increase in the number of rps of the user shaft by a maximum value for n=0 to a null value for n=no. For n>no, the machine operates as a pump. In this case the direction of the velocity of the resultant applied to the liquid contained in the active circuits and the pressure developed increases with (n2−no2).

[0017] B. Construction Details of the Turbopump

[0018] In the patent description of the present application there are symbols, physical magnitudes, mathematical expressions and circuits identical to those used in the description of the patents EP0964161A1 and U.S. Pat. No. 6,395,917B1 of the pump based on identical rotational inertial forces.

[0019] A basic difference is the use instead of one-way valves in the machine described below of two-way valves which allow interesting applications described below.

[0020] In FIG. 1/5 the construction diagram of the turbopump is summarized. It consists of a rotor R1 oscillating with a maximum rotation of ±φ0 around the shaft 1 fastened to the supporting frame 7. The oscillation mechanism of R1 consists of the connecting rod 3 whose small end is coupled to the piston pin 2 fastened at R1 and with its big end coupled to the pin 4 of the crank 5. The latter is fastened to the crankshaft 6 parallel to the shaft 1 which rotates at angular velocity φ′=dφ/dt on bearings fastened to the supporting frame 7. To the rotor R1 is rigidly fastened a hydraulic circuit consisting of a tube whose axis is curved around a circumference whose center belongs to the axis of the shaft 1 which is perpendicular to the plane of the circumference. To the tube are applied two apertures with cross section SA and SB having common axis A-B which has a point in common with the axis of the shaft 1.

[0021] The longitudinal axis of the tube is divided by the axis A-B in two semicircumferences corresponding to two active circuits designated C1 and C1. Each of the latter going from point B towards A has respectively a left-hand direction and a right-hand direction. At the ends of C1 and C1, there is inserted respectively the pair of identical two-way valves (V1, V11) and (V1′, V11′) The two pairs are controlled mechanically so that the pair (V1, V11) and the pair (V1′, V11′) are respectively open only in the interval θ(0°, 180°) and the interval θ(180°, 360°). With this arrangement the following advantages are secured: (a), independence of the two pairs (C1, f1) and (C1′, f1′) where f1 (respectively f1′) is the force generated by the liquid of C1 (C1′) which in this manner can operate only in the respective circuit; (b) the two-wayness of the valves allows in each circuit a velocity of the liquid in two opposite directions and therefore a single machine can operate either as a turbine or a pump; c) transfer to the rotor of the kinetic energy of the liquid corresponding to its relative velocity with respect to the circuit at the moment of closing of the valves. It is noted that at C1 for ν=180° and at C1′ for ν=360° the liquid respectively contained has the maximum relative velocities and therefore the closing of the valves causes a considerable impulse of moment on the crankshaft.

[0022] It is noted that the oscillation system by means of connecting rod and crank can, with the advantage of less encumbrance and saving of components, consist of the crankshaft 5 to which is fastened eccentrically a ball bearing whose external ring can rotate resting with close tolerance alternatively in the intervals θ(0°, 180°) and the interval θ(180°, 360°) only on one of the two parallel blades equidistant from the oscillation axis of R1 to which they are welded.

[0023] It is also noted that the active circuit Ci (i=1, 1′) consisting of a semicircumference can also be realized by a circuit made up of a cylindrical or Archimedean spiral. The two active circuits Ci made from a cylindrical spiral with an uneven number of superimposed layers are made up of a whole number of turns to which is added a final half-turn. The 2-phase circuit is obtained by connecting the two half-turns of two identical circuits so that the two circuits Ci starting from their point of connection are wound with opposite rotation direction. The 2-phase circuit wound as an Archimedean spiral consists of two circuits Ci wound as Archimedean spirals which must be wound with opposite direction starting from the initial point. The cylindrical and Archimedean spiral windings are particularly suitable in high pressure cases.

[0024] C. Operation of the Machine as a Turbine or a Pump

[0025] It was established that in the interval θ(0°, 180°) only the valves of the circuit C1 should be open where the left-hand force f1 (FIG. 1/5) is developed and that in ν(180°, 360°) only the valves of the circuit C1′ where the right-hand force f1′ is developed should be open.

[0026] It was also established that the external force fe should have direction from SA to SB (FIG. 1/5) and therefore it has a direction opposite to that of the inertial forces f1 and f1′ developed in the circuits C1′ where i=1, 1′.

[0027] From the established conditions it follows that the series (f1−fe) causes acceleration of the mass m0 of the liquid of Ci expressed by: 1$\begin{array}{cc}\frac{d^2{S}_i}{{\mathrm{dt}}^2}=\frac{1}{m_0}\left({\stackrel{\_}{f}}_i-{\stackrel{\_}{f}}_e\right)& 1)\end{array}$

[0028] From (1) is inferred the following value of the relative displacement of the liquid of the circuit Ci in θ(0°, 180°) and in θ(180°, 360°): 2$\begin{array}{cc}S\left({180}^{\circ }\right)=2\pi {\phi }_o{r}_o\frac{n^2-n_o^2}{n_2}& \left(2\right)\end{array}$

[0029] where φ0 is the maximum rotation angle of the rotor oscillatory motion to which corresponds the mean value {overscore (f)} and n0 is the number of rotations per second of the crank to which corresponds the equalization {overscore (f)}i={overscore (f)}e.

[0030] From (2) is inferred the mean value of the velocity of the circuit Ci in θ(0°, 180°) and θ(180°, 360°). 3$\begin{array}{cc}{\stackrel{\_}{v}}_c={\mathrm{nS}}_i\left({180}^{\circ }\right)=2\pi {\phi }_o{r}_o\frac{n^2-n_o^2}{n}& \left(3\right)\end{array}$

[0031] from which is found the flow:

Q={overscore (ν)} c S c   (4)

[0032] For n<n0 velocity {overscore (ν)}c expressed by (3) has a right-hand direction opposite to that of fi and the machine when operating as a turbine transfers to the rotor the power fi{overscore (ν)}c yielded by the liquid of Ci. For n>no the velocity {overscore (ν)}c has the same direction as fi and the machine when operating as a pump having a head of fe takes from the rotor the power:

P fi ={overscore (ν)}c{overscore (f)}i  (5)

[0033] which it transfers to the liquid of Ci.

[0034] From the integration of (1) it follows that when operating as a turbine, for n<no the liquid of the circuit C1′ at closing angle θ=180° of its valve V1 has a maximum relative velocity and direction identical to that of the rotor expressed by: 4$\begin{array}{cc}{v}_c\left({180}^{\circ }\right)=4\pi {\phi }_o{r}_o\frac{n^2-n_o^2}{n}& \left(6\right)\end{array}$

[0035] Accordingly the closing of the valve V1 causes transmission to the rotor R1 of the kinetic energy: 5$\begin{array}{cc}{E}_c=m_o\frac{v_c^2\left({180}^{\circ }\right)}{2}& \left(7\right)\end{array}$

[0036] The same phenomenon is repeated for the angle θ=360° at which upon closing of the valve V1′ there is transmission to R1 having maximum velocity and direction identical to that of the liquid, of an identical Eo of the liquid of the circuit C1′. Accordingly the power developed by the liquid of the circuits for closing of the valves is: 6$\begin{array}{cc}{P}_{\mathrm{CH}}=n{m}_o\frac{v_c^2\left({180}^{\circ }\right)}{2}& \left(8\right)\end{array}$

[0037] For (5) an (8) it follows that the total power developed by the turbine is: 7$P=P_{\mathrm{fi}}+P_{\mathrm{CH}}={\stackrel{\_}{f}}_i{\stackrel{\_}{v}}_c+n{m}_o\frac{v_o^2\left({180}^{\circ }\right)}{2}$

[0038] Power P is transmitted to the rotor R1 and to the crankshaft in accordance with the following equations:

P=P fi +P CH =P R1 =P MA   (10)

[0039] where

P R1 =r 0 {overscore (f)} R1 {overscore (φ)}

[0040] in which FR1 is the mean value of the reaction caused on the rotor by the power Pfi and PCH and {overscore (φ)} is the mean value of the angular velocity of R1 in φ(0, φ0).

[0041] In addition:

P MA =r MA {overscore (f)} MA θ  (11)

[0042] where rMA is the radius of the crank and {overscore (f)}MA is the mean value of the reaction on the crank caused by the power PR1.

[0043] Similar phenomena take place in the operation of the machine as a pump at valve closing.

[0044] From the above relationships it is inferred that in operation of the machine as a turbine the mean value of the moment transmitted to the crankshaft aMA and the user is due to the summation (Pfi+PCH)/θ′ which with change of the number of rps changes by a maximum value for n=0 to a value null for n=no.

[0045] In addition said tendency occurs continuously and automatically and without the use of any particular device.

[0046] For n>no the machine operates as a pump developing the power expressed by P1=nfiS(180°). It displays the following advantages: (1) the pump has an upper limit of rps established only by the mechanical strength of its components and not due to functional motives as for example in the piston pump. In addition it has no preferred velocity like for example the centrifugal pump. (2) With the change in rps the pump develops a flow rate, pressure and power respectively increasing with:

[0047] n, n2, n3 while the output tends to increase with n. Accordingly with variation of the rps it can vary its field of applicability in a broad range. 3) The pump furthermore has no mechanical components except the valves in contact with the liquid pumped and therefore with an appropriate choice of materials is particularly suited to pumping of dangerous and corrosive liquids.

[0048] D. Valve Opening and Closing Mechanism

[0049] The mechanism consists of (FIG. 2/5): (1) four shafts a1(i=1, 2, 3, 4) rotating on bearings with vertical axis fastened in a central position to the side walls of the circuits Ci; (2) toothing D1 (i=1, 2, 3, 4) applied to the end of each shaft ai in a position outside the circuit; (3) a closing and opening plate Li(i=1, 2, 3, 4) each fastened to the corresponding shaft aL within the corresponding circuit Ci; and (4) two cylindrical segments 8 and 9 fastened to the supporting framework and on each of which are fastened two toothings d1(i=1, 2, 3, 4) each of which can couple with the corresponding toothing D1 only for one 90° rotation of the corresponding plate Li. In the case of sinusoidal oscillation of the rotor R1 and left-hand rotation of R1 in θ(−90°, +90°) with change of the angle θ of the crank to (0°, 180°) and of the corresponding angle ω of the rotor the mechanism gives the following results: (1) for θ−0 and ω=0 the four plates Li of the valves V1 are in closed position and velocity ω>0 of R1 is maximum. An increase of θ causes coupling of the toothings (D1, d1) and (D2, d2) and beginning of the opening phase which terminates for 0=0 and and ω=ω1 with a tangential position of L1 and L2 with respect to the longitudinal axis of C1. At the same time the blades L3 and L4 remain in the closing position. (2) for θ=90° and ω=ωo the left-hand force f1>0 is maximum and velocity ω′ of R1 is null. (3) With an increase in θ rotor velocity is ω′<0 and a force fi>0 until for θ=180°−θ1 and ω=ω1 uncoupling of the toothing (D1, d2) and (D2, d2) starts. (4) For θ=180° and ω=0 and a maximum right-hand velocity ω′<0 the coupling of the toothing (D1, d1) and (D2, d2) ends, closing of the blades L1 and L2 is completed and coupling of the toothing (D3, d3) and (D4, d4) initiates. (5) for θ=180°+θ1 and ω=−ω1 the plates have reached the tangential position with respect to the axis of the circuit C1. (6) for ν=270° and ω=−ωo the right-hand force f1′<0 is maximum and velocity ω′ null. (7) To an increase in θ corresponds a 107 ′>0 and f1<0 until the uncoupling phase of the toothing (D3, d3) and (D4, d4) initiates for θ=360°−θ1 and ω=−ω1 which terminates for 0=360°, ω−0, maximum velocity ω′>0 and plates L3 and L4 in closing position.

[0050] It is noted that the closing and opening operation of the valves V1 takes place with the rotation of a very small angle ω1 because of the very high axle ratio (radius ro of C1 /radius of a1). In addition the baricentric position of the shafts a1 cancels the moment generated thereon by the motion of the liquid and reduces their stress. To avoid hydraulic leaks stuffing boxes are arranged at the crossings of the circuits C1 and C1, by the shafts 1 and 1′.

[0051] E) Inertial Forces Employed in the Liquid of the Turbopump and Balancing of the reactions Transmitted to the Supporting Framework

[0052] With reference to the above statements the inertial forces employed in the operation of the turbopump (FIG. 3/5) are of two types, to wit: (a) the pair of rotational inertial forces f1 and f1′ with identical semisinusoidal trend. The f1 has a left-hand direction and is generated in θ (0°, 180°) in the liquid of C1 by a change in the velocity of R1 from a maximum left-hand value to a maximum right-hand value. The f1′ has a right-hand direction and is generated in θ (0°, 180°) in the liquid C1′ by an equal and opposite change in velocity of R1. (b) The pair of impulsive inertial forces fCH and fCH′ corresponding to the closing of the valves of the circuits C1 and C1′ at the end of the above mentioned intervals and the sudden stopping of the relative velocity of the liquid of the circuits C1′ which has reached maximum value and in addition is concomitant with a maximum rotating velocity and same direction as the rotor. The forces fCH are useful because they return to the rotor the kinetic energy of the velocity of the liquid and because they equalize the trend of the inertial forces fi at the points where they are null (FIG. 3/5).

[0053] Balancing of the reactions to the inertial forces due to the oscillatory motion of the rotor and transmitted to the supporting framework can be obtained by using a flywheel having a moment of inertia identical to that of the rotor R1 with respect to an axis of rotation parallel to that of R1. It must also be subjected to oscillatory motion which differs only for a phase difference of 180° with respect to the phase of the rotor to be balanced.

[0054] (F) The Turbopump Connected to a Filling Tank and a Drain Tank

[0055] It consists (FIG. 4/5) of a machine identical to the one shown in FIG. 1/5. In it the section SA is connected by a tube to a filling tank SC arranged at a geodetic height and which develops the pressure Pe and the external force applied to the machine fe=peSA. The external force fe can also be developed by a pump whose outlet is connected to the section SA. In particular the pump can be based on rotational inertial forces. The section SB is connected by a tube to a drain tank SS. Oscillation of the rotor R1 is caused by a connecting rod & crank system as designed or by a shaft system aMA to which is applied a bearing in eccentric position whose external ring rotates between two blades fastened to R1 as described above. Oscillation of the rotor R1 generates the inertial forces whose mean value — and in case of sinusoidal oscillation of the rotor— is as above {overscore (f)}i=8πm oφoron2 indicated. The machine operates as a turbine or as a pump depending on whether the rps of the crankshaft of mean value equal to f1 viz. {overscore (f)}i is less or more than n=no=(fe/moφoro){fraction (1/2)}. Operation of the machine as a turbine allows conversion of the potential pressure energy accumulated in the tank SC into mechanical energy of the crank aMA and allows use of said energy for mechanical purposes. A motor applied to the shaft BMA with n>no allows operation of the machine as a pump to transfer the liquid from the tank SS to the tank SC to create a reserve of energy which can be used later.

[0056] G. Control of the Power Exchanged Between a Motor and a User

[0057] Control of the power exchanged between the shaft aMO of a motor MO and the shaft aUT of a user UT implies the following two problems: (a) control of the power transmitted by the shaft aMO to the shaft aUT, and (b) control of the power transmitted from the shaft aUT to the shaft aMO and its utilization.

[0058] If it is {overscore (f)}j−{overscore (f)}i>0 where j=2, 2′ and i=1, 1′ (FIG. 5/5) there is a right-hand velocity νc of the liquid contained in the circuit of which the sections SA1, SB1, SB2 and SAZ are parts. Accordingly the machine MA2 operates as a pump which converts the mechanical power of the shaft aMO of the motor MO into hydraulic power which is transferred to MA1 operating as a turbine. The latter converts the hydraulic power into mechanical power which is transferred to the shaft aUT of the user UT.

[0059] Designating by n1 and n2 respectively the number of rps of the shafts aUT and aMO it can be stated that, (a) the machine MA1 develops power null for n1=0 and for n1=n2 while for n1 satisfying to 0<n1<n2 we have:

P={overscore (f)} i {overscore (ν)} c +P CH ≠

[0060] where is

{overscore (f)} i =8πmoφoron12

[0061] and

{overscore (ν)}=K (n2−n1);

[0062] (b) that the machine MA1 for n1=nm where n1<nm<n2 develops a maximum power PM and accordingly the moment applied to the shaft by the user MUT=P/2n′n1 in the interval n1(0, nM) increases with the increase of n1 while it decreases with the increase of n1 in n1(nM, n2).

[0063] Accordingly the MA1 for {overscore (f)}2{overscore (f)}1>0 develops an ideal moment for connection of any motor to any user.

[0064] For {overscore (f)}2{overscore (f)}1<0 the machines MA2 and MA1 operate respectively as a turbine and a pump and accordingly the mechanical power connected to auT is transmitted to aMO. In this case the corresponding energy, if the phenomenon is of brief duration, can be stored in fly-wheel weights. If the phenomenon is of long duration it can be used with other suitable systems.

[0065] Change of sign of the relationship {overscore (f)}2−{overscore (f)}1 can be accomplished be merely changing the number of rps of MO. In addition the series of two machines MA2 and MA1 is allowed even in the presence of an even very high ratio of their oscillation frequency and without the need of a speed reducer.

[0066] The system can be particularly advantageous in the field of automobile traction by replacing the speed change gear with toothed wheels having a limited number of ratios and requiring in addition a clutch and an appropriate control with the above described system having an automatic and continuous control. {overscore (f)}2−{overscore (f)}1>0 in addition as assumed above in para. (b) the system proposed can even avoid the dispersion of energy with {overscore (f)}2−{overscore (f)}1<0 more or less extended braking as it can be appropriately used after its transfer to the drive shaft.

Claims

1. Machine based on rotational inertial forces operating as a turbine or a pump characterized in that it consists of the following components, to wit, (a) a mechanism made up of a crankshaft, crank and connecting rod designed to generate the oscillatory motion of the rotor R1, (b) a tube fastened to R1 curved and closed on itself and communicating with an inlet SA and an outlet SB dividing the tube in two circuits C1 C1′ in such a manner that the surface area of their projection on a plane perpendicular to the oscillation axis of R1 is equal, (c) four 2-way valves each inserted at each end of C1 and C1′ and operated by a mechanism in which with to complete oscillation of R1 corresponds a left-hand rotation of 360° of the cranks causing opening of the pair of valves of C1 only in the interval θ(0°, 180°) and opening of the valves of C1′ only in the interval θ(180°, 360°) with the origin of the angle θ being fixed so that for θ=0° there is a corresponding maximum left-hand velocity of the rotor and for θ=180° the maximum right-hand velocity. In this manner the liquid of C1 develops a left-hand inertial force f1 and the liquid of C1′ an identical right-hand inertial force f1′. In addition both are oriented towards the cross section SA to which is applied the external force fe with opposite direction with the forces fi increasing with the velocity of rotation of the cranks so that for a mean value fi less than fe the velocity of the liquid of Ci has a direction from SA to SB and the machine operates as a turbine while for {overscore (f)}i>{overscore (f)}e the machine it operates as a pump.

2. Machine in accordance with claim 1 characterized in that the valve opening and closing mechanism consists of the following components, to wit, a shaft parallel to that of the rotor R1 rotating in baricentric position in C1 on bearings fastened to R1 to the outside of C1 and having a side toothing and a blade fastened to said shaft in the active circuit to realize opening and closing of the valve; a cylinder segment fastened to the supporting frame with a toothing which for reciprocal motion of R1 couples for a short arc with the above mentioned side toothing with all being arranged in such a manner that with each 180° rotation of the crankshaft the above mentioned shaft in rotating with the rotor in an angle ±φ0 and coupling with the toothing of the cylindrical segment at the beginning and the end of the angular path causes alternately rotation by ±90° of the valve closing and opening member with an identical mechanism being provided for each valve.

3. Machine in accordance with claim 1 characterized in that the closing and opening member of the active circuits consists of a blade fastened to a rotating shaft in a position such that the moment generated on said shaft by the liquid of the circuit is null.

4. Machine in accordance with claim 1 characterized in that the reactions transmitted to the supporting frame and caused by the inertial force of the oscillatory motion of R1 are balanced by a flywheel having inertial moment identical to that of R1 and subjected around an axis parallel to that of R1 to an oscillatory motion differing from that of R1 only by a 180° phase difference.

5. Machine in accordance with claim 1 characterized by the system consisting of the series Filling tank Sc-turbopump-Drain Tank Ss with the machine operating as a turbine with a number of revolutions per second of the crankshaft n<no for which the mean value of the inertial forces developed in the active circuits of the machine is less than the external force generated by the geodetic height of the filling tank Sc with the turbine in this condition converting the liquid pressure energy of the tank Sc into mechanical energy of the user employing an ideal moment decreasing with the increase in the number of revolutions per second of its shaft with the liquid used being dumped at the same time into the drain tank Ss with a motor applied to the crankshaft with a number of revolutions per second n>no causing operation of the machine as a pump and transfer of the liquid from the tank Ss to the tank Sc to constitute an energy reserve usable subsequently.

6. Machine in accordance with claim 1 characterized by the series of two machines MA2 and MA1 with cross sections (SA2, SA1) and ( SB1, SB2) connected hydraulically and with crankshafts of MA2 and MA1, connected respectively by means of connecting rods to the shaft of the motor aMO and of the user aUT for {overscore (f)}2−{overscore (f)}1>0 with the machine MA2 operating as a pump transmitting power of the motor MO converted into hydraulic power to the machine MA1 operating as a turbine while the turbine converts the hydraulic power into mechanical power and transmits it to the user by employing a moment decreasing with the increase in revolutions per second and the above mentioned series being able to replace advantageously any geared speed changer with in addition the series for {overscore (f)}2−{overscore (f)}1<0 transferring to the motor the kinetic energy of the user which can be appropriately utilized.

7. Machine in accordance with claim 1 characterized by connection of the two machines MA2 and MA1 which exchange the hydraulic and mechanical power even in the presence of a very high ratio of the two frequencies of their oscillatory motion giving the advantage of avoidance of the use of a speed reducer.