WO2006100528A1

WO2006100528A1 - Fluid-mechanic self-adjustable power transfer systems via linear feedback with real time load torque meters (c. v. t.)

Info

Publication number: WO2006100528A1
Application number: PCT/GR2006/000012
Authority: WO
Inventors: Nikolaos Botsis
Original assignee: Nikolaos Botsis
Priority date: 2005-03-21
Filing date: 2006-03-17
Publication date: 2006-09-28
Also published as: GR20050100141A

Abstract

This invention relates to self-adjustable linear power transfer systems consisting of compression pumps and hydraulic motors of any kind as well as solid gear elements with the use of a planetary mechanism according to the systems - A1 -B x -C 1 -D l - aiming at the transfer of power of a wide range, wherein a mechanical linkage (9) allows a torque feedback from a torque meer (5) on the output shaft (16;19). This enables to regulate a constant output torque.

Description

FLUID-MECHANIC SELF-ADJUSTABLE POWER TRANSFER SYSTEMS VIA LINEAR FEEDBACK WITH REAL TIME LOAD TORQUE METERS ( C . V . T . )

This invention relates to fluid-mechanic self-adjustable systems of mechanical power transfer able to meet variable loads of wide range either by using pumps and hydraulic motors (of any kind) or via solid coupled gear elements like the use of a planetary gear system always coupled with real time load torque meters that cooperate with one to one correspondence mechanisms of linear feedback in order to transform the power transfer systems to linear systems. The power transfer systems of continuously variable transmission (CVT) are more and more applied to many sectors of modern technology. From 1877 up to the present day people search for the appropriate system of continuously variable transmission to meet great and continuously variable loads. The first industrialized CVT was Variomatic manufactured in the 1950s and was applied only to small vehicles. A latter system in the 1990s was TOROTRAC - CVT that has also not provided the desired solution to the problem concerning the transfer of bulk power. While several CVT systems have been tried from time to time, none could bring the desired result up to now.

The systems of the present invention relate (besides others) to sectors requiring bulk power like the automobiles sector, wind energy, massive production of electric power via hydraulic turbines, drilling, shipbuilding and aerospatial technology.

Brief presentation of the figures depicting the systems of linear power transfer - A₁ - Bi - Ci and Di -. System - Ai -, Figure - 1 -.

Figure -1- depicts a self-adjustable fluid-mechanic system of linear mechanical power transfer (rotating by fluid power) coupled to a mechanical torque meter, which cooperates with a feedback mechanism. The system consists of the pump (1) supplying two- directional (Ni-N₂) fluid power, put into motion by the power producing motor (E), the circuits (N - N_x - R₁ - R - N₂ - R₂ - R), the hydraulic motor (2), the rotor (3) whose longitudinal shaft forms a mechanical torque meter (of one-sided axial thrust) with the elements (4-5-V-6-7-C-K) and the mechanism of linear hydraulic feedback distributor dependent on the elements (8 - 8_A - 9 - 10- ll - ll_A- 12). System - Ai — , Figure — 2 -.

Figure —2- depicts the longitudinal part of the rotor (3_B), as it forms a torque meter of inclined plane via an endless screw (14), while the nut (15) transfers the mechanical information (for the transformation of the load on the output shaft) on the one hand to the balance spring of the torque meter and on the other hand to the feedback system (12) through the arm (8_B).

System - Bi -, Figure — 3 -

In Figure -3- a self-adjustable fluid-mechanic system of linear mechanical power transfer is depicted, similar, as far as the basic elements are concerned, to the system - Ai - that comprises the pump (1) with two-directional supply and the hydraulic motor (2) and similar with regard to the arrangement of the hydraulic circuits of the fluid power. The main difference is in the system of the torque meter, whose sensor shaft (19), since it affects a pair of rings facing towards opposite directions (18R-18_L) and forces them to concurrent convergence with equal force distribution, is the reason why (since it is a power output shaft) it is not subjected to axial thrust.

System - Ci -, Figure - 4 -.

Figure -4- depicts a planetary gear system with one input - two outputs, consisting of gear elements (- 21 - 22 - 23 - 24 - 25 -) whose one output comprises the torque meter of the system - Bl - while the other output is coupled to the power input (26) of the closed circuit pump (27). The operation of the pump is controlled (linearly) by the feedback system (12) that is guided automatically by the torque meter, which is determined by the load. In this way a self-adjustable system of linear mechanical power transfer is created. System - Ci — , Figure - 5 -.

Figure —5- depicts a torque meter with the abilities of the meter of figure -A-, which is not subjected to axial thrust. It consists of the sensor shaft (19A), which comprises the opposite facing screws (14_L-14R) of left-hand and right-hand thread that cooperate with the nuts (15_L-15_R) on which the balance spring (7π_>) is mounted.

System - Ci -, Figure - 6 -.

Figure -6- depicts the system -Ci- with feedback mechanism with the use of an electricity generator (M) via the controllable load (A) guided by the torque meter of the system.

System - Di -, Figures - 7-8-9- and -10 -.

Figures —7-8- and -9- depict a fluid-mechanic load torque meter with radial piston arrangement It consists of the rotor's shaft (3_D) that is incorporated either into the part (37) comprising the cylinders (36) or with the casing (45), which comprises internally the cavity (44), whose wall (44_A) has ellipsoidal form. It also consists of the sensor shaft (30) that forms either an elliptical lobe (3 I_A) or a cluster of cylinders (31_B). Figure -10- depicts a self-adjustable fluid-mechanic system of linear mechanical power transfer that comprises a hydraulic torque meter as depicted in figures -7-8-9-. Its main characteristics are the fluid power pump (1) with two-directional supply, the hydraulic motor (2_A) with the hydraulic torque meter of figure —9- and the feedback system (12_B).

Figure -11- depicts a mechanism of linear feedback with the elements (12_G) that comprises the thermostatic system (47-T-10_A-46-G-9_G), which corrects continuously the position of the ball (10_A) according to the geometry of the linearly variable cross-section in cavity (11) in relation to the temperature of the hydraulic fluid. Ih addition, Figure -12- depicts a system of linear feedback that can take the form of a linearly variable cross- section through-hole (49) that lies transversely across the body of the piston (48) moving inside the cylinder (50), which has the communication port (51). Reference to the electromotor (E), the pumps and the hydraulic motors. a) The depiction of the electromotor (E) of constant number of revolutions aims at representing the constant input power that the system should have in order to detect easily the variation of the output power (revolutions-torque) when the external load varies. b) The pump (1) is a conventional type pump as is the hydraulic motor (2). The most common types of pumps used for high pressures in systems of bulk power transfer used to rotate hydraulic motors are the gear pumps, the rotary pumps with compartments and sliding vanes, the piston pumps with jyrating pistons (axial or radial) and the piston pumps with camshaft and valves like respectively the hydraulic motors.

The invention to be described can function in combination with any of the abovementioned pumps as well as with any hydraulic motor. In order though to understand the operation of the aforementioned systems, the pumps depicted are considered rotary pumps (of constant supply) with sliding vanes positioned on the perimeter of the rotor, which rotates in the interior of the stator. Consequently the hydraulic motors are of a respectively similar type.

Assembly of the system -A₁- in figure -1-. The electromotor (E) producing constant power is connected to the shaft-rotor (I_A) of the pump (1), which is connected to two circuits. The pump's output is connected to the circuit (N) that is separated into two paths (Ni) and (N₂) of hydraulic power supply and the input of the pump is connected to the circuit (R) resulting from the two paths (R₁) and (R₂) of fluid power return. The path (Ni) guides the hydraulic fluid towards the hydraulic motor (2) and rotates the rotor (3 _A) and the path (N₂) guides the hydraulic fluid towards the linear feedback distributor (12). The paths (R₁) and (R₂) guide the returning hydraulic power towards the pump intake (R). The rotor (3 _A) across its longitudinal shaft forms (as a basic structure element) a torque meter and consists in the balance spring (7), the ring (6) with the converging internal conical surface (V), the cylindrical roller bearings (K) that are partially immersed on the one hand into the channel (C) of the longitudinal shaft of the rotor (3 _A) and on the other hand into an equivalent channel, which is in the internal periphery of the gear ring (6) in order to transfer the torque of the rotor (3_A) also to the ring (6). It also consists of the ring (4) that comprises the rolling wheels (5) that, when the load is equal to the torque of the motor (E), then they touch the bottom of the internal conical surface (V). The ring (4) is based as well on the shaft of the rotor (3_A) as on the seat of the box (33). The torque meter is completed by positioning — incorporating the workhead (B) into the end of the rotor's (3A) shaft and via a line of ball bearings (S) a thrust bearing is formed for the variable axial thrusts that the ring (4) exerts (via the spring) on a part of the shaft —rotor (3A). In this way the rotor (3A) with its sub-groups is transformed to an elastic-solid transfer system and via the ring (4) it achieves real-time recognition of any external load variation. The number of the rolling wheels (5) belonging to the ring (4) and the number of the formed channels (C) existing in the perimeter of the shaft (3_A) is minimum 2 with diametrical isomeric arrangement. Always according to dimensioning, as much their arrangement as their numbering can vary.

The body of the ring (6) forms a body of double thrust bearing that receives the ball bearings (S) and the ring (8). The ring (8) projects the incorporated arm (8_A) on which the rod (9) is supported. At the other end of the rod, the spherical head (general description of the shape) or short the ball (10) is incorporated. The linear displacement of the ball (10) inside the conical cavity (11) creates a linearly variable cross-section, which allows the controlled flow of the hydraulic fluid and so a mechanism of linear feedback is created. Note: The spherical head (10) can have various shapes during the tests in the laboratory so that the feedback system produces the optimum results.

The operation principle of the system -A₁- in figure— 1-.

In order to understand the operation of the system in brief we shall consider that any supplied quantity of hydraulic fluid resulting from a complete rotation of the pump (1), leads to a complete rotation of the rotor (3 _A) of the hydraulic motor (2). This of course is true only when in the linear feedback system (12), the ball (10), which is positioned inside the conical cavity of the linearly variable cross-section (11), hinders the flow of the hydraulic power from the circuit (N₂) to the return circuit (R₂)- Thus, the resulting transfer ratio between the pump and the hydraulic motor in this case is 1:1 since the load is equal to the motor³ s (E) torque.

Considering that all aforementioned systems are proposed for use with variable load, then, in order to understand their operation, the following condition has to be taken into consideration: The torque of the motor (supplying the system with power) has to be greater (even if there is the smallest difference) than the torque of a load (in stable operation conditions) in any relational transfer ratio according to a predetermined variation scale.

In a mathematic model, there should be a symbolic difference foreseen even if it is in the range of 0,005 so that the torque of the motor has a positive sign (+) in order to ensure the stable operation of the motor if there is an increase (momentary or permanent) in the load. In the case though where the motor (E) produces maximum torque equal to the minimum torque of the load, then the abovementioned required difference (0,005) could result from a, foreseen by the manufacture, priority of fluid power flow through the feedback system and then the real transfer ratio between the motor and the minimum load will be 1 : 0,995 so that the motor is in superior position with reserved amount of torque equal to 0,005. Consequently, if the motor produces 10 Kgm torque at 1000 R.P.M., the minimum load (initial load) should be equal to 9,95 Kgm that will appear on the spring (7)- And while the abovementioned condition is been presented as an example for the systems - A₁ - B₁ - C₁ and - D₁ -, in order to understand easily the operation of these systems we shall accept that the torque of the minimum load will be considered equal to the maximum constant torque of the motor and consequently the transfer ratio between mem will be 1:1 for as long as the said minimum load remains constant. As we analyze the operation of the system - Ai₅ we see that during the time that the external load increases, the ring (4) gradually slows down and it acquires a relative velocity to the shaft-rotor (3A) and to the gear ring (6). The gear ring (6), via the internal conical surface (V), which transfers the torque of the motor via the rolling wheels (5) towards the ring (4), is subjected to axial displacement caused by the ring (4) through which also the rod (9) is displaced. The rod comprises the ball (10), which allows the start of the linear flow of the hydraulic liquid but mainly the linear displacement of the balance spring (7), whose axial force (due to spring arming) increases to become equal and opposite to the increasing load.

The feedback system as an adjusting device of angular velocities. During the time the load increases part of the fluid power starts to flow through the feedback system [and which in quantitative terms is extracted from the hydraulic motor (2)] and this is the reason why the angular rotational velocity of the rotor (3 A) changes in relation to the constant angular velocity of the rotor (I_A) of the pump (1). The reduction of the rotor 's (3 _A) number of revolutions has as a result the increase of its torque and this is the reason for the start of the spring (7) arming. Said spring starts to develop an axial force greater than the maximum nominal torque of 10 Kgm of the electromotor (E). After the load has been doubled the system enters a constant operation mode and the transfer ratio between the motor (E) and the output shaft (3) is 2:1, resulting from the torque meter via the feedback system. In this constant operation mode, the ball (10) that will have remained stationary at some point within the conical cavity (11) having variable cross-section, will have contributed to the existence of a certain free space needed for the constant flow of part of the fluid power.

Conclusion: The flow of a quantity of hydraulic power through the feedback system in order to change the output shaft's angular velocity, when this angular variation happens in relation to the load level, does not result to consumption of energy, because this "hydroplaning" is part of the internal torque of the system and consequently the loss of energy by the internal procedure of changes is equal to zero. The use of the torque meter of figure —2- by the system -Al -.

Every self-adjustable system put in motion by fluid power like e.g. by a pump and a hydraulic motor could also use an inclined plane torque meter resulting from the nut (15) via an endless screw like the torque meter of figure -2-. In this case the rotor has the indication (3B), while its longitudinal part forms an endless screw (14) cooperating with the nut (15).

Between the (incorporated into the rotor's shaft) cup (J) and the nut (15) the spring (7) touching the thrust bearings (-S- 13-) is clamped. The one part of the nut is threaded and the other forms a clutch, whereat, via the ball bearings (S) rolling in the channels (C), the torque is transferred also to the power output shaft (16). Any external load variation is transferred to the nut either via the spring (7) through the nut towards the shaft (16) or via the external (main) load through the shaft (16) towards the nut. This has as a result that every motion of the nut affects (through the arm - 8_B- and the rod —9-) directly the feedback system as also the torque meter of figure -1-. The difference of these two torque meters is that the meter of figure —1- can measure the load while the shaft rotates either clockwise or counterclockwise, while the torque meter of figure —2- can measure a load only in the rotation direction of the nut on its screw. Assembly of the system -Br in Figure —3-.

Because the motor (E), the pump (1), the hydraulic motor (2), the feedback system as well as the assembly of the hydraulic circuits is similar to the ones of system -Al-, the assembly of the system -Bl- will focus on the system of the mechanical torque meter (zero axial thrust) comprising the sensor shaft (19). The rotor (3 c) of the hydraulic motor (2) is incorporated into the cylindrical shaft (17) that rolls on the thrust bearings (33). The shaft (17) - depicted in cross-section - comprises the concentric cylinder (FC). In the interior of the cylinder there are the grooves arranged per 180°, while on its bottom the manufacture allows the mounting and the rolling of another shaft.

The other shaft (19) belongs to the system of the torque meter and comprises the balance spring (7). On the right and on the left of the spring the gear rings (18R-18L) with the flat guideways (W) are placed in a 180° arrangement. Said quideways can move on the shaft (19), since the shaft passes freely through them. Finally the shaft (19) comprises the heads (20_R-20_L) that are incorporated into it.

The sensor shaft (19) belonging to the torque meter enters the interior of the cylindrical shaft (17), since the flat guideways (W) belonging to the gear rings (18_R-18L) enter the respective channels (F) existing in the cylinder (FC) and the incoming end (19_L) of the shaft (19) is seated on the bearing (Q) at the bottom of the cylindrical shaft (17), while the other end of the shaft is seated on a part of the box (33 ).

Each gear ring with the indication (18_R) or (18_L) has a toroidal surface at its one side that forms two inclined curved surfaces (V) and each head (20_R) or (2O_L) has two projections. On each projection a rolling wheel (5) is based with freewheeling. The rolling wheels of each head (incorporated into the shaft) are adjacent to the conical surface at the point where the inclined surfaces (V) of each ring converge, while the gear ring (18R) is appropriately adjusted in order to form the pierced boss (H) that on the one hand is penetrated by the shaft (19) on which it is based and on the other hand the external diameter of the boss (H) is mounted to the ring (8) that is projected to the arm (8_A). At the end of the arm the rod (9) is incorporated that activates the feedback system (12).

The operation principle of the system -Bi- in Figure —3-.

As in the system -Ai-, also in the system -Bi-, when the load at the shaft (19) is equal to the torque of the motor (E), then every revolution of the rotor (1 _A) of the pump (1) causes a revolution of the rotor (3 c) of the hydraulic motor (2) and consequently of the power output shaft (19).

The cylindrical shaft (17), due to its incorporation into the rotor (3c), transfers the torque it receives to the gear rings (18_R-18_L) via the flat guideways (W) via the channels (F) (in the form of clutch). The gear rings via the surface (V), as they are adjacent to the rolling wheels (5) of the stable heads (20_R-20_L), tend to rotate (freely) around the shaft (19) on which they are based. Because though the axial force of the balance spring (7) is equal to the torque of the external load, the spring does not get further compressed and the torsional torque of the gear rings (via the resultant force resulting from the inclined surface) switches over (through the rolling wheels) to the incorporated heads (20_R-20_L) and rotates the shaft (19). When (via a brake PRONY) the load at the shaft (19) starts to increase, the said shaft will start to slow down and this results in the further compression of spring (7). At the start of this phase the following mechanical operations will take place:

In the first case an axial thrust will be exerted on the spring (7) simultaneously on both ends. This has as a result that, at the sensor shaft (19) of the torque meter (and power output), every tendency for axial thrust on both sides of its axial arrangement is eliminated via self-balancing. In the second case and during the start of the displacement of the gear ring (18_R), a cross-section starts to be formed linearly [and to expand by the displacement of the ball (10)]. Fluid power starts to flow from the said cross-section through the feedback system and it starts from the slowing down of the rotor's (3 c) revolution, but also from the upgrading of its torque.

Assembly of the system -C₁- in Figure —4-.

The system -Cr uses the torque meter of the system -B₁- but the power of the motor (E) is transferred via a Toothed Epicyclic Gear System (TEGS) (planetary gear mechanism). However, as far as the assembly of the torque meter is concerned, it is the same as in the system -Bi-.

The planetary gear is comprised of the planet carrier (21) that is the power input of the motor (E). The planet carrier comprises the spindles (22) whereat the planet gears (23) are seated — rolling, which are coupled on the one hand to the drum (24) and on the other to the toothed rotor-sun (25) that, via the link plate (25A), is incorporated into the cylindrical shaft (17) of the torque meter. At the same time, the external toothing of the drum (24) is permanently coupled to the toothed gear (26), which is also the power input shaft towards the pump (27) that can be either a gear pump or a rotary-vane type pump or a rotary-piston lobe type pump or any kid of pressure pump. The output circuit (28) of the pump is a closed type circuit (with one direction supply) and passes through its elongated casing (12) and forms a cavity (-11-1 IA-) with linear cross-section that is controlled by the rod (9) comprising the ball (10). The circuit returns to the pump in the form of the entry of its hydraulic fluid. Whatever is included in the casing (12_A) comprises the system of linear feedback that pilots the revolution rate or even the complete still standing of the pump (27).

Operation of the system -Ci- in Figure -4-.

The arrangement of the elements of the planetary system must be such that at each revolution of the motor (E) on the planet carrier (while the drum -24- is stationary) the shaft of the power output torque meter (19) (under minimum load) should perform a complete rotation so that the transfer ration should be 1 :1.

So, after random selection, the power outputs of the planetary gear system happened to be the on the one hand the rotor-sun (25) and on the other hand the drum (24) and the power is directed towards both outputs. Since the one of the two outputs has to function as a permanent power output, then the other output (drum) should be controllable. Ih the case of 1:1 transfer ratio, the pump doesn't rotate. This is due to the fact that since the supply - outlet (28) has a single direction and is interrupted (in a controlled way) by the feedback system, then the latter, via the pump (27) has a controlled braking effect on the drum (24) of the planetary system. When there is an increase in the load at the shaft (19) of the torque meter (its operation has been analyzed in the system -Bl-), then, via the arm (8c), the rod (9) will move linearly and the displacement of the ball (10) will contribute to the forming of a cross-section equivalent to the degree and the rate of the hydraulic fluid flow per time unit that will make the shaft of the pump (27) move at a determined revolution rate.

Due to the uninterrupted torque the drum (24) exerts on the gear of the pump, the degree of freedom resulting from the feedback system (whenever it happens), and which sets the drum at rotation rate, acts similar as if there is a change in the arrangement of the solid elements of the planetary system, since, via the change of the angular velocities, the sun's (25) rotation slows down, while at the same time it torque is upgraded. The system -Ci- with the torque meter of Figure -5-.

The toothed rotor-sun (25) of the planetary gear is incorporated via the plate (25 _A) into the cylindrical shaft (17A) of the torque meter, which has diametrically slots or channels (F). In addition, the sensor shaft (19_A), whereof one end is seated on the boss (Q) of the cylindrical shaft (17_A), comprises the screws (14_R -14_L) of left-hand and right-hand thread that cooperate with the respective nuts (15_R -15_L). Each nut is formed in a way as to receive a thrust bearing (S), whereat the freewheeling rings (13) that form a cup receive the balance spring (7_D). Either both or one end of said spring are/is incorporated into the arm (D), which can only slide on the shaft of the bar (L) being stabilized on the casing of the box (33) so that the spring does not rotate. The nut (15_R) comprises at its ends the flat guideways (W). One pair of the guideways enters into the slots (F) of the cylindrical shaft (17_A), while the other pair (W) enters into the slots (F) belonging to the nut (15_L) that also comprises the freewheeling ring (8). In this way, the nuts form a rotation coupling on the one hand with each other and on the other hand with the cylindrical shaft (17_A) in order to transfer the torque.

The kinematics of the torque meter with opposite facing screws during the operation of the system -C₁-.

When the cylindrical shaft (19_A) starts to slow down due to an increase in the external load, the existing torque of the system is transferred via the shaft (17_A) to the nut (15_R) and via the successive coupling (of the nuts) both nuts are set into rotation according to the direction of their convergence. During the time the nuts converge, the balance spring (7D) gets also compressed until its axial force is equal to the one of the external load's torque so that the spring should carry out only axial displacements without to rotate. The designing of this torque meter allows on the one hand to eliminate axial thrusts on the sensor shaft (19_A) and on the other hand, via the non-rotation of the spring during the rotation of the system, not to have radial tendencies during the rotation of the shaft. Said meter can cooperate also with the systems -Ai- and -Bi- via its incorporation into the respective rotor each time. Assembly and operation of the system -Ci- in figure -6-.

By replacing the pump (27) with the generator (M), whereof the rotor (26_A), via the toothed wheel, gets in permanent coupling to the drum (24) of the TEGS (planetary gear mechanism) and via the variable resistance — load (A), a feedback system through an electromagnetic field is formed. When the end of the rod (9κ), on which a pin (Z) is based, is in position -A-, then the total resistance (A) enters the closed circuit of the generator. And when the end of the rod is in position -B-, then, in the circuit of the generator practically the rotor of the generator faces the minimum resistance during its rotation. Basically, the generator during the variations of the torque meter according to the resistance does never produce electric load, because the input torque towards the generator (via the drum) is less than the torque the resistance provides (A) within the limits of electro-motion.

Assembly of the system -Di- in Figure -10-.

While this system retains the mechanisms and the basic operations of the systems -A_land -Bi-, however it uses as a torque meter the hydraulic type of figure —9-. Therefore the assembly of the said system will focus on the motor (2 A), whose rotor (3D) has a fluid- mechanic torque meter.

The shaft of the rotor (3D) is pierced and is penetrated by the power output sensor shaft (30). The shaft (30) belongs to the system of the torque meter and its left end (according to figure -10-) forms a body (31_B) of cylindrical shape that comprises (transversely across its center line) the pierced cylinder (36_A) in order to receive the pistons, while at its flat, external side it comprises the mounting boss (O).

The shaft-rotor (3_D) is incorporated into the casing (45) that (internally) forms on the one hand a cavity (44), whose side wall — bow (44_A) has elliptical shape and on the other hand a cylinder (40) that receives the piston (41_A). In the transverse cylinder (36_A) the pistons (35) are positioned that comprise the sealing rings (OR), while each piston comprises the rolling wheel (34) that rolls freely on a spindle mounted on the piston. The perimeter of the rolling wheels (34) is adjacent to the wall of the elliptical bow (44_A) of the cavity (44) that communicates with the cylinder (40) via the through-hole aperture (39). Across the center line passing through the center of the rotor (3D) and on the left side of the cylinder (40), the casing of the feedback system (12_B) is positioned and mounted without being adjacent to the front face of the cylinder (40).

The rod (9_E) comes out of the casing of the feedback system. The rod comprises at one end the ball (10) and at the other end the incorporated cylindrical disk (U) that receives the thrust bearing (S). Between the internal flat surface of the disk (U) and the casing (12_G), the balance spring (7_A) is positioned that activates the torque meter after the free space between the heads of the pistons (35) has been filled with hydraulic fluid (oil), which, via the pipe (39), communicates also with the space of the piston (41_A). Because the piston (41A) has to rotate together with the cylinder (40), the piston, via its incorporated into it projections (Y), is coupled to the channel - slot (F) that is on the body of the cylinder (40).

Operation principle of the system -Di- in Figure -10-.

As it is known from the systems -Ai-Bj-, when the total supplied fluid power (by the pump -1-) flows only through the hydraulic motor (2_A) and sets the rotor (3_D) into motion with a transfer ratio 1:1, then the load at the output shaft (30) is equal to the torque of the motor (E) and consequently the transfer ratio between the motor (E) and the output shaft is 1:1.

In case the load increases (and while the motor -E- does not supply more power), then the output shaft (30) will have to slow down as also the incorporated (into the shaft) cylinder (36_A). Taking into consideration the remark regarding the superior position of the motor's torque (page 4, paragraph 4), the rotor (3_D) with the casing (45), while it continues to move with a pace that slows down linearly, by its change of position and consequently by the ellipsoidal bow (44_A), causes the pistons (35) to be pushed further towards the interior of the cylinder (36_A) with pushing at the same time also the (rotating with its cylinder) piston (41_A), which, via the thrust bearing (S), pushes linearly the rod (9_E) and via the rod also the spring (7_A). This results in the respective degree of freedom so that fliud power can flow through the feedback system (10-1 I_A) that will determine the output torque of the C.V.T. in relation to the torque of the (external) load. Assembly and operation of the feedback system in Figure -11-

It consists of the casing (12_G) that comprises the input (N₂) of the fluid power that communicates with the cavity (11) having the linear cross-section (H A) and the output pipe (R₂)- At the right side (according to the figure) it is penetrated by the arm (9G) mat comprises the head (U), whose external side forms a mounting for a thrust bearing, while its internal surface is used for clamping the spring (7A). At the longitudinal part (G) of the arm, the spring (46), the ball (10_A), which can shift lengthwise, and the thermostatically controlled valve (T) are positioned, while all of them are held together by the sealing washer (47). The aim of this system is the automatic thermostatic adjustment — trimming regarding the correction of the latent in relation to the actual position the ball (10_A) should have on its mounting shaft with regard to the geometrical point of its equivalency to the linear cross-section (H_A) of the cavity (11) according to the temperature and the viscosity of the hydraulic fluid.

Because the temperature is the factor characterizing the thermal condition of a body and via the thermal condition its kinematic property, this is also the reason why the fluidity of a hydraulic fluid varies. Though, also the heat as a source of energy (on the basis of the law of thermodynamics) forces the drum of the thermostat to expand across its axis and to push the ball to a new position increasing also the axial force of the spring (46), whose aim is to push the ball reversibly during the contraction of the thermostat. In this way the degree of freedom resulting from the flow or not of the supplied fluid power and via the feedback system (since it is the actual mechanism for the determination of the angular velocities of C.V.T.) will approach the optimum transfer ratio that should prevail, since it will minimize the loss of energy during the operation of the system. The said feedback system (12G) can be applied as it is to the system -Dl- of figure —10-, while, if we remove the spring (7_A) and shape the end (U) of the rod (9_G) to a rod (9), it can be applied also to the systems -Ai- figure -1-, -Bi- figure -3- and -Ci- figure -A-.

Assembly of the feedback system with linear cross-section port in figure —12-.

The said feedback system consists of the piston (48) that is incorporated into the rod (9_P). Said piston comprises at its perimeter the transverse through-hole port (49), whose cross- section has a linear shape. The piston (48) cooperates with the cylinder (50). In the interior of the cylinder (and at a certain point of the bow of one of its side) there is the communication port (51) transversely located across the cylinder that has a parallelogramic shape or oilier shape (according to the desired result) as can be seen from the dashed line. When the piston enters the cylinder the two ports meet and, according to the meeting point, the revealed part (51_A) of the port (51) gets larger or smaller depending on the linear curve of the edge (X) of the port (49).

If then we define the moving port (49) as the input of the fluid power and the stable port (51) as the output of fluid power, then the flow rate will depend on the cross-section (51_A) that will vary according to the direction of the rod's (9_P) displacement.

Torque meter and feedback system

A transfer system with two independent power outputs is an indefinite system. If though, the two outputs are connected successively to each other to a real time torque meter that activates a feedback system (hydraulic or electromagnetic), then this system is transformed to a linear system, that is a C.V.T.

The gear cavities or the linear cross-section ports mentioned in the feedback systems can acquire an infinite number of shapes that are practically impossible to be noted down.

However, the feedback systems have a common denominator and consequently a single relational outcome resulting from the cooperation of determined mechanical parts either in relative to each other motion or in a stationary state always in relation to the operation condition of the C.V.T. In any operational position (between them) they might be, the fact is, that in order to be displaced to a new point, a necessary condition is the achievement of the linear variation of the fluid's flow cross-section. However, whatever the mechanical process of the motions might be, a hydraulic feedback system is characterized by its outcome and that is nothing else than to have a (fluid power) flow cross-section, linearly variable and either always coupled to a real time torque meter (if the intention is to apply the system in sectors like the wind energy, the automobiles sector or the shipbuilding) or formed by the displacement of the movable part of a feedback system via an electromechanical method (via an anemometer with rheostat) as an alternative solution only for wind energy in order to transform a power transfer system to a self-adjustable C.V.T.

Claims

CLAIMS Fluid-mechanic self-adjustable power transfer systems via linear feedback with, real time load torque meters comprising of hydraulic mechanisms as well as solid gear elements with the use of a planetary gear mechanism determined as CV. T. according to the systems - Ai - Bi - Ci - Di - that are characterized by the feet that the systems - Ai - Bi and Di - consist in the compression pump (1) with two direction (Ni - N₂) fluid power supply. Said pump is either a rotodynamic pump comprising of compartments and sliding vanes or a piston pump with rotating pistons (axial) or a radial-piston pump and generally any type of pressure pump, whose fluid power flows, via the closed-type circuit (N-Ni-Ri-R-N₂-R₂-R), through the respective (or any other kind) hydraulic motors (2) or (2_A) and rotates the rotors (3_A), (3_B), (3 c) or (3_D) that form alternative load torque meters, while the system - Ci — consists in the planetary mechanism of power input and said power flows through the gear elements like the planet carrier (21), the planets (23), the drum (24), while the mechanism's rotor - sun (25) is incorporated into the torque meter via opposite facing gear rings like these of system — Bi - and, if the variation system operates via fluid power like the one of system - Ai - comprising the hydraulic motor (2), then it is characterized by the fact that the longitudinal axial part of the rotor (3 _A) forms a torque meter of one-sided axial thrust consisting of the power output ring (4) that transfers the axial thrust to the workhead (B) via the bearing (S), said thrust energy derives from the balance spring (7), which exerts axial force on the (axially sliding) ring (6) and via the surface (V) and the rolling wheels (5), the torque is transferred also to the ring (4) deriving from the shaft of the rotor via the channels (C) and the cylindrical roller bearings (K). If the hydraulic motor of figure - Ai — comprises the rotor (3B), then it is characterized by the fact that its longitudinal axial part forms a torque meter with the use of the screw (14), the nut (15) and the spring (7) that exerts axial force on the nut while via the cylindrical roller bearings (K) and the cylindrical channel (C) it transfers the torque of the rotor (3_B) to the sensor shaft (16), while as far as the system — Bi - is concerned, whose motor (2) comprises the rotor (3 c), then it is characterized by the fact that the longitudinal part of the rotor forms a cylindrical shaft (17) that rolls on the bearings (33) and comprises the cylinder (FC) with the longitudinal grooves (F) that are entered by the flat guideways (W) belonging to the gear rings (18_L-18_R) that are based on the sensor shaft (19), whose one end (19_L) is based on the boss (Q) at the bottom of the cylindrical shaft (17) and the other end is based on a bearing of the box

(33) and it is characterized by the fact that the shaft (19) passes through the center of the through-hole aperture of the opposite facing gear rings (18L-18_R) between which the balance spring (7) is positioned, while on the external side of the rings the heads (2O_L - 20_R) are incorporated into the shaft (19), each head comprising a pair of rolling wheels (5) that are adjacent to the inclined curved surface (V) of the rings (18_L-18_R) and the ring (18_R) thereof forms a boss (H). As far as the system — Ci — is concerned, which can have a torque meter also with a screw, then it is characterized by the fact that the toothed rotor - sun (25) is incorporated into the cylindrical shaft (17A) comprising the slots (F) and the mounting boss (Q) on which the longitudinal part of the shaft (19_A) is based, which comprises the opposite facing screws (14_L-14_R) of left- hand and right-hand thread with the respective nuts (15_L - 15_R) between which the balance spring (7_D) is positioned, based on the thrust bearings (S) and it is characterized by the feet that the system -Dl- consists in the motor (2_A) that comprises the rotor (3_D), whose axial mounting part is pierced and through which the sensor shaft (30), seated on bearings (S), passes, whose one end forms a transverse pierced cylinder (36_A) on the carrier body (31_B) that ends in a pierced boss (O) based on a part of the casing (45) that is incorporated into the rotor (3_D) and forms a cavity

(44) with a side wall bow (44_A) that has elliptical shape and forms also a cylinder (40) that receives the piston (41_A) and it is characterized by the fact that inside the transverse cylinder (36_A) the opposite facing pistons (35) are positioned that comprise the rolling wheels (34), which are adjacent to the ellipsoidal surface (44A) and it is characterized by the feet that at the end of the shaft (30) there can be, instead of the transverse cylinder (36A), the elliptical lobe (31A) and the rotor (3D) can be incorporated into the casing (37) comprising the cylinders (36) instead into the casing

(45) and when the rotor (3_D) is incorporated into the casing (45) it comprises coaxially (rotating with the carrier body), and into the cylinder (40) with the piston (41_A), then it is characterized by the feet that between the piston and the rod (9_E) there is the bearing (S) and by the feet that between the moving rod (9_E) and the stable casing of the feedback system (12_B) or (12G), whose rod (9_G) comprises a thermostat, there is the balance spring (7_A) of the torque meter, while at the other end of the rod (9_E) there is the spherical (or of any other shape) head (10) inside the linear cavity (11-1 I_A), wherein the fluid power flows in from the circuit (N₂) and flows out from the circuit (R₂). If the hydraulic motor (2) comprises the rotor (3 A) or (3_B) like in the system - Al-, then it is characterized by the feet that the ring (6) or equivalently the nut (15) comprises the freewheeling ring (8) that ends in the arm (8_A) or (8_B) on which the rod (9) is incorporated that comprises the spherical (or of any other shape) head (10) inside the linear cavity (11-1 I_A) of the feedback system (12) that communicates with the fluid power input (N2) and output (R₂), while the torque meters of the systems - B₁ and Ci - comprising the opposite feeing gear rings (18_L -18_R), are then characterized by the feet that the gear ring (18_R) comprises the ring (18) on the boss (H) and the arm (8c) of the ring (18) comprises the rod (9) with the spherical (or of any other shape) head (10) inside the linear cavity (11-1 I_A) with an operational mode similar to that of the system -Al- and it is characterized by the fact that the feedback mechanism of system -Cl- is completed on the one hand by the pressure pump (27), whose power input shaft (26) is permanently coupled to the drum (24) and on the other hand by the closed type hydraulic circuit (28-29) of the pump controlled by the feedback system (12_A) and it is characterized by the fact that by the replacement of the pump (27) with the electromotor (M), whose rotor (26_A) is permanently coupled to the drum (24), while the resistance - load (A) is altered by the rod (9κ) via the pin (Z) through the torque meter, an alternative mechanism of linear feedback for the system -Cl- is completed and if all the power transfer systems comprise a feedback system with input-output ports, then it is characterized by the feet that the piston (48), which is incorporated into the rod (%) and comprises the through-hole port (49) with cross- section of linear shape, enters the interior of the cylinder (50) that comprises the communication port (51) and via the displacement of the rod (9_P) the area of the revealed cross-section (51A) increases and decreases alternately and it is characterized by the feet that the ports (49) and (51) can be formed also on flat, adjacent (via overlapping sliding) plates.

2. Fluid-mechanic self-adjustable power transfer systems via linear feedback with real time load torque meters consisting of hydraulic mechanisms where the systems -Ai - Bi - and - Di- thereof that consist in the compression pump (1) with constant volumetric two directional supply (Ni-N₂) and in hydraulic motors according to claim -1- are characterized by the fact that, via the controlled intervention (by a torque meter of any kind) through the feedback system (of any kind) in the circuit (N₂), the continually constant pump (1) supply passing through the abovementioned circuit is transformed (as far as the hydraulic motor is concerned) to linear variable supply with linear adjustment also regarding the output torque of the system.

3. Fluid-mechanic self-adjustable power transfer systems via linear, feedback with real time load torque meters consisting of hydraulic mechanisms where the system -Bi- thereof that consists in the compression pump (1) and the hydraulic motor (2) comprising the rotor (3 c), whose longitudinal axial part forms a cylindrical shaft (17) comprising the concentric cylinder (FC) with the longitudinal grooves (F) according to claim -1- is characterized by the fact that via the entering and the mounting on the boss (Q) of the one end (19L) of the sensor shaft (19) with the incorporated heads (2O_L - 2O_R) and the rolling wheels (5) that comprises the opposite facing gear rigs (18_L - 18_R) with the spring (7) positioned in-between and via the entering of the flat guideways (W) (belonging to the gear rings) into the grooves (F) a mechanical torque meter with axial thrust self-emulator is formed.

4. Fluid-mechanic self-adjustable power transfer systems via linear feedback with real time load torque meters consisting in compression pumps and hydraulic motors or also in gear elements where the system -Bi- thereof; whose motor (2) comprises the rotor (3c) that, via the cylindrical shaft (17) and the sensor shaft (19) forms a meter with axial thrust self-emulator according to claims —1- and -3- is characterized by the fact that via the incorporation of the toothed rotor (25) into the cylindrical shaft (17) with the carrier shaft (19) the system - Ci- is formed with power transfer through gear elements via a planetary mechanism, whose shaft of the rotor - sun (25) forms a torque meter with axial thrust self-emulator.

5. Fluid-mechanic self-adjustable power transfer systems via linear feedback with real time load torque meters consisting in compression pumps and hydraulic motors or also in gear elements with the use of a planetary mechanism like the system -Ci-, whose toothed rotor — sun (25) can comprise also an alternative torque meter with opposite facing screws according to claim -1-, which is characterized by the fact that the torque transfer from the cylindrical shaft (17_A) to the sensor shaft (19_A) is performed by the nut (15_R) comprising at its ends the flat guideways (W) whereof the one pair enters the slots (F) of the cylindrical shaft (17_A), while the other pair (W) enters the slots (F) belonging to the nut (15_L) comprising also the freewheeling ring

(8) and by the fact that the via the incorporation of the ends of the balance spring (7_D) into the arm (D) sliding on the bar (L) that allows only its axial displacement, a torque meter with axial thrust self-emulator without radial tendencies is formed.

6. Fluid-mechanic self-adjustable power transfer systems via linear feedback with real time load torque meters consisting in compression pumps and hydraulic motors where the system -Di- thereof, consisting of the motor (2A) that comprises the rotor (3p) and the feedback system (12_B) according to claim -1- is characterized by the fact that via the filling of the cylinder's (36_A) free space with hydraulic fluid and the on the spot rotation of the rotor (3_D) with the casing (45) around the slowing down (or stationary) transverse cylinder (36_A) that is a projection of the output shaft (30), a fluid pneumatic load torque meter is formed as, via the rotation of the ellipsoidal cavity (44) around the adjacent to it rolling wheels of the pistons (35), hydraulic pressure is exerted on the concentric piston (41A) and by the said piston, via a thrust bearing and the rod (9E), hydraulic pressure is exerted on the stably mounted balance spring (7_A), whose compression is interrupted when its degree of resistance is equalized with the external resistance - load at the shaft (30) and it is characterized by the fact that the rotational sequence of the piston (41_A) with regard to the rotating cylinder (40) is performed by clutch-type coupling through the projections (Y) of the piston that enter the longitudinal channels (F) of the cylinder.

7. Fluid-mechanic self-adjustable power transfer systems via linear feedback with real time load torque meters consisting in compression pumps and hydraulic motors where the system -Di- thereof, consisting of the motor (2_A) that comprises hydraulic load torque meter according to claims -1- and -5- is characterized by the fact that the spring (7A), as a basic part of the torque measurement system, is based on and clamped on the casing of the feedback system (12_B) and it activates the torque meter by reacting, via the rod (9E), to the thrust exerted on it by the piston (41_A) of the hydraulic torque measurement system.

8. Fluid-mechanic self-adjustable power transfer systems via linear feedback with real time load torque meters consisting of hydraulic mechanisms as well as solid gear elements with the use of a planetary mechanism as well as the use of various feedback systems according to claims -1 -, -5- and -6- are characterized by the feet that the feedback system (12Q) comprising the rod (9_G) that forms the part (G) whereat the thermostat (T), the spherical (or of other shape) head (10_A) as well as the spring (46) are mounted, while between the casing (12G) and the head (U) of the rod (9_G) the balance spring (7_A) is based and clamped, forms a feedback mechanism with automatic thermostatic adjustment proposed for the system -Di- and by the fact that via the appropriate configuration- removing the head (U) from the rod (9σ) as well as removing the spring (7_A) - it is proposed also for the systems -Ai- Bi- and -Ci-.