Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
  • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
  • F04C2/20—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

• the present invention relates to a rotary pump, the body of which delimits a closed cavity of generally oval-shaped general cross section, in which a vane rotor, coupled to a drive motor, is mounted to define there permanently, during its rotation, a suction zone and a discharge zone of variable volumes, isolated from one another and communicating respectively with a suction opening and a discharge opening.
• a vane rotor coupled to a drive motor
• this is provided with movable vanes which ensure the formation and sealing of the suction and discharge zones of variable volumes by being applied, with high friction, under the effect of centrifugal forces developed at high speeds, against the inner wall of the pump cavity, inside which said rotor occupies an eccentric position.
• a first drawback which results from this is that this wall and the ends of the vanes are subject to premature wear, considerably limiting the life of the pump.
• Centrifugal vane pumps are also commonly used in the wine industry to transport grapes from .25 harvest or storage tanks to winemaking facilities and, in this application, carry an additional disadvantage residing in the fact that the grapes are very often damaged by rolling or crushing at the points of tangency forming an acute angle between the rotor and the wall of the cavity of the pump, as well as between the vanes 30 which determine the mobile rooms of variable volumes, which hinders their use for example in certain winemaking methods which require whole grains.
• the present invention proposes to remedy all these drawbacks and, to do this, it relates to a rotary pump of the type specified in the preamble, which is characterized in that a cylindrical rotor is rotatably mounted around the axis of a main chamber concentric with said rotor, constituting a part of the cavity of the pump body, and carries fixed vanes distributed at equal angular intervals at the periphery of the rotor while being sized to come into constant contact with gentle friction with the wall of said chamber, while said cavity contains, opposite to said main chamber, a rotary valve which is oriented in the direc ⁇ tion of the axis of the main chamber by completely closing, in this position, the opening formed between the surface of the rotor and the portion of the.
• valve being able, under the action of actuating means acting in synchronism with the rotation of the rotor, to undergo a cyclic erasure movement allowing each time the passage of a pallet of the rotor while ensuring the maintenance of a soft friction contact between the valve and the latter.
• the pump according to the invention is not affected by the drawbacks of the conventional pumps mentioned above by the fact that the concentricity of the rotor and of the main chamber in which it is rotated, on the one hand removes any tangent point between these two organs, avoiding the rolling of the fruits conveyed, and on the other hand allows the chamber in which the fruits are conveyed inside the pump, and which has its walls constantly parallel to each other, does not vary in volume, thus avoiding any damaging compression of the grapes, the energy consumed by the mere setting in motion of the pump members being itself very low by the constancy of the sliding nature of the contact between the moving and stationary parts.
• the rotor vanes preferably extend entirely in planes passing through the axis of the latter, so that the vanes come, without dead angle, into contact with the peripheral wall of the main chamber, thus eliminating , in the case of a transfer of grapes through the pump of the invention, the risks of rolling or crushing of the grapes, this being also obtained by eliminating the eccentricity of the rotor relative to the main chamber , which created an acute angle at their point of tangency, where the grapes which were rolled there were coiled.
• the valve is mounted in rotation on the axis, parallel to that of the rotor, of the semi-cylindrical auxiliary chamber constituting a part of the cavity contiguous to the chamber.
• main and open on it and whose axis is located in the bisector plane of the angle formed by the suction and discharge ports is constituted by a shaft provided with fins of the same height, which extend over the entire length of said auxiliary chamber and are equal in number to twice that of the rotor vanes while being uniformly distributed around the circumference of the valve, these fins being successively joined by concave surfaces which are substantially hyperbolic and cover the entire length of the radius of the auxiliary chamber, which is equal to the distance separating the axis of the latter from the surface of the rotor, said means for actuating the valve being designed.
• the rotary valve of the pump according to the invention therefore guarantees well, at all times of the rotation of the rotor, a perfect seal at its contact with the latter. On the other side, the seal is obtained by the soft friction contact which the fins in rotation exert in rotation with the wall of the auxiliary chamber.
• the actuation means of the valve are consti ⁇ killed by the rotor drive motor and by a synchronization mechanism by means of which this motor is coupled to the valve shaft.
• a preferred mode of said synchronization mechanism comprises, outside the pump cavity, a first circular plate wedged on the rotor shaft and provided, in angular positions corresponding to those of the rotor vanes, with fingers drive cut according to the involute of a gear tooth, and a second plate which is wedged on the valve shaft and which is formed of branches positioned in correspondence with the fins of the latter while delimiting cutouts between them complementary to that of the drive fingers of the first plate, the second plate also being in sliding contact with the edge of the first, by the free outer edge of one of its branches.
• the free outer edges of the branches of the second plate respectively carry, at each of their ends, a loose roller in contact with the edge of the first plate and each of the drive fingers of the latter is bordered two substantially semi-circular notches intended to cooperate with the rollers during the rotation of the Maltese cross thus formed.
• the interior cavity of the pump has a longitudinal plane of symmetry on which the axes of rotation of the valve and of the rotor are located, the connection planes of the main chamber formed by a portion of cylinder with the semi-cylindrical auxiliary chamber, symmetrical with respect to the plane of the axes, conforming to a shape and an inclination capable of ensuring the best flow of the product both at suction and at delivery.
• the suction and discharge openings open on either side of this same plane of symmetry, in the space which communicates, over their entire length, the main and auxiliary chambers, and are extended externally by connection end pieces whose axes are preferably orthogaonal.
• the rotor of the pump according to the invention will preferably be provided with two diametrically opposite vanes and the valve will therefore comprise four vanes arranged in a cross, of which two will automatically close the semi-cylindrical chamber along its diametrical plane to thus advantageously delimit suction and discharge zones without blind spots, thus promoting the flow of the product to be pumped.
• FIGS. 1 and 2 are sectional views, taken along the line I-I of Figure 3, showing the pump respectively in the rest position and in the transfer position;
• FIG. 3 is an external side view of the pump of Figures 1 and 2;
• FIGS. 1 to 3 are views of the device for synchronizing the movements of the rotor and the rotary valve of this pump.
• the body 1 of the pump visible in FIGS. 1 to 3, delimits an interior cavity of cross section with a generally oval shape, which has a longitudinal plane of symmetry P and is closed laterally by plane end walls. , parallels 2 and 3.
• the internal cavity of the pump is more precisely formed of a main chamber 4 which develops in a form at least equal to an open hemi-cylinder and communicating with a smaller semi-cylindrical auxiliary shaft 5, whose axes X ,, X hail extend parallel to each other in the plane of symmetry P of the cavity.
• these two chambers 4, 5 communicate laterally, over the entire length of the cavity, by an intermediate space 39 into which open, on either side of the plane of symmetry P and flush with the diametrical planes of the chambers 4, 5, two suction ends 7 and discharge ends 8 intended to be connected by flanges 9, 10 to corresponding conduits.
• the active element of the pump according to the invention consists of a cylindrical rotor 11 with two fixed pallets 12, 13, keyed onto a shaft 14 which extends on the axis X_. of the large cylindrical chamber 4 concentric with said rotor, and supported in rotation by the two end walls 2, 3 of the casing, the shaft 14 extending beyond one of the latter to come to couple, by l '' through a speed reduction box 15, to a motor 16 or other rotary drive system (see figure
• the two paddles 12, 13 of the cylindrical rotor 11 are more precisely positioned in a diametral plane of the latter and are advantageously connected to its peripheral surface by rounded transition zones 17.
• the paddles 12, 13, which will be of preferably integrally with the rotor 11, have more than a sufficient height so that, during the rotation of the latter, their free end traverses with gentle friction the inner wall of the main chamber 4.
• the pallets 12, 13 like the rotor 11, also extend over the entire length of the pump cavity to come to apply gentle friction against the end walls 2, 3 of the latter.
• the rotor 11 of the pump according to the invention cooperates with a rotary valve 18, keyed onto a shaft 19 which extends on the axis X ⁇ of the auxiliary chamber 5 and is supported in rotation by the two end walls 2 , 3 from the pump body.
• the rotary valve 18, which also covers the entire length of the cavity until it comes into gentle friction contact with its end walls 2, 3, has in cross section the shape of a cross defined by four fins axial continuous 20a to 20d of the same height, which are distributed at angular intervals equal to 90 ° around the periphery of the valve 18 while being successively advantageously united by concave surfaces substantially hyperbolic, such as 21, which have a radius of curvature slightly less than the radius of the envelope circle of the pallets 12, 13 of the rotor 11.
• the height of the fins 20a to 20d of the valve 18, measured from the axis X tillof the auxiliary chamber, is also equal to the interior radius of this last, which corresponds to the distance separating the axis X "from the cylindrical surface of the rotor 11.
• the height of the central part of the valve 18, between the deepest point of each concave surface 21 and l axis X is equal to the distance between axes X. and X", minus the envelope radius of the pallets 12, 13 of the rotor 11.
• the shaft 19 of the valve 18 protrudes outside the body 1 of the pump, on the same side as the shaft 14 of the rotor 11, to which it is coupled by a synchronization mechanism housed in a casing 22 located between the box speed reduction 15 and the pump body 1.
• This synchronization mechanism comprises, as shown in this figure, a first circular plate 24 keyed to the shaft 14 of the rotor 11, this first plate 24 having on its edge two projecting fingers 25, 26 cut along the involute of a gear tooth and placed in diametrically opposite positions corresponding respectively to those of the two pallets 12, 13 on the rotor 11.
• the notches 27 and 28, substantially semicircular, are furthermore hollowed out in the edge of the plate 24, on both sides and d other of each of the fingers 25 and 26.
• the first plate 24 cooperates with a second plate 29 in the shape of a Maltese cross, wedged on the shaft 19 of the valve 18 and located, with the first plate, in the same plane orthogonal to this tree.
• the four trapezoidal branches 30 of this second plate 29 have their median axes placed in angular positions corresponding respectively to those of the fins 20a to 20d on the valve 18 and delimit between them identical cutouts 31 having a shape complementary to that of the fingers 25 and 26 of the first plate 24
• rollers 33 are mounted which, as can be seen in FIG. 4, are intended to roll on the edge of the first plate 24 when the branch corresponding 30 of the second plate is oriented in its direction.
• the vanes 12, 13 of the rotor 11 are both in contect with the wall of the main chamber 4 by closing the latter along its diamé ⁇ tral plane.
• Two of the fins 20b and 20d of the valve 18 close the auxiliary chamber 5 in the same way, while a third wing 20a of the valve is in contact with the cylindrical surface of the rotor 11.
• the rotor 11 and the valve 18 delimit, respectively in front of the end pieces 7 and 8, suction zones 34 and discharge zones 35, perfectly isolated from one another and practically devoid of blind spot, which will facilitate the flow of the grapes.
• the motor 16 being put into service, the rotor 11 turns in the direction of arrow A (FIG.
• the cyclic pivoting of the valve 18 takes place in the following manner.
• the circular plate 24- When approaching the end of this angular pivoting, the circular plate 24-collects, in the notch 28 located behind the finger 25, the front roller 33b of the next branch 30b of the second plate 29 and the latter switches back completely over the edge of the circular plate 24, on which it rolls by its two rollers 33b, 33c until that the second finger 26 of the plate 24 reaches, which causes a new pivoting of the valve 18 when approaching the second pallet 13 of the rotor 11.
• the rotor of the pump according to the invention can be provided with more than two vanes with a number each time of the fins on the valve.
• the pump according to the invention can be used to convey all types of easily damaged fruit as well as any other liquid or pasty material. It can also be used as a blower.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Rotary Pumps (AREA)

Applications Claiming Priority (2)

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ID=9338748

Family Applications (1)

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• 1986
  • 1986-09-01 FR FR8612522A patent/FR2603349B1/fr not_active Expired - Lifetime
• 1987
  • 1987-08-28 EP EP19870905624 patent/EP0321483A1/de not_active Withdrawn
  • 1987-08-28 WO PCT/FR1987/000336 patent/WO1988001694A1/fr not_active Ceased
  • 1987-09-01 GR GR871347A patent/GR871347B/el unknown
  • 1987-09-01 ES ES8702540A patent/ES2008198A6/es not_active Expired

Non-Patent Citations (1)

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