EP3173621A1 - Pump for supplying an application system of a liquid covering product - Google Patents

Pump for supplying an application system of a liquid covering product Download PDF

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Publication number
EP3173621A1
EP3173621A1 EP16200396.6A EP16200396A EP3173621A1 EP 3173621 A1 EP3173621 A1 EP 3173621A1 EP 16200396 A EP16200396 A EP 16200396A EP 3173621 A1 EP3173621 A1 EP 3173621A1
Authority
EP
European Patent Office
Prior art keywords
pistons
drum
cam profile
pump according
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16200396.6A
Other languages
German (de)
French (fr)
Other versions
EP3173621B1 (en
Inventor
Philippe De Talhouet
Romain Gaillet
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Exel Industries SA
Original Assignee
Exel Industries SA
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Filing date
Publication date
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Publication of EP3173621A1 publication Critical patent/EP3173621A1/en
Application granted granted Critical
Publication of EP3173621B1 publication Critical patent/EP3173621B1/en
Not-in-force legal-status Critical Current
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05C—APPARATUS FOR APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05C11/00—Component parts, details or accessories not specifically provided for in groups B05C1/00 - B05C9/00
    • B05C11/10—Storage, supply or control of liquid or other fluent material; Recovery of excess liquid or other fluent material
    • B05C11/1002—Means for controlling supply, i.e. flow or pressure, of liquid or other fluent material to the applying apparatus, e.g. valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/128—Driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/16—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0058—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0058—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control
    • F04B11/0066—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control with special shape of the actuating element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/146—Piston-rod guiding arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/047—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being pin-and-slot mechanisms

Definitions

  • the invention relates to a feed pump for a system for applying a liquid coating product.
  • the feed pumps for liquid coating product application systems such as paints, generally consist of an electric or pneumatic motor, a hydraulic pump and a coupling means connecting the motor to the pump .
  • Electrical pump a supply pump having an electric motor and pneumatic pump, a pump having a pneumatic motor.
  • Electric pumps are preferentially used because of their better performance and lower cost of use. The problem lies in the transformation of movement between the electric motor, which presents a rotary movement, and the hydraulic pump, which has a reciprocating linear movement. When reversing its direction of movement, the piston of the hydraulic pump reaches a zero speed which causes a drop in the pressure at the outlet of the pump. Electric pumps must therefore be provided to compensate for these inversions.
  • Pumps comprising a single piston actuated by a rod-crank system are known. In these pumps, the speed of rotation of the electric motor is controlled to obtain a constant flow. Pumps comprising a single piston actuated by a rack are known from US-2014/219819 . The inversions are operated on different teeth of the rack to reduce its wear. None of these systems makes it possible to avoid a pressure drop at the outlet of the pump.
  • the invention intends to remedy by proposing a new feed pump for a system for applying a coating product. liquid, allowing a more effective compensation of inversions of the pistons of the pump.
  • the invention relates to a feed pump of a system for applying a liquid coating product, comprising a motor actuating at least two pistons.
  • This pump is characterized in that it comprises a drum driven in rotation by the motor, the drum comprising an outer cylindrical surface having a cam profile, in that each of the pistons is integral with a rod on which is fixed a roller rolling on the cam profile such that the roller connected to each of the pistons via one of the rods is driven in translation along the axis of translation of the corresponding piston under the action of the rotation of the drum, in that each of the rollers is in contact with the cam profile at a position angularly offset from the position of the other rollers such that one of the pistons is in motion when another piston reaches an inversion point of its direction of movement. movement, and in that it comprises compensating means adapted to accelerate one of the pistons when another piston reaches a point of reversal of its direction of movement.
  • the acceleration of one of the pistons during the inversion of another piston allows effective compensation of the pressure drop.
  • the pressure obtained at the outlet of the pump is generally constant.
  • the Figures 1 to 5 represent a feed pump 1 of a system for applying a liquid coating product not shown.
  • the pump 1 comprises an electric motor 3 with a rotation axis X-X '.
  • the motor actuates two pistons 5 and 6 each mounted in a chamber 8 with the possibility of sliding along respective axes X5 and X6 parallel to the axis X-X '.
  • the displacement of the pistons 5 and 6 in the chambers 8 makes it possible to deliver a liquid coating product, such as a paint, under pressure.
  • the engine 3 actuates the pistons 5 and 6 by means of a transmission system comprising a drum 9 rotated by the engine 3 around the X-X 'axis. Transmission of the rotation of the motor 3 to the drum 9 can be direct or indirect, via a not shown multiplication system.
  • the drum 9 comprises an outer cylindrical surface 90 centered on the axis X-X '.
  • the outer surface 90 has a cam profile 92.
  • Each of the pistons 5 and 6 is respectively secured to a first rod 51 and a second rod 61 on which are fixed a first roller 53 and a second roller 63, each of the rollers 53 and 63 rolling on the cam profile 92 so that each of the rollers 53 and 63 linked to each of the pistons 5 and 6 via the rods 51 and 61 is driven in translation parallel to the axis XX 'under the action of the rotation of the drum 9.
  • the cam profile 92 is formed by a continuous groove comprising two helical grooves 94 and 95 each extending over one half of the circumference of the drum 9, and symmetrical with respect to a plane P1 passing through the rotation axis X-X '.
  • the grooves 94 and 95 each comprise a respective cylindrical bottom 94a and 95a, upper helical walls 94b and 95b and lower helical walls 94c and 95c.
  • the rollers 53 and 63 are selectively in contact with one of the upper helical walls 94b and 95b or lower 94c and 95c, along lines of contact perpendicular to the axis X-X '.
  • Each of the pistons 5 and 6 has a top dead center and a bottom dead point corresponding to the reversal points of its direction of movement in translation. During these inversions, the linear velocity of the pistons 5 and 6 decreases and then passes through a zero value, which induces a cut in the pressure at the outlet of the pump. It is therefore necessary to compensate for the slowing down of the speed of one of the pistons 5 and 6 when it reaches its inversion point by the movement of the other piston.
  • the point of contact of one of the rollers 53 and 63 with the cam profile 92 is at a position angularly offset relative to the position of the point of contact of the other roller in such a way that one of the pistons 5 and 6 is in motion when the other piston is at a point of reversal of its direction of movement.
  • the respective positioning of the rollers 53 and 63 allows that, as shown in FIG. figure 4 the roller 53 reaches its high inversion point while the roller 63 is approximately at halfway up its movement up. This partially compensates for the pressure drop due to the reversal of a piston.
  • the offset angle A of the rollers 53 and 63 is preferably between 70 ° and 100 °.
  • the offset angle A of the rollers is 90 °.
  • This angle A is also the angle formed by the axes X5 and X6 with respect to the axis X-X '.
  • the offset can not be 180 °, because the pistons 5 and 6 would reach their inversion point simultaneously and could not compensate each other.
  • the rollers 53 and 63 are offset by a quarter of a drum revolution 9, which implies that the roller 53 reaches the limit between the grooves 94 and 95 while the roller 63 reaches the central part of the groove 95, which corresponds to half the stroke of the piston 6.
  • the pump 1 comprises compensating means adapted to accelerate one of the pistons 5 and 6 while the other piston reaches its inversion point. .
  • the compensation means may comprise means for accelerating the rotational speed of the drum 9 formed by a control unit 10 shown diagrammatically in FIG. figure 1 , for a predetermined time before and after the passage of one of the pistons 5 and 6 at its inversion point.
  • a control unit 10 shown diagrammatically in FIG. figure 1
  • the speed of rotation of the drum 9 is accelerated by the control unit 10 so that the speed of translation of the piston Another piston is also accelerated, to allow the compensation of the slowing down of the first piston.
  • This method emerges from the curve represented on the figure 5 , which shows the evolution of the speed of rotation V of the drum 9 as a function of the angular position of the drum 9.
  • the speed profile is transmitted to the motor 3 by the control unit 10 in the form of an electrical signal S10 .
  • an inversion of a piston 5 or 6 takes place, which gives rise to compensation by increasing the speed V around this position angular.
  • the rotation speed of the drum 9 can be increased from 5 to 10 revolutions per minute.
  • the control unit 10 is preferably an electronic unit providing a slave control of the speed of rotation of the motor 3.
  • the angle interval before and after the passage of the piston at the point of inversion during which the speed of the drum 9 is increased can be between 0.14 and 0.28 radians.
  • a second embodiment of the invention is shown on the figure 6 .
  • the elements common to the first embodiment have the same references and function in the same way. Only the differences from the first mode are explained below.
  • the compensating means may comprise, in place of the means for accelerating the speed of rotation of the drum 9 or concomitantly, two angular sectors 97 of the cam profile 92 and whose angle of inclination A97, measured by relative to a plane P2 perpendicular to the axis of rotation X-X ', is greater than the angle of inclination A92, said nominal, of a remaining angular sector of the cam profile 92.
  • the remaining angular sector is defined as the portion of the cam profile 92 extending outside the angular sectors 97.
  • An angular sector 97 of steep inclination is provided on a central portion of each of the grooves 94 and 95.
  • the rollers 53 and 63 being offset by 90 °, the roller 53 reaches an inversion point, as can be seen on the left of the figure 6 , while the roller 63 is in contact with the angular sector 97, as can be seen on the right of the figure 6 .
  • the speed of translation along the axis XX 'of the roller 63 is increased by increasing the slope of the walls 94b, 95b, 94c and 95c.
  • the acceleration of the piston 6 integral with the roller 63 thus compensates for the slowing down and the zero-speed transition of the piston 5. This allows that reaching by one of the pistons 5 and 6 of its inversion point causes only one relatively small variation in the outlet pressure of the pump 1.
  • the value of the angle of inclination A97 is preferably twice the value of the angle of inclination A92.
  • the pump 1 may also comprise a pressure sensor 100 situated downstream of two hydraulic lines C1 and C2 for outputting the pistons 5 and 6, making it possible to measure the pressure at the outlet of the pump 1 and to measure the pressure drop following the approach of one of the pistons of an inversion point.
  • the pressure sensor 100 which is included in the compensation means, is connected to the control unit 10, or to any other means adapted to increase the speed of rotation of the drum 9 as a function of the pressure value, measured by the pressure sensor 10 and transmitted to the control unit 10 in the form an electrical signal SP.
  • the triggering of the acceleration of the drum speed 9 can be conditioned by the passage of the value of the outlet pressure below a threshold value, for example equal to 15 bars.
  • the pump 1 may comprise more than two pistons.

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

Abstract

Cette pompe (1) d'alimentation d'un système d'application d'un produit de revêtement liquide comprend un moteur (3) actionnant au moins deux pistons, un tambour (9) entrainé en rotation par le moteur (3), le tambour comprenant une surface cylindrique externe (90) présentant un profil de came (92), chacun des pistons étant solidaire d' une tige (51, 61) sur laquelle est fixée un galet (53, 63) roulant sur le profil de came (92) de telle manière que le galet lié à chacun des pistons via une des tiges est entraîné en translation selon l'axe (X-X') de translation du piston correspondant sous l'action de la rotation du tambour (9). Chacun des galets est en contact avec le profil de came à une position décalée angulairement par rapport à la position des autres galets de telle manière que l'un des pistons soit en cours de mouvement lorsqu'un autre piston atteint un point d'inversion de son sens de mouvement. La pompe comprend des moyens de compensation (10) adaptés pour accélérer l'un des pistons lorsqu'un autre piston atteint un point d'inversion de son sens de mouvement.This pump (1) for supplying a system for applying a liquid coating product comprises a motor (3) actuating at least two pistons, a drum (9) driven in rotation by the motor (3), the drum comprising an outer cylindrical surface (90) having a cam profile (92), each of the pistons being integral with a rod (51, 61) on which is fixed a roller (53, 63) rolling on the cam profile ( 92) such that the roller connected to each of the pistons via one of the rods is driven in translation along the axis (X-X ') of translation of the corresponding piston under the action of the rotation of the drum (9). Each of the rollers is in contact with the cam profile at a position angularly offset relative to the position of the other rollers such that one of the pistons is in motion when another piston reaches a reversal point. his sense of movement. The pump comprises compensating means (10) adapted to accelerate one of the pistons when another piston reaches a point of reversal of its direction of movement.

Description

L'invention concerne une pompe d'alimentation d'un système d'application d'un produit de revêtement liquide.The invention relates to a feed pump for a system for applying a liquid coating product.

Les pompes d'alimentation pour les systèmes d'application de produits de revêtement liquide comme les peintures, sont généralement constituées d'un moteur électrique ou pneumatique, d'une pompe hydraulique et d'un moyen d'accouplement reliant le moteur à la pompe. On appellera pompe électrique, une pompe d'alimentation présentant un moteur électrique et pompe pneumatique, une pompe présentant un moteur pneumatique. Les pompes électriques sont préférentiellement utilisées du fait de leur meilleur rendement et de leur coût d'utilisation moins élevé. La problématique réside dans la transformation de mouvement entre le moteur électrique, qui présente un mouvement rotatif, et la pompe hydraulique, qui présente un mouvement linéaire alternatif. Lors de l'inversion de son sens de mouvement, le piston de la pompe hydraulique atteint une vitesse nulle ce qui provoque une chute de la pression en sortie de la pompe. Les pompes électriques doivent donc être prévues pour compenser ces inversions.The feed pumps for liquid coating product application systems such as paints, generally consist of an electric or pneumatic motor, a hydraulic pump and a coupling means connecting the motor to the pump . Electrical pump, a supply pump having an electric motor and pneumatic pump, a pump having a pneumatic motor. Electric pumps are preferentially used because of their better performance and lower cost of use. The problem lies in the transformation of movement between the electric motor, which presents a rotary movement, and the hydraulic pump, which has a reciprocating linear movement. When reversing its direction of movement, the piston of the hydraulic pump reaches a zero speed which causes a drop in the pressure at the outlet of the pump. Electric pumps must therefore be provided to compensate for these inversions.

Des pompes comprenant un seul piston actionné par un système de bielle-manivelle sont connues. Dans ces pompes, la vitesse de rotation du moteur électrique est pilotée pour obtenir un débit constant. Des pompes comprenant un seul piston actionné par une crémaillère sont connues de US-A-2014/219819 . Les inversions sont opérées sur des dents différentes de la crémaillère pour réduire son usure. Aucun de ces systèmes ne permet d'éviter une chute de pression en sortie de la pompe.Pumps comprising a single piston actuated by a rod-crank system are known. In these pumps, the speed of rotation of the electric motor is controlled to obtain a constant flow. Pumps comprising a single piston actuated by a rack are known from US-2014/219819 . The inversions are operated on different teeth of the rack to reduce its wear. None of these systems makes it possible to avoid a pressure drop at the outlet of the pump.

Il est également connu d'utiliser une pompe à deux pistons diamétralement opposés, c'est-à-dire déphasés de Pi radians, dont les mouvements sont induits par la rotation d'une came coeur, dont le profil et le mécanisme lié sont adaptés pour que, lors de l'inversion du mouvement d'un des pistons, l'autre piston ne soit pas tout à fait en fin de course. Toutefois, un tel système n'est pas entièrement satisfaisant dans la mesure où il implique la variation continuelle du couple à fournir par le moteur. Par ailleurs, étant donné la conception de la came coeur connue, celle-ci ne présente qu'un moyen de poussée du piston de la pompe hydraulique, ainsi, pour réaliser la course du piston dans le sens inverse, il faut un mécanisme de rappel.It is also known to use a pump with two diametrically opposed pistons, that is to say out of phase with Pi radians, whose movements are induced by the rotation of a heart cam, whose profile and the linked mechanism are adapted so that, when reversing the movement of one of the pistons, the other piston is not quite at the end of the race. However, such a system is not entirely satisfactory insofar as it involves the continuous variation of the torque to be supplied by the motor. Moreover, given the design of the known core cam, it only has one means of thrusting the piston of the hydraulic pump, thus, to achieve the stroke of the piston in the opposite direction, a return mechanism is required .

C'est à ces inconvénients qu'entend remédier l'invention en proposant une nouvelle pompe d'alimentation d'un système d'application d'un produit de revêtement liquide, permettant une compensation plus efficace des inversions des pistons de la pompe.It is these drawbacks that the invention intends to remedy by proposing a new feed pump for a system for applying a coating product. liquid, allowing a more effective compensation of inversions of the pistons of the pump.

A cet effet, l'invention concerne une pompe d'alimentation d'un système d'application d'un produit de revêtement liquide, comprenant un moteur actionnant au moins deux pistons. Cette pompe est caractérisée en ce qu'elle comprend un tambour entrainé en rotation par le moteur, le tambour comprenant une surface cylindrique externe présentant un profil de came, en ce que chacun des pistons est solidaire d' une tige sur laquelle est fixée un galet roulant sur le profil de came de telle manière que le galet lié à chacun des pistons via une des tiges est entraîné en translation selon l'axe de translation du piston correspondant sous l'action de la rotation du tambour, en ce que chacun des galets est en contact avec le profil de came à une position décalée angulairement par rapport à la position des autres galets de telle manière que l'un des pistons soit en cours de mouvement lorsqu'un autre piston atteint un point d'inversion de son sens de mouvement, et en ce qu'elle comprend des moyens de compensation adaptés pour accélérer l'un des pistons lors qu'un autre piston atteint un point d'inversion de son sens de mouvement.To this end, the invention relates to a feed pump of a system for applying a liquid coating product, comprising a motor actuating at least two pistons. This pump is characterized in that it comprises a drum driven in rotation by the motor, the drum comprising an outer cylindrical surface having a cam profile, in that each of the pistons is integral with a rod on which is fixed a roller rolling on the cam profile such that the roller connected to each of the pistons via one of the rods is driven in translation along the axis of translation of the corresponding piston under the action of the rotation of the drum, in that each of the rollers is in contact with the cam profile at a position angularly offset from the position of the other rollers such that one of the pistons is in motion when another piston reaches an inversion point of its direction of movement. movement, and in that it comprises compensating means adapted to accelerate one of the pistons when another piston reaches a point of reversal of its direction of movement.

Grâce à l'invention, l'accélération de l'un des pistons pendant l'inversion d'un autre piston permet une compensation efficace de la chute de pression. La pression obtenue en sortie de la pompe est globalement constante.Thanks to the invention, the acceleration of one of the pistons during the inversion of another piston allows effective compensation of the pressure drop. The pressure obtained at the outlet of the pump is generally constant.

Selon des aspects avantageux mais non obligatoires de l'invention, une telle pompe peut incorporer une ou plusieurs des caractéristiques suivantes, prises selon toute combinaison techniquement admissible :

  • Les moyens de compensation comprennent des moyens d'accélération de la vitesse de rotation du tambour pendant une durée prédéterminée avant et après le passage d'un des pistons à son point d'inversion : dans ce mode de réalisation, au moment des inversions, la vitesse de rotation du moteur augmente tandis que le couple baisse, de telle sorte que la puissance demandée au moteur reste constante.
  • Les moyens d'accélération comprennent une unité de contrôle du moteur.
  • Les moyens de compensation comprennent un capteur de pression placé en aval des pistons, et les moyens d'accélération sont adaptés pour augmenter la vitesse de rotation du tambour en fonction d'une valeur de pression mesurée par le capteur de pression.
  • Les moyens de compensation sont formés par deux secteurs angulaires du profil de came ayant un angle d'inclinaison, par rapport à un plan perpendiculaire à l'axe de rotation du tambour, supérieur à un angle d'inclinaison d'un secteur angulaire restant du profil de came. Dans ce mode de réalisation, la compensation est réalisée en conservant une vitesse et un couple moteur constants.
  • L'angle d'inclinaison des secteurs angulaires du profil de came formant les moyens de compensation est le double de l'angle d'inclinaison du secteur angulaire restant du profil de came.
  • La pompe comprend deux pistons décalés angulairement de 90°.
  • Le profil de came comprend deux rainures hélicoïdales s'étendant chacune sur la moitié de la circonférence du tambour, et symétriques par rapport à un plan passant par l'axe de rotation du tambour.
  • Les galets sont décalés angulairement d'un angle compris entre 70° et 100°.
  • L'angle de décalage des galets est de 90°.
According to advantageous but non-compulsory aspects of the invention, such a pump may incorporate one or more of the following features, taken in any technically permissible combination:
  • The compensation means comprise means for accelerating the speed of rotation of the drum for a predetermined time before and after the passage of one of the pistons at its inversion point: in this embodiment, at the moment of the inversions, the motor rotation speed increases while the torque drops, so that the power demand of the motor remains constant.
  • The acceleration means comprise a motor control unit.
  • The compensation means comprise a pressure sensor placed downstream of the pistons, and the acceleration means are adapted to increase the speed of rotation of the drum as a function of a pressure value measured by the pressure sensor.
  • The compensation means are formed by two angular sectors of the cam profile having an inclination angle, with respect to a plane perpendicular to the axis of rotation of the drum, greater than an angle of inclination of a remaining angular sector of the drum. cam profile. In this embodiment, the compensation is performed while maintaining a constant speed and motor torque.
  • The angle of inclination of the angular sectors of the cam profile forming the compensation means is twice the angle of inclination of the remaining angular sector of the cam profile.
  • The pump comprises two pistons angularly offset by 90 °.
  • The cam profile comprises two helical grooves each extending over half the circumference of the drum, and symmetrical with respect to a plane passing through the axis of rotation of the drum.
  • The rollers are angularly offset by an angle between 70 ° and 100 °.
  • The offset angle of the rollers is 90 °.

L'invention sera mieux comprise et d'autres avantages de celle-ci apparaîtront plus clairement à la lumière de la description qui va suivre d'une pompe d'alimentation conforme à son principe, faite à titre d'exemple non limitatif en référence aux dessins annexés dans lesquels :

  • la figure 1 est une vue en perspective d'une pompe conforme à un premier mode de réalisation de l'invention,
  • la figure 2 est une vue à plus grande échelle du détail II à la figure 1,
  • la figure 3 est une vue de dessus de la pompe des figures 1 et 2,
  • la figure 4 est une coupe selon le plan IV-IV à la figure 3,
  • la figure 5 est une courbe de variation de la vitesse de rotation en fonction de la position angulaire d'un moteur de la pompe des figures 1 à 4;
  • la figure 6 est une vue similaire à la figure 4 et à plus grand échelle d'une pompe conforme à un second mode de réalisation de l'invention, sur laquelle uniquement un tambour et des galets de la pompe sont représentés,
  • la figure 7 est une vue similaire à la figure 1, d'une pompe conforme à un troisième mode de réalisation de l'invention.
The invention will be better understood and other advantages thereof will appear more clearly in the light of the following description of a feed pump according to its principle, given by way of non-limiting example with reference to drawings in which:
  • the figure 1 is a perspective view of a pump according to a first embodiment of the invention,
  • the figure 2 is a larger-scale view of detail II to the figure 1 ,
  • the figure 3 is a top view of the pump figures 1 and 2 ,
  • the figure 4 is a section on plane IV-IV at the figure 3 ,
  • the figure 5 is a curve of variation of the speed of rotation as a function of the angular position of a motor of the pump of Figures 1 to 4 ;
  • the figure 6 is a view similar to the figure 4 and on a larger scale a pump according to a second embodiment of the invention, in which only a drum and rollers of the pump are shown,
  • the figure 7 is a view similar to the figure 1 , a pump according to a third embodiment of the invention.

Les figures 1 à 5 représentent une pompe 1 d'alimentation d'un système d'application d'un produit de revêtement liquide non représenté. La pompe 1 comprend un moteur électrique 3 d'axe de rotation X-X'.The Figures 1 to 5 represent a feed pump 1 of a system for applying a liquid coating product not shown. The pump 1 comprises an electric motor 3 with a rotation axis X-X '.

Le moteur actionne deux pistons 5 et 6 montés chacun dans une chambre 8 avec possibilité de coulissement selon des axes respectifs X5 et X6 parallèles à l'axe X-X'. Le déplacement des pistons 5 et 6 dans les chambres 8 permet de délivrer un produit de revêtement liquide, tel qu'une peinture, sous pression.The motor actuates two pistons 5 and 6 each mounted in a chamber 8 with the possibility of sliding along respective axes X5 and X6 parallel to the axis X-X '. The displacement of the pistons 5 and 6 in the chambers 8 makes it possible to deliver a liquid coating product, such as a paint, under pressure.

Le moteur 3 actionne les pistons 5 et 6 par l'intermédiaire d'un système de transmission comprenant un tambour 9 entrainé en rotation par le moteur 3 autour de l'axe X-X'. La transmission de la rotation du moteur 3 au tambour 9 peut être directe ou bien indirecte, par l'intermédiaire d'un système de démultiplication non représenté.The engine 3 actuates the pistons 5 and 6 by means of a transmission system comprising a drum 9 rotated by the engine 3 around the X-X 'axis. Transmission of the rotation of the motor 3 to the drum 9 can be direct or indirect, via a not shown multiplication system.

Le tambour 9 comprend une surface cylindrique externe 90 centrée sur l'axe X-X'. La surface externe 90 présente un profil de came 92. Chacun des pistons 5 et 6 est respectivement solidaire d'une première tige 51 et d'une seconde tige 61 sur lesquelles sont fixés un premier galet 53 et un second galet 63, chacun des galets 53 et 63 roulant sur le profil de came 92 de telle manière que chacun des galets 53 et 63 lié à chacun des pistons 5 et 6 via les tiges 51 et 61 est entrainé en translation parallèlement à l'axe X-X' sous l'action de la rotation du tambour 9.The drum 9 comprises an outer cylindrical surface 90 centered on the axis X-X '. The outer surface 90 has a cam profile 92. Each of the pistons 5 and 6 is respectively secured to a first rod 51 and a second rod 61 on which are fixed a first roller 53 and a second roller 63, each of the rollers 53 and 63 rolling on the cam profile 92 so that each of the rollers 53 and 63 linked to each of the pistons 5 and 6 via the rods 51 and 61 is driven in translation parallel to the axis XX 'under the action of the rotation of the drum 9.

Dans l'exemple représenté, le profil de came 92 est formé par une rainure continue comprenant deux rainures hélicoïdales 94 et 95 s'étendant chacune sur une moitié de la circonférence du tambour 9, et symétriques par rapport à un plan P1 passant par l'axe de rotation X-X'. Les rainures 94 et 95 comprennent chacune un fond respectif 94a et 95a de forme cylindrique, des parois hélicoïdales supérieures 94b et 95b et des parois hélicoïdales inférieures 94c et 95c. Les galets 53 et 63 sont sélectivement en contact avec l'une des parois hélicoïdales supérieures 94b et 95b ou inférieures 94c et 95c, selon des lignes de contact perpendiculaires à l'axe X-X'.In the example shown, the cam profile 92 is formed by a continuous groove comprising two helical grooves 94 and 95 each extending over one half of the circumference of the drum 9, and symmetrical with respect to a plane P1 passing through the rotation axis X-X '. The grooves 94 and 95 each comprise a respective cylindrical bottom 94a and 95a, upper helical walls 94b and 95b and lower helical walls 94c and 95c. The rollers 53 and 63 are selectively in contact with one of the upper helical walls 94b and 95b or lower 94c and 95c, along lines of contact perpendicular to the axis X-X '.

Sur la figure 4, le moteur 3, le tambour 9 et les galets 53 et 63 apparaissent deux fois du fait de la géométrie du plan de coupe IV-IV.On the figure 4 the motor 3, the drum 9 and the rollers 53 and 63 appear twice because of the geometry of the section plane IV-IV.

Lorsque le tambour 9 tourne sur lui-même autour de l'axe X-X', le contact entre les parois hélicoïdales 94b, 95b, 94c, 95c et les galets 53 et 63 provoque la translation des tiges 51 et 61, qui est transmise aux pistons 5 et 6, ce qui permet d'obtenir alternativement l'aspiration du produit de revêtement puis son expulsion sous pression en sortie de la pompe 1.When the drum 9 rotates about itself about the axis X-X ', the contact between the helical walls 94b, 95b, 94c, 95c and the rollers 53 and 63 causes the translation of the rods 51 and 61, which is transmitted to the pistons 5 and 6, which allows to obtain alternately the suction of the coating product and its expulsion under pressure at the outlet of the pump 1.

Chacun des pistons 5 et 6 a un point mort haut et un point mort bas correspondant aux points d'inversion de son sens de mouvement en translation. Lors de ces inversions, la vitesse linéaire des pistons 5 et 6 diminue puis passe par une valeur nulle, ce qui induit une coupure de la pression en sortie de la pompe. Il est donc nécessaire de compenser le ralentissement de la vitesse de l'un des pistons 5 et 6 lorsqu'il atteint son point d'inversion par le mouvement de l'autre piston. Ainsi, conformément à l'invention, le point de contact d'un des galets 53 et 63 avec le profil de came 92 est à une position décalée angulairement par rapport à la position du point de contact de l'autre galet de telle manière que l'un des pistons 5 et 6 soit en cours de mouvement lorsque l'autre piston est à un point d'inversion de son sens de mouvement. Avantageusement, le positionnement respectif des galets 53 et 63 permet que, comme cela est représenté à la figure 4, le galet 53 atteigne son point d'inversion haut pendant que le galet 63 est approximativement à mi-course de son mouvement vers le haut. Cela permet de compenser partiellement la chute de pression due à l'inversion d'un piston.Each of the pistons 5 and 6 has a top dead center and a bottom dead point corresponding to the reversal points of its direction of movement in translation. During these inversions, the linear velocity of the pistons 5 and 6 decreases and then passes through a zero value, which induces a cut in the pressure at the outlet of the pump. It is therefore necessary to compensate for the slowing down of the speed of one of the pistons 5 and 6 when it reaches its inversion point by the movement of the other piston. Thus, according to the invention, the point of contact of one of the rollers 53 and 63 with the cam profile 92 is at a position angularly offset relative to the position of the point of contact of the other roller in such a way that one of the pistons 5 and 6 is in motion when the other piston is at a point of reversal of its direction of movement. Advantageously, the respective positioning of the rollers 53 and 63 allows that, as shown in FIG. figure 4 the roller 53 reaches its high inversion point while the roller 63 is approximately at halfway up its movement up. This partially compensates for the pressure drop due to the reversal of a piston.

L'angle A de décalage des galets 53 et 63 est préférentiellement compris entre 70° et 100°. De façon préférentielle, l'angle de décalage A des galets est de 90°. Cet angle A est également l'angle formé par les axes X5 et X6 par rapport à l'axe X-X'. Le décalage ne peut pas être de 180°, car les pistons 5 et 6 atteindraient leur point d'inversion simultanément et ne pourraient se compenser mutuellement.The offset angle A of the rollers 53 and 63 is preferably between 70 ° and 100 °. Preferably, the offset angle A of the rollers is 90 °. This angle A is also the angle formed by the axes X5 and X6 with respect to the axis X-X '. The offset can not be 180 °, because the pistons 5 and 6 would reach their inversion point simultaneously and could not compensate each other.

Ainsi, comme cela est représenté à la figure 3, les galets 53 et 63 sont décalés d'un quart de tour de tambour 9, ce qui implique que le galet 53 atteint la limite entre les rainures 94 et 95 pendant que le galet 63 atteint la partie centrale de la rainure 95, ce qui correspond à la moitié de la course du piston 6.Thus, as shown in figure 3 , the rollers 53 and 63 are offset by a quarter of a drum revolution 9, which implies that the roller 53 reaches the limit between the grooves 94 and 95 while the roller 63 reaches the central part of the groove 95, which corresponds to half the stroke of the piston 6.

Afin de compenser de façon plus efficace l'inversion des pistons, conformément à l'invention, la pompe 1 comprend des moyens de compensation adaptés pour accélérer l'un des pistons 5 et 6 pendant que l'autre piston atteint son point d'inversion.In order to more effectively compensate for the inversion of the pistons, according to the invention, the pump 1 comprises compensating means adapted to accelerate one of the pistons 5 and 6 while the other piston reaches its inversion point. .

Selon un premier mode de réalisation de l'invention, les moyens de compensation peuvent comprendre des moyens d'accélération de la vitesse de rotation du tambour 9 formés par une unité de contrôle 10 représentée schématiquement à la figure 1, pendant une durée prédéterminée avant et après le passage d'un des pistons 5 et 6 à son point d'inversion. Ainsi, pendant toute la période où l'un des pistons ralentit, passe par la vitesse nulle, puis à accélère de nouveau, la vitesse de rotation du tambour 9 est accélérée par l'unité de contrôle 10 afin que la vitesse de translation de l'autre piston soit également accélérée, afin de permettre la compensation du ralentissement du premier piston. Cette méthode ressort de la courbe représentée sur la figure 5, qui montre l'évolution de la vitesse de rotation V du tambour 9 en fonction de la position angulaire du tambour 9. Le profil de vitesse est transmis au moteur 3 par l'unité de contrôle 10 sous la forme d'un signal électrique S10. A chaque quart de tour du tambour 9, correspondant à une rotation de Pi/2 radians, une inversion d'un piston 5 ou 6 a lieu, ce qui donne lieu à une compensation par l'augmentation de la vitesse V autour de cette position angulaire.According to a first embodiment of the invention, the compensation means may comprise means for accelerating the rotational speed of the drum 9 formed by a control unit 10 shown diagrammatically in FIG. figure 1 , for a predetermined time before and after the passage of one of the pistons 5 and 6 at its inversion point. Thus, during the entire period when one of the pistons slows down, goes through the zero speed, then accelerates again, the speed of rotation of the drum 9 is accelerated by the control unit 10 so that the speed of translation of the piston Another piston is also accelerated, to allow the compensation of the slowing down of the first piston. This method emerges from the curve represented on the figure 5 , which shows the evolution of the speed of rotation V of the drum 9 as a function of the angular position of the drum 9. The speed profile is transmitted to the motor 3 by the control unit 10 in the form of an electrical signal S10 . At each quarter turn of the drum 9, corresponding to a rotation of Pi / 2 radians, an inversion of a piston 5 or 6 takes place, which gives rise to compensation by increasing the speed V around this position angular.

A titre d'exemple, la vitesse de rotation du tambour 9 peut être augmentée de 5 à 10 tours par minute.For example, the rotation speed of the drum 9 can be increased from 5 to 10 revolutions per minute.

L'unité de contrôle 10 est de préférence une unité électronique réalisant un contrôle asservi de la vitesse de rotation du moteur 3.The control unit 10 is preferably an electronic unit providing a slave control of the speed of rotation of the motor 3.

A titre d'exemple, l'intervalle d'angle avant et après le passage du piston au point d'inversion pendant lequel la vitesse du tambour 9 est augmentée peut être compris entre 0,14 et 0,28 radians.By way of example, the angle interval before and after the passage of the piston at the point of inversion during which the speed of the drum 9 is increased can be between 0.14 and 0.28 radians.

Un deuxième mode de réalisation de l'invention est représenté sur la figure 6. Dans ce mode de réalisation, les éléments communs au premier mode de réalisation portent les mêmes références et fonctionnent de la même manière. Seules les différences par rapport au premier mode sont exposées ci-après.A second embodiment of the invention is shown on the figure 6 . In this embodiment, the elements common to the first embodiment have the same references and function in the same way. Only the differences from the first mode are explained below.

Sur la figure 6, seul le tambour 9, dans ses deux positions de la coupe de la figure 4, et les galets 53 et 63 sont représentés dans un souci de clarté.On the figure 6 , only the drum 9, in its two positions of the section of the figure 4 and rollers 53 and 63 are shown for the sake of clarity.

Dans le mode de réalisation représenté sur la figure 6, les moyens de compensation peuvent comprendre, en remplacement des moyens d'accélération de la vitesse de rotation du tambour 9 ou bien de façon concomitante, deux secteurs angulaires 97 du profil de came 92 et dont l'angle d'inclinaison A97, mesuré par rapport à un plan P2 perpendiculaire à l'axe de rotation X-X', est supérieur à l'angle d'inclinaison A92, dit nominal, d'un secteur angulaire restant du profil de came 92. Le secteur angulaire restant est défini comme la partie du profil de came 92 s'étendant en dehors des secteurs angulaires 97. Un secteur angulaire 97 d'inclinaison accentuée est ménagé sur une partie centrale de chacune des rainures 94 et 95. Ainsi, les galets 53 et 63 étant décalés de 90°, le galet 53 atteint un point d'inversion, comme cela est visible sur la gauche de la figure 6, pendant que le galet 63 est en contact avec le secteur angulaire 97, comme cela est visible sur la droite de la figure 6. De cette façon, la vitesse de translation selon l'axe X-X' du galet 63 est donc augmentée grâce à l'augmentation de la pente des parois 94b, 95b, 94c et 95c. L'accélération du piston 6 solidaire du galet 63 compense donc le ralentissement et le passage à vitesse nulle du piston 5. Ceci permet que l'atteinte par l'un des pistons 5 et 6 de son point d'inversion ne provoque qu'une variation relativement faible de la pression de sortie de la pompe 1.In the embodiment shown on the figure 6 , the compensating means may comprise, in place of the means for accelerating the speed of rotation of the drum 9 or concomitantly, two angular sectors 97 of the cam profile 92 and whose angle of inclination A97, measured by relative to a plane P2 perpendicular to the axis of rotation X-X ', is greater than the angle of inclination A92, said nominal, of a remaining angular sector of the cam profile 92. The remaining angular sector is defined as the portion of the cam profile 92 extending outside the angular sectors 97. An angular sector 97 of steep inclination is provided on a central portion of each of the grooves 94 and 95. Thus, the rollers 53 and 63 being offset by 90 °, the roller 53 reaches an inversion point, as can be seen on the left of the figure 6 , while the roller 63 is in contact with the angular sector 97, as can be seen on the right of the figure 6 . In this way, the speed of translation along the axis XX 'of the roller 63 is increased by increasing the slope of the walls 94b, 95b, 94c and 95c. The acceleration of the piston 6 integral with the roller 63 thus compensates for the slowing down and the zero-speed transition of the piston 5. This allows that reaching by one of the pistons 5 and 6 of its inversion point causes only one relatively small variation in the outlet pressure of the pump 1.

Selon un aspect avantageux mais non obligatoire de l'invention, la valeur de l'angle d'inclinaison A97 est de préférence le double de la valeur de l'angle d'inclinaison A92.According to an advantageous but not compulsory aspect of the invention, the value of the angle of inclination A97 is preferably twice the value of the angle of inclination A92.

Il est évident que le positionnement du secteur angulaire 97 au centre des rainures 94 à 95 est lié à l'orientation à 90° des galets 53 et 63.It is obvious that the positioning of the angular sector 97 in the center of the grooves 94 to 95 is related to the 90 ° orientation of the rollers 53 and 63.

Selon un troisième mode de réalisation, la pompe 1 peut également comprendre un capteur de pression 100 situé en aval de deux conduites hydrauliques C1 et C2 de sortie des pistons 5 et 6, permettant de mesurer la pression en sortie de la pompe 1 et de mesurer la chute de pression consécutive à l'approche d'un des pistons d'un point d'inversion. Le capteur de pression 100, qui est compris dans les moyens de compensation, est relié à l'unité de contrôle 10, ou à tout autre moyen adapté pour augmenter la vitesse de rotation du tambour 9 en fonction de la valeur de pression, mesurée par le capteur de pression 10 et transmise à l'unité de contrôle 10 sous la forme d'un signal électrique SP. A cet effet, le déclenchement de l'accélération de la vitesse de tambour 9 peut être conditionné au passage de la valeur de la pression en sortie en dessous d'une valeur seuil, par exemple égale à 15 bars.According to a third embodiment, the pump 1 may also comprise a pressure sensor 100 situated downstream of two hydraulic lines C1 and C2 for outputting the pistons 5 and 6, making it possible to measure the pressure at the outlet of the pump 1 and to measure the pressure drop following the approach of one of the pistons of an inversion point. The pressure sensor 100, which is included in the compensation means, is connected to the control unit 10, or to any other means adapted to increase the speed of rotation of the drum 9 as a function of the pressure value, measured by the pressure sensor 10 and transmitted to the control unit 10 in the form an electrical signal SP. For this purpose, the triggering of the acceleration of the drum speed 9 can be conditioned by the passage of the value of the outlet pressure below a threshold value, for example equal to 15 bars.

Selon un mode de réalisation non représenté, la pompe 1 peut comprendre plus de deux pistons.According to an embodiment not shown, the pump 1 may comprise more than two pistons.

Les caractéristiques des modes de réalisation et variantes décrits ci-dessus peuvent être combinées pour former de nouveaux modes de réalisation de l'invention.The features of the embodiments and variants described above may be combined to form new embodiments of the invention.

Claims (10)

Pompe (1) d'alimentation d'un système d'application d'un produit de revêtement liquide, comprenant un moteur (3) actionnant au moins deux pistons (5, 6), caractérisée en ce qu'elle comprend un tambour (9) entrainé en rotation par le moteur (3), le tambour comprenant une surface cylindrique externe (90) présentant un profil de came (92), en ce que chacun des pistons est solidaire d' une tige (51, 61) sur laquelle est fixée un galet (53, 63) roulant sur le profil de came (92) de telle manière que le galet lié à chacun des pistons via une des tiges est entraîné en translation selon l'axe (X-X') de translation du piston (5, 6) correspondant sous l'action de la rotation du tambour (9), et en ce que chacun des galets est en contact avec le profil de came à une position décalée angulairement (A) par rapport à la position des autres galets de telle manière que l'un des pistons (6) soit en cours de mouvement lorsqu'un autre piston (5) atteint un point d'inversion de son sens de mouvement, et en ce qu'elle comprend des moyens de compensation (97 ; 10 ; 100) adaptés pour accélérer l'un des pistons (5, 6) lorsqu'un autre piston (5, 6) atteint un point d'inversion de son sens de mouvement.Pump (1) for supplying a system for applying a liquid coating product, comprising a motor (3) actuating at least two pistons (5, 6), characterized in that it comprises a drum (9 ) rotated by the motor (3), the drum comprising an outer cylindrical surface (90) having a cam profile (92), in that each of the pistons is integral with a rod (51, 61) on which is fixed a roller (53, 63) rolling on the cam profile (92) so that the roller connected to each of the pistons via one of the rods is driven in translation along the axis (X-X ') of translation of the piston (5, 6) corresponding under the action of the rotation of the drum (9), and in that each of the rollers is in contact with the cam profile at a position angularly offset (A) relative to the position of the other rollers in such a way that one of the pistons (6) is in motion when another piston (5) reaches a reversal point in its direction of movement. e movement, and that it comprises compensating means (97; 10; 100) adapted to accelerate one of the pistons (5, 6) when another piston (5, 6) reaches a point of reversal of its direction of movement. Pompe selon la revendication 1, caractérisée en ce que les moyens de compensation comprennent des moyens d'accélération (10) de la vitesse de rotation du tambour (9) pendant une durée prédéterminée avant et après le passage d'un des pistons (5, 6) à son point d'inversion.Pump according to Claim 1, characterized in that the compensating means comprise means (10) for accelerating the speed of rotation of the drum (9) during a predetermined time before and after the passage of one of the pistons (5, 6) at its point of inversion. Pompe selon la revendication 2, caractérisée en ce que les moyens d'accélération comprennent une unité de contrôle (10) du moteur (3).Pump according to claim 2, characterized in that the acceleration means comprise a control unit (10) of the motor (3). Pompe selon l'une des revendications 2 et 3, caractérisée en ce que les moyens de compensation comprennent un capteur de pression (100) placé en aval des pistons (5, 6), et en ce que les moyens d'accélération (10) sont adaptés pour augmenter la vitesse de rotation (V) du tambour (9) en fonction d'une valeur de pression (SP) mesurée par le capteur de pression (100).Pump according to one of claims 2 and 3, characterized in that the compensating means comprise a pressure sensor (100) placed downstream of the pistons (5, 6), and in that the acceleration means (10) are adapted to increase the rotational speed (V) of the drum (9) as a function of a pressure value (SP) measured by the pressure sensor (100). Pompe selon la revendication 1, caractérisée en ce que les moyens de compensation sont formés par deux secteurs angulaires (97) du profil de came (92) ayant un angle d'inclinaison (A97), par rapport à un plan (P2) perpendiculaire à l'axe de rotation (X-X') du tambour (9), supérieur à un angle d'inclinaison (A92) d'un secteur angulaire restant du profil de came (92).Pump according to Claim 1, characterized in that the compensating means are formed by two angular sectors (97) of the cam profile (92) having an angle of inclination (A97) with respect to a plane (P2) perpendicular to the axis of rotation (X-X ') of the drum (9), greater than an angle of inclination (A92) of a remaining angular sector of the cam profile (92). Pompe selon la revendication 5, caractérisée en ce que l'angle d'inclinaison (A97) des secteurs angulaires (97) du profil de came (92) formant les moyens de compensation est le double de l'angle d'inclinaison (A92) du secteur angulaire restant du profil de came (92).Pump according to claim 5, characterized in that the angle of inclination (A97) of the angular sectors (97) of the cam profile (92) forming the compensation means is twice the angle of inclination (A92) the remaining angular sector of the cam profile (92). Pompe selon l'une des revendications précédentes, caractérisée en ce qu'elle comprend deux pistons (5, 6) décalés angulairement de 90°.Pump according to one of the preceding claims, characterized in that it comprises two pistons (5, 6) angularly offset by 90 °. Pompe selon l'une des revendications précédentes, caractérisée en ce que le profil de came (92) comprend deux rainures hélicoïdales (94, 95) s'étendant chacune sur la moitié de la circonférence du tambour (9), et symétriques par rapport à un plan (P1) passant par l'axe de rotation (X-X') du tambour.Pump according to one of the preceding claims, characterized in that the cam profile (92) comprises two helical grooves (94, 95) each extending over half the circumference of the drum (9), and symmetrical with respect to a plane (P1) passing through the axis of rotation (X-X ') of the drum. Pompe selon l'une des revendications précédentes, caractérisée en ce que les galets (53, 63) sont décalés angulairement d'un angle (A) compris entre 70° et 100°.Pump according to one of the preceding claims, characterized in that the rollers (53, 63) are angularly offset by an angle (A) between 70 ° and 100 °. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'angle (A) de décalage des galets (53, 63) est de 90°.Pump according to one of the preceding claims, characterized in that the offset angle (A) of the rollers (53, 63) is 90 °.
EP16200396.6A 2015-11-25 2016-11-24 Pump for supplying an application system of a liquid covering product Not-in-force EP3173621B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1561346A FR3044052B1 (en) 2015-11-25 2015-11-25 PUMP FOR SUPPLYING A SYSTEM FOR APPLYING A LIQUID COATING PRODUCT

Publications (2)

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EP3173621A1 true EP3173621A1 (en) 2017-05-31
EP3173621B1 EP3173621B1 (en) 2019-03-06

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US (1) US20170146008A1 (en)
EP (1) EP3173621B1 (en)
JP (1) JP2017110638A (en)
KR (1) KR20170061090A (en)
CN (1) CN107051832B (en)
FR (1) FR3044052B1 (en)

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CN112879261A (en) * 2021-03-01 2021-06-01 胡兵 Concrete pump with ultrahigh lift
US20230106780A1 (en) * 2021-10-01 2023-04-06 Board Of Regents, The University Of Texas System Reciprocating Pump
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CN115013283A (en) * 2022-07-06 2022-09-06 浙江千机智能科技有限公司 Power plant

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Also Published As

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US20170146008A1 (en) 2017-05-25
CN107051832A (en) 2017-08-18
JP2017110638A (en) 2017-06-22
CN107051832B (en) 2021-03-12
EP3173621B1 (en) 2019-03-06
FR3044052A1 (en) 2017-05-26
KR20170061090A (en) 2017-06-02
FR3044052B1 (en) 2019-09-13

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