EP3023638B1 - Pumping unit for alimentary liquids - Google Patents
Pumping unit for alimentary liquids Download PDFInfo
- Publication number
- EP3023638B1 EP3023638B1 EP15003265.4A EP15003265A EP3023638B1 EP 3023638 B1 EP3023638 B1 EP 3023638B1 EP 15003265 A EP15003265 A EP 15003265A EP 3023638 B1 EP3023638 B1 EP 3023638B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pumping unit
- piston
- unit according
- electric motor
- valves
- 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.)
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Links
- 238000005086 pumping Methods 0.000 title claims description 47
- 239000007788 liquid Substances 0.000 title claims description 24
- 230000033001 locomotion Effects 0.000 claims description 29
- 230000009467 reduction Effects 0.000 claims description 10
- 230000002441 reversible effect Effects 0.000 claims description 7
- 235000013305 food Nutrition 0.000 claims description 6
- 239000000463 material Substances 0.000 claims description 6
- 230000003134 recirculating effect Effects 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 3
- 230000008901 benefit Effects 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000007726 management method Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 235000015203 fruit juice Nutrition 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000010985 leather Substances 0.000 description 1
- 238000004811 liquid chromatography Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000037452 priming Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 229920002994 synthetic fiber Polymers 0.000 description 1
- 235000018553 tannin Nutrition 0.000 description 1
- 229920001864 tannin Polymers 0.000 description 1
- 239000001648 tannin Substances 0.000 description 1
- 235000014101 wine Nutrition 0.000 description 1
Images
Classifications
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- 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
-
- 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
- F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
-
- 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
-
- 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
- F04B49/065—Control using electricity and making use of computers
-
- 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
- F04B53/10—Valves; Arrangement of valves
- F04B53/108—Valves characterised by the material
Definitions
- the present invention relates to a pumping unit for alimentary liquids, such as for example wines, musts, distilled products, food oils, fruit juices and pulps, and the like.
- single-cylinder or multiple-cylinder volumetric piston pumps are usually used to move alimentary liquids that do not withstand centrifugal motions and tend to emulsify or alter their physical state or their organoleptic characteristics as a consequence of those transfer operations that are not performed delicately.
- these pumps have one or more chambers that are alternately connected to a suction pipe and to a delivery pipe by means of valves of a different type depending on the liquid to be processed; a piston slides hermetically within each chamber.
- the actuation of the pistons is generally performed by link and rod systems or by crank and slotted link mechanisms which, despite being widely used, have some drawbacks that are not negligible and are substantially tied to the pulsed motion of the piston.
- the piston speed in fact varies for each stroke from a value equal to zero, when the piston is at one end of the chamber, to a maximum value when the piston is halfway along the stroke, and then the speed returns to zero at the end of the stroke.
- flywheel is usually actuated by means of chains of gears that transmit to the flywheel the torque generated by the motor.
- US6079797 discloses a dual action ball screw pump for a vehicular braking system.
- the pump body has an axial bore defining a travel chamber and a pressure chamber. An input port and an output port are formed in the pressure chamber.
- a ball screw is provided in the travel chamber.
- a piston is connected to the ball screw and slidably extends into the pressure chamber as the ball screw is rotated. The piston divides the pressure chamber into an input chamber having a maximum volume and an output chamber having a maximum volume which is less than the maximum of the input chamber.
- EP0309596 discloses a pumping apparatus for delivering liquid at a high pressure, for use in liquid chromatography.
- the pump has two pistons which reciprocate in two chambers.
- the output of the first pump chamber is connected via a valve to the input of the second pump chamber.
- the pistons are driven by ball-screw spindles.
- the stroke volume displaced by the piston is freely adjustable by corresponding control of the angle by which the shaft of the drive motor is rotated during a stroke cycle.
- the control circuitry is operative to reduce the stroke volume when the flow rate which can be selected by user at the user interface is reduced, thus leading to reduced pulsations in the outflow of the pumping apparatus.
- the aim of the invention is to solve the above described drawbacks, by providing a pumping unit, particularly for alimentary liquids, that is capable of providing a pumping action with flow-rates that are as constant as possible, without entailing the use of oil-pressure controlled systems or of kinematic chains formed by gears in an oil bath.
- a particular object of the invention is to provide a pumping unit that allows to maximize the flow-rate in the presence of an equal diameter of the piston and where said flow-rate can be modified simply and rapidly.
- Another object of the invention is to provide a pumping unit which, for an equal flow-rate, entails a lower number of piston strokes, and therefore of reverse motion, so as to minimize shocks and vibrations and to preserve at the best the organoleptic characteristics of the transferred product.
- Another object of the invention is to provide a pumping unit in which it is possible to predict accurately even from the beginning, the lifespan of the components used.
- a further object of the invention is to provide a pumping unit that avoids the use of the lubricating fluids or lubricants that are normally present in the reduction units that receive the link-and-rod or crank and slotted link systems, and in the pumps operated by oil-pressure controlled cylinders.
- these lubricants may leak and contaminate the place where the pumps are located, the pumps being usually located in environments for processing alimentary liquids.
- Another object of the invention is to provide a pumping unit that is capable of reducing the pulses caused by the alternating operation.
- Another object of the invention is to provide a pumping unit that has no flywheel mass, has a reduced weight and dimensions, and can be installed easily on a truck that can be towed or is self-propelled in order to facilitate its transfers.
- a pumping unit particularly for alimentary liquids, is designated generally by the reference numeral 1.
- the pumping unit 1 includes a base, not shown in the figures, which supports a volumetric pump 2 constituted by a body 3 that is preferably but not necessarily made of stainless steel, in which one or more chambers 4 are defined, also known as cylinders, inside which pistons 5, also known as plungers, hermetically slide.
- a volumetric pump 2 constituted by a body 3 that is preferably but not necessarily made of stainless steel, in which one or more chambers 4 are defined, also known as cylinders, inside which pistons 5, also known as plungers, hermetically slide.
- Figure 1 shows a volumetric pump 2 that comprises a single chamber 4 inside which a single double effect piston 5 slides; however, it is evident to the person skilled in the art that the pumping unit according to the present invention can also support pumps having a different number of pistons, or pumps in which the volume variation is given by the motion of elements of another type.
- the piston 5 comprises a disk-like body that supports on its edge one or more sealing rings 6 that are appropriately made of synthetic material and/or of natural leather treated with tannin.
- the piston 5 is connected to a stem 7 that protrudes from a wall of the body 3 and is able to slide hermetically.
- the chamber 4 is connected alternately to a suction pipe 8 and to a delivery pipe 9, which can be connected respectively to a container for liquid to be transferred and to a receiving container.
- connection of the chamber 4 to the pipes is adjusted by suction valves 10a and 10b and by delivery valves 11a and 11b, which cooperate respectively with seats 12a, 12b and 13a, 13b.
- suction valves 10a and 10b and the delivery valves 11a and 11b automatically open and close respectively upon the increase and decrease of the volume of the chamber 4.
- the suction valves 10a and 10b and the delivery valves 11a and 11b are gravity-actuated ball valves, per se already known, which substantially comprise a metallic core coated with a polymeric material that is suitable for food use.
- the suction valves 10a and 10b and the delivery valves 11a and 11b substantially comprise ground ball screws made of stainless steel.
- the pumping unit 1 is provided with an electromechanical device 14 that is preset to move the piston 5 according to an alternating rectilinear motion.
- the electromechanical device 14 includes a screw drive means 15 which is operatively connected to the piston 5 and is actuated by an electric motor means 16.
- the screw drive means 15 comprises a per se known recirculating ball screw, which is formed by a recirculating ball screw 17 and by a threaded shaft 18.
- the recirculating ball screw 17 is coupled to the free end of the stem 7, while the threaded shaft 18 is connected to the electric motor means 16 by means of a flexible coupling 19, with the possibility to turn in both directions of rotation.
- the electric motor means 16 is arranged substantially in axial alignment with the threaded shaft 18; however, this is merely an example.
- the electric motor means 16 can in fact be mounted in a different position with respect to the threaded shaft 18, using for example reduction units with parallel axes, perpendicular reduction units, or other adequate transmission systems.
- the stem 7 is provided with a longitudinal cavity 20 that is substantially cylindrical and is extended at its axis of symmetry.
- the longitudinal cavity 20 is conceived to receive part of the threaded shaft 18 during the alternating motion of the piston 5.
- the electric motor means 16 is constituted by a variable-speed electric motor, preferably a brushless motor with a low flywheel mass, the operation of which is controlled by an electronic control device 21 by means of which it is possible to set the operation of the pumping unit 1.
- the electronic control device 21 allows to keep the sliding speed of the piston 5 substantially constant.
- the electronic control device 21 allows to associate the time of reverse motion of the piston 5 with the opening/closing time of the suction valves 10a and 10b and of the delivery valves 11a and 11b.
- valves are gravity-actuated, for an equal weight of the balls that in practice constitute the valves, their opening/closing times can be longer or shorter depending on the higher or lower density of the transferred liquid.
- the electronic control device 21 therefore allows to synchronize the flow-rate gap caused by the pulsed motion of the piston 5 with the rising and falling times of said balls.
- a pulse reduction device is mounted on the pumping unit 1.
- the device is constituted by compensation chambers, which are per se known and are not shown in the figures and are arranged on the suction pipe 8 and on the delivery pipe 9.
- the compensation chambers are connected to a pair of piston air generators 22, which supply said chambers so that the volume of air sufficient to ensure their effectiveness is maintained inside them.
- the piston air generators 22 are constituted by single effect pneumatic cylinders with return spring and one-way valves, which are arranged on the outside, at the dead centers of the axial sliding of the stem 7.
- a pusher 23 of appropriate shape which is integral with the stem 7, which upon arriving at the braking steps compresses the air inside the cylinders.
- the entire pumping unit 1 can be mounted on a truck that can be towed or is self-propelled, not shown in the figures, so as to facilitate its transfers in the various regions of use.
- the electromechanical device 114 includes a slider 115 that slides with a rectilinear motion along a linear guide 116 and is fixed to the base that supports the volumetric pump 2 so as to be substantially aligned with the sliding direction of the piston 5.
- the slider 115 is connected kinematically to the stem 7 of the piston 5 and its motion along the linear guide 116 is actuated by a screw drive means 15 which is substantially equivalent to the one already described.
- electromechanical device 14 or 114 allows to guide in the best possible way the piston 5 in its linear alternating motion.
- the rotary motion imparted to the threaded shaft 18 by the electric motor means 16 in fact causes the recirculating ball screw 17 to reach alternately the two opposite ends of the threaded shaft 18.
- the piston 5 sucks the liquid from a part of the chamber 4 through the suction valve 10a, while the delivery valve 11a remains closed, and simultaneously compresses the liquid that is present in the opposite part of the chamber 4, sending it through the delivery valve 11b to the delivery pipe 9.
- volumetric pump 2 The operation of the volumetric pump 2 is different from that of a pump that is actuated in a traditional manner due to greater constancy in the sliding speed of the piston 5 and due to a significant reduction of reverse motion time.
- Reduction of reverse motion time is furthermore facilitated by the absence of flywheel mass and by the management of the electric motor means 16 that is performed by the electronic control device 21 which, as already highlighted previously, allows to synchronize the reverse motion time of the piston 5 with the opening/closing time of the suction valves 10a 10b and of the delivery valves 11a and 11b.
- Another advantageous characteristic of the present pumping unit is constituted by the fact that the electromechanical device 14 or 114 allows to use also pistons/chambers that have a longer stroke and a large bore.
- Another advantageous characteristic of the present pumping unit is constituted by the fact that the electromechanical device 14 or 114 allows to exert forces and strokes that are not available in traditional pumps which, subjected to intense operating pressures, are overloaded to the point of damaging the gears of the reduction unit and the systems for transferring rotary motion into linear motion.
- Another advantageous characteristic of the present pumping unit is constituted by the fact that the electromechanical device 14 or 114 lacks radio transmissions of motion, with consequent reduced wear of the rolling element; however, this does not hinder the possibility of different motion transmissions.
- the electromechanical device 14 or 114 has a very high efficiency, since it uses systems with rolling motions preferably along balls or rollers.
- the electromechanical device 14 or 114 by using preferably brushless motors with a low flywheel mass with electronic position and speed control, allows the present pumping unit to have a constant torque from zero to the maximum rotary speed of the threaded shaft 18, with the consequent possibility to vary the flow-rate of the volumetric pump 2 from zero to the maximum flow-rate at the maximum operating pressure.
- These electronic controls which are an integral part of the present pumping unit, furthermore allow to interface the machine with external electric/electronic control systems, for example for the supply of refrigeration and/or heating circuits.
- a further advantage of the invention resides in that the present pumping unit can be used as a dosage pump; by using an electronic management of the motion of the piston inside the chamber, it is in fact easy to program the exact quantity of cycles in order to dose or mix the transferred liquids in addition to being able to detect, with good approximation, the pumped quantity thereof and the actual partial and/or total operating times; therefore, it also acts as a litre-counter.
- Another advantage of the invention resides in the fact that the present pumping unit can be used to supply filtering systems requiring for example pumps with a small flow-rate with high pumping pressures and self-controlled constant pressures.
- Another advantage of the invention resides in that the motion of the piston is started according to a progressive acceleration ramp until the set speed is reached; this leads to a great advantage during the final filling of tanks and/or of other containers.
- starting process according to an acceleration ramp is advantageous also for the flexible hoses used for transfer.
- the pumping unit particularly for alimentary liquids, thus conceived is susceptible of numerous modifications and variations, all of which are within the scope of the inventive concept; all the details may furthermore be replaced with other technically equivalent elements.
- the materials used may be any according to the requirements and the state of the art.
Description
- The present invention relates to a pumping unit for alimentary liquids, such as for example wines, musts, distilled products, food oils, fruit juices and pulps, and the like.
- As is known, single-cylinder or multiple-cylinder volumetric piston pumps are usually used to move alimentary liquids that do not withstand centrifugal motions and tend to emulsify or alter their physical state or their organoleptic characteristics as a consequence of those transfer operations that are not performed delicately.
- More particularly, these pumps have one or more chambers that are alternately connected to a suction pipe and to a delivery pipe by means of valves of a different type depending on the liquid to be processed; a piston slides hermetically within each chamber.
- The actuation of the pistons is generally performed by link and rod systems or by crank and slotted link mechanisms which, despite being widely used, have some drawbacks that are not negligible and are substantially tied to the pulsed motion of the piston.
- The piston speed in fact varies for each stroke from a value equal to zero, when the piston is at one end of the chamber, to a maximum value when the piston is halfway along the stroke, and then the speed returns to zero at the end of the stroke.
- The frequent repetition of these working cycles, repetition that is necessary for pumps of the conventional type in order to provide the required flow rates, causes considerable turbulence, which tends to deteriorate the organoleptic characteristics of the transferred liquid, and strong stress on the delivery pipes due to hammer effects.
- In addition, one should consider that both in the case of link and rod systems and in the case of crank and slotted link mechanisms, the piston stroke and the flow-rate of the pumps are in practice conditioned by the diameter of the flywheel that actuates the system.
- Due to cost and easy handling reasons, the trend is to use flywheels with diameters that do not exceed certain limits and consequently the maximum flow-rates that can be obtained with pumps of the known type are generally relatively low, at least as regards single-cylinder pumps.
- It should also be considered that in the pumps currently in use the flywheel is usually actuated by means of chains of gears that transmit to the flywheel the torque generated by the motor.
- Consequently, the hydraulic power of known pumps and the maximum pressure of the transferred liquid are limited by the geometric characteristics of the gears and, in particular, by the geometric characteristics of the set of teeth.
- It is necessary to stress the fact that the gears contribute to increase the flywheel mass already present in known pumps, making any sudden stop even more difficult.
-
US6079797 discloses a dual action ball screw pump for a vehicular braking system. The pump body has an axial bore defining a travel chamber and a pressure chamber. An input port and an output port are formed in the pressure chamber. A ball screw is provided in the travel chamber. A piston is connected to the ball screw and slidably extends into the pressure chamber as the ball screw is rotated. The piston divides the pressure chamber into an input chamber having a maximum volume and an output chamber having a maximum volume which is less than the maximum of the input chamber. -
EP0309596 discloses a pumping apparatus for delivering liquid at a high pressure, for use in liquid chromatography. The pump has two pistons which reciprocate in two chambers. The output of the first pump chamber is connected via a valve to the input of the second pump chamber. The pistons are driven by ball-screw spindles. The stroke volume displaced by the piston is freely adjustable by corresponding control of the angle by which the shaft of the drive motor is rotated during a stroke cycle. The control circuitry is operative to reduce the stroke volume when the flow rate which can be selected by user at the user interface is reduced, thus leading to reduced pulsations in the outflow of the pumping apparatus. - The aim of the invention is to solve the above described drawbacks, by providing a pumping unit, particularly for alimentary liquids, that is capable of providing a pumping action with flow-rates that are as constant as possible, without entailing the use of oil-pressure controlled systems or of kinematic chains formed by gears in an oil bath.
- Within the scope of this aim, a particular object of the invention is to provide a pumping unit that allows to maximize the flow-rate in the presence of an equal diameter of the piston and where said flow-rate can be modified simply and rapidly.
- Another object of the invention is to provide a pumping unit which, for an equal flow-rate, entails a lower number of piston strokes, and therefore of reverse motion, so as to minimize shocks and vibrations and to preserve at the best the organoleptic characteristics of the transferred product.
- Another object of the invention is to provide a pumping unit in which it is possible to predict accurately even from the beginning, the lifespan of the components used.
- A further object of the invention is to provide a pumping unit that avoids the use of the lubricating fluids or lubricants that are normally present in the reduction units that receive the link-and-rod or crank and slotted link systems, and in the pumps operated by oil-pressure controlled cylinders.
- In case of failures or malfunctions, these lubricants, normally constituted by reduction unit oil or oil for oil-pressure controlled circuits, may leak and contaminate the place where the pumps are located, the pumps being usually located in environments for processing alimentary liquids.
- Another object of the invention is to provide a pumping unit that is capable of reducing the pulses caused by the alternating operation.
- Another object of the invention is to provide a pumping unit that has no flywheel mass, has a reduced weight and dimensions, and can be installed easily on a truck that can be towed or is self-propelled in order to facilitate its transfers.
- This aim, as well as these and other objects that will become better apparent hereinafter, are achieved by a pumping unit, particularly for alimentary liquids, as claimed in the appended claims.
- Further characteristics and advantages will become better apparent from the description of preferred but not exclusive embodiments of a pumping unit according to the invention, illustrated by way of non-limiting example in the accompanying drawings, wherein:
-
Figure 1 is a schematic view of a pumping unit; -
Figure 2 is a chart of the variations over time of the piston speed in a pump mounted on a pumping unit according to the invention and in a conventional pump; -
Figure 3 is a schematic view of a pumping unit according to the invention. - With reference to the cited
Figures 1 and2 , a pumping unit, particularly for alimentary liquids, is designated generally by thereference numeral 1. - The
pumping unit 1 includes a base, not shown in the figures, which supports a volumetric pump 2 constituted by abody 3 that is preferably but not necessarily made of stainless steel, in which one ormore chambers 4 are defined, also known as cylinders, inside whichpistons 5, also known as plungers, hermetically slide. -
Figure 1 shows a volumetric pump 2 that comprises asingle chamber 4 inside which a singledouble effect piston 5 slides; however, it is evident to the person skilled in the art that the pumping unit according to the present invention can also support pumps having a different number of pistons, or pumps in which the volume variation is given by the motion of elements of another type. - In the specific case, the
piston 5 comprises a disk-like body that supports on its edge one ormore sealing rings 6 that are appropriately made of synthetic material and/or of natural leather treated with tannin. - The
piston 5 is connected to a stem 7 that protrudes from a wall of thebody 3 and is able to slide hermetically. - The
chamber 4 is connected alternately to asuction pipe 8 and to a delivery pipe 9, which can be connected respectively to a container for liquid to be transferred and to a receiving container. - Conveniently, the connection of the
chamber 4 to the pipes is adjusted bysuction valves delivery valves seats - The
suction valves delivery valves chamber 4. - In the case being considered, the
suction valves delivery valves - According to a variation that is not shown in the accompanying figures and that is particularly adapted for the transfer of particularly dense liquids, the
suction valves delivery valves - In this case, the use of
appropriate seats - The above already known embodiments, in addition to minimizing the noise of the volumetric pump 2, allow to overcome any sealing problems of the valves caused by scoring or incisions that can be created by small foreign objects.
- According to the present invention, the
pumping unit 1 is provided with anelectromechanical device 14 that is preset to move thepiston 5 according to an alternating rectilinear motion. - According to a preferred embodiment, the
electromechanical device 14 includes a screw drive means 15 which is operatively connected to thepiston 5 and is actuated by an electric motor means 16. - In greater detail, the screw drive means 15 comprises a per se known recirculating ball screw, which is formed by a recirculating
ball screw 17 and by a threadedshaft 18. - The recirculating
ball screw 17 is coupled to the free end of the stem 7, while the threadedshaft 18 is connected to the electric motor means 16 by means of aflexible coupling 19, with the possibility to turn in both directions of rotation. - In the illustrated example, the electric motor means 16 is arranged substantially in axial alignment with the threaded
shaft 18; however, this is merely an example. - According to a constructive variation not shown in the figures, the electric motor means 16 can in fact be mounted in a different position with respect to the threaded
shaft 18, using for example reduction units with parallel axes, perpendicular reduction units, or other adequate transmission systems. - Advantageously, the stem 7 is provided with a
longitudinal cavity 20 that is substantially cylindrical and is extended at its axis of symmetry. - The
longitudinal cavity 20 is conceived to receive part of the threadedshaft 18 during the alternating motion of thepiston 5. - The electric motor means 16 is constituted by a variable-speed electric motor, preferably a brushless motor with a low flywheel mass, the operation of which is controlled by an
electronic control device 21 by means of which it is possible to set the operation of thepumping unit 1. - In particular, the
electronic control device 21 allows to keep the sliding speed of thepiston 5 substantially constant. - Furthermore, the
electronic control device 21 allows to associate the time of reverse motion of thepiston 5 with the opening/closing time of thesuction valves delivery valves - In this regard, it should be considered that since these valves are gravity-actuated, for an equal weight of the balls that in practice constitute the valves, their opening/closing times can be longer or shorter depending on the higher or lower density of the transferred liquid.
- From a practical point of view, the
electronic control device 21 therefore allows to synchronize the flow-rate gap caused by the pulsed motion of thepiston 5 with the rising and falling times of said balls. - Conveniently, in order to reduce the pulses induced by alternating operation, a pulse reduction device is mounted on the
pumping unit 1. - In greater detail, the device is constituted by compensation chambers, which are per se known and are not shown in the figures and are arranged on the
suction pipe 8 and on the delivery pipe 9. - Advantageously, the compensation chambers are connected to a pair of
piston air generators 22, which supply said chambers so that the volume of air sufficient to ensure their effectiveness is maintained inside them. - In the specific case, the
piston air generators 22 are constituted by single effect pneumatic cylinders with return spring and one-way valves, which are arranged on the outside, at the dead centers of the axial sliding of the stem 7. - The alternating actuation of the cylinders is performed by a
pusher 23 of appropriate shape, which is integral with the stem 7, which upon arriving at the braking steps compresses the air inside the cylinders. - In this manner, the air by passing through the pipes and the one-way valves, is sent to the inner part of each compensation chamber.
- After the mechanical compression of the stem of each pneumatic cylinder, the spring returns the stem to its maximum extension, ready for the next maneuver.
- Advantageously, the
entire pumping unit 1 can be mounted on a truck that can be towed or is self-propelled, not shown in the figures, so as to facilitate its transfers in the various regions of use. - In
Figure 3 , in which the pumping unit according to the invention is designated generally by thereference numeral 101, the alternating motion of thepiston 5 is performed by anelectromechanical device 114 that is substantially similar to the preceding one. - More particularly, the
electromechanical device 114 includes aslider 115 that slides with a rectilinear motion along alinear guide 116 and is fixed to the base that supports the volumetric pump 2 so as to be substantially aligned with the sliding direction of thepiston 5. - The
slider 115 is connected kinematically to the stem 7 of thepiston 5 and its motion along thelinear guide 116 is actuated by a screw drive means 15 which is substantially equivalent to the one already described. - As regards
Figure 3 , the elements that correspond to the elements that have already been described with reference toFigure 1 have been designated by the same reference numerals. - The operation of the pumping unit according to the present invention is evident from what has been described above.
- In particular it is evident that the
electromechanical device piston 5 in its linear alternating motion. - The rotary motion imparted to the threaded
shaft 18 by the electric motor means 16 in fact causes the recirculating ball screw 17 to reach alternately the two opposite ends of the threadedshaft 18. - This motion is transmitted, through the stem 7, to the
piston 5. - Whereas in the case of the
electromechanical device 14 motion transmission is direct, in the case of theelectromechanical device 114 it occurs by means of theslider 115 that follows the axial sliding of thepiston 5. - During the forward stroke, the
piston 5 sucks the liquid from a part of thechamber 4 through thesuction valve 10a, while thedelivery valve 11a remains closed, and simultaneously compresses the liquid that is present in the opposite part of thechamber 4, sending it through thedelivery valve 11b to the delivery pipe 9. - In the reverse stroke, i.e. during return, the liquid is sucked into a part of the
chamber 4 through thesuction valve 10b, while the liquid contained in the opposite part is sent through thedelivery valve 11a to the delivery pipe 9. - The operation of the volumetric pump 2 is different from that of a pump that is actuated in a traditional manner due to greater constancy in the sliding speed of the
piston 5 and due to a significant reduction of reverse motion time. - These peculiarities are clearly highlighted in the chart of
Figure 2 , in which the variations over time of the speed of thepiston 5, represented with asolid line 50, are compared with those of the piston of a traditional single-cylinder pump of the traditional type, shown in dashes 60. - Reduction of reverse motion time is furthermore facilitated by the absence of flywheel mass and by the management of the electric motor means 16 that is performed by the
electronic control device 21 which, as already highlighted previously, allows to synchronize the reverse motion time of thepiston 5 with the opening/closing time of thesuction valves 10adelivery valves - Another advantageous characteristic of the present pumping unit is constituted by the fact that the
electromechanical device - This allows to reduce the number of strokes per minute even to one quarter in the volumetric pump 2 with respect to a pump of the traditional type, with a consequent reduction of wear and more delicate transfer, to the full advantage of the organoleptic characteristics, which are better preserved, of the transferred product.
- Furthermore, the long stroke of the
piston 5, which by way of example is four times longer than that of conventional pumps, gives the volumetric pump 2 a very large liquid priming and vacuum capacity, greatly facilitating the suction of liquids even in underground tanks. - Another advantageous characteristic of the present pumping unit is constituted by the fact that the
electromechanical device - Another advantageous characteristic of the present pumping unit is constituted by the fact that the
electromechanical device - Moreover, it should be considered that the
electromechanical device - The
electromechanical device shaft 18, with the consequent possibility to vary the flow-rate of the volumetric pump 2 from zero to the maximum flow-rate at the maximum operating pressure. - These electronic controls, which are an integral part of the present pumping unit, furthermore allow to interface the machine with external electric/electronic control systems, for example for the supply of refrigeration and/or heating circuits.
- A further advantage of the invention resides in that the present pumping unit can be used as a dosage pump; by using an electronic management of the motion of the piston inside the chamber, it is in fact easy to program the exact quantity of cycles in order to dose or mix the transferred liquids in addition to being able to detect, with good approximation, the pumped quantity thereof and the actual partial and/or total operating times; therefore, it also acts as a litre-counter.
- Another advantage of the invention resides in the fact that the present pumping unit can be used to supply filtering systems requiring for example pumps with a small flow-rate with high pumping pressures and self-controlled constant pressures.
- Another advantage of the invention resides in that the motion of the piston is started according to a progressive acceleration ramp until the set speed is reached; this leads to a great advantage during the final filling of tanks and/or of other containers.
- Once the almost complete filling of the vessel has been reached, in order to complete total topping-up, the operator, after stopping the pump, must in fact restart it to complete the filling; the fact that the piston speed can vary without discontinuities between two limiting values evidently facilitates this operation, in particular with respect to pumps of the traditional type, which in general merely have the possibility to use two different operating speeds.
- Moreover, it should be considered that starting process according to an acceleration ramp is advantageous also for the flexible hoses used for transfer.
- It has been demonstrated, therefore, that the pumping unit, particularly for alimentary liquids, according to the invention, fully achieves the intended aim and objects.
- The pumping unit, particularly for alimentary liquids, thus conceived is susceptible of numerous modifications and variations, all of which are within the scope of the inventive concept; all the details may furthermore be replaced with other technically equivalent elements.
- In practice, the materials used, so long as they are compatible with the specific use, as well as the contingent shapes and dimensions, may be any according to the requirements and the state of the art.
Claims (9)
- A pumping unit for alimentary liquids, comprising a volumetric pump (2) provided with at least one chamber (4) inside which a piston (5) slides hermetically; said chamber (4) is connected alternately to a suction pipe (8) and to a delivery pipe (9) by means of automatic valves (10a, 10b, 11a, 11b); said pumping unit (1) further comprising an electromechanical device (114) for the alternating motion of said piston (5); said electromechanical device (114) being substantially constituted by a screw drive means (15) operatively connected to said piston (5) and actuated by an electric motor means (16); said pumping unit (1) being characterized in that said electromechanical device (114) comprises at least one slider (115) that can slide on at least one linear guide (116); said slider (115) being associated with said screw drive means (15) so as to interact with said piston (5).
- The pumping unit according to claim 1, characterized in that said screw drive means (15) comprises at least one recirculating ball screw (17) and a threaded shaft (18); said threaded shaft (18) being turned by said electric motor means (16); said recirculating ball screw (17) being associated with a stem (7) that is connected to said piston (5).
- The pumping unit according to claim 2, characterized in that said stem (7) comprises a substantially cylindrical longitudinal cavity (20) adapted to receive at least a portion of said threaded shaft (18), during the alternating motion of said piston (5).
- The pumping unit according to one or more of the preceding claims, characterized in that said electric motor means (16) comprises at least one variable-speed electric motor.
- The pumping unit according to one or more of the preceding claims, characterized in that said electric motor means (16) comprises an electronic control device (21) for controlling said electric motor.
- The pumping unit according to claim 5, characterized in that said electronic control device (21) comprises a system for synchronizing the reverse motion time of said piston (5) with the opening/closing time of said valves (10a, 10b, 11a, 11b).
- The pumping unit according to one or more of the preceding claims, characterized in that said valves (10a, 10b, 11a, 11b) are gravity-actuated ball valves constituted by a metallic core coated with polymeric material suitable for food use.
- The pumping unit according to one or more of the preceding claims, characterized in that the said sealing seats (12a, 12b, 13a, 13b) of said valves (10a, 10b, 11a, 11b) comprise a metallic core associated with the body (3) of said volumetric pump (2); said core being coated with polymeric material suitable for food use.
- The pumping unit according to one or more of the preceding claims, characterized in that it comprises a pulse reduction device which comprises at least one compensation chamber that can be connected to the delivery pipe (9), or the suction pipe (8), of said volumetric pump (2); said compensation chamber being fed by at least one piston air generator (22) that can be operated by the axial sliding of said stem (7) during the alternating motion of said piston (5).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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ITVI20140297 | 2014-11-17 |
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EP3023638B1 true EP3023638B1 (en) | 2020-01-22 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP15003265.4A Active EP3023638B1 (en) | 2014-11-17 | 2015-11-17 | Pumping unit for alimentary liquids |
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EP (1) | EP3023638B1 (en) |
ES (1) | ES2787176T3 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
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IT201700009231A1 (en) * | 2017-01-27 | 2018-07-27 | Alphasol S P A | High pressure volumetric dispenser for filling containers such as aerosol cans through aerosol valves, valves with bags called BOV (bag on valve), metering valves and similar with liquid and / or creamy products. |
CN106949032A (en) * | 2017-05-17 | 2017-07-14 | 广州市欧通机械有限公司 | A kind of special oil sanitation-grade high-pressure delivery pump |
CN107152387B (en) * | 2017-06-29 | 2020-05-19 | 中国工程物理研究院总体工程研究所 | Quantitative oil supply flow adjusting device for piston cooling nozzle performance experiment bench |
IT201800002800A1 (en) * | 2018-02-19 | 2019-08-19 | Ima Spa | VOLUMETRIC PUMP. |
US20220228485A1 (en) * | 2019-07-08 | 2022-07-21 | Halliburton Energy Services, Inc. | Direct drive for a reservoir fluid pump |
IT202000007915A1 (en) * | 2020-04-15 | 2021-10-15 | Cft Spa | SYSTEM FOR PUMPING FLUIDS CONTAINING SOLID PARTICLES |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB622649A (en) * | 1946-03-29 | 1949-05-05 | Self Priming Pump & Eng Co Ltd | A new or improved diaphragm pump |
CH447637A (en) * | 1964-09-18 | 1967-11-30 | Ceskoslovenska Akademie Ved | Device for precise dosing of liquids |
FR2525288B1 (en) * | 1982-04-19 | 1988-09-16 | Unima Anjou | DEVICE FOR CONTROLLING A RECIPROCATING PUMP, PARTICULARLY FOR A SPRAYER FOR AGRICULTURAL USE |
DE3785207T2 (en) * | 1987-09-26 | 1993-07-15 | Hewlett Packard Gmbh | PUMP DEVICE FOR DISPENSING LIQUID AT HIGH PRESSURE. |
US6079797A (en) * | 1996-08-16 | 2000-06-27 | Kelsey-Hayes Company | Dual action ball screw pump |
US9739272B2 (en) * | 2012-11-29 | 2017-08-22 | Fair Oaks Farms Brands, Llc | Liquid product dispensing system and method |
-
2015
- 2015-11-17 ES ES15003265T patent/ES2787176T3/en active Active
- 2015-11-17 EP EP15003265.4A patent/EP3023638B1/en active Active
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ES2787176T3 (en) | 2020-10-15 |
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