WO2023047002A1 - Pompe a pistons axiaux - Google Patents

Pompe a pistons axiaux Download PDF

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Publication number
WO2023047002A1
WO2023047002A1 PCT/ES2022/070364 ES2022070364W WO2023047002A1 WO 2023047002 A1 WO2023047002 A1 WO 2023047002A1 ES 2022070364 W ES2022070364 W ES 2022070364W WO 2023047002 A1 WO2023047002 A1 WO 2023047002A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
piston pump
axial piston
pistons
coupled
Prior art date
Application number
PCT/ES2022/070364
Other languages
English (en)
Spanish (es)
Inventor
Emiliano FERNÁNDEZ MORÁN
Original Assignee
Fernandez Moran Emiliano
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Fernandez Moran Emiliano filed Critical Fernandez Moran Emiliano
Priority to EP22741544.5A priority Critical patent/EP4407179B1/fr
Publication of WO2023047002A1 publication Critical patent/WO2023047002A1/fr

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Classifications

    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/101—Control of working-fluid admission or discharge peculiar thereto for machines with stationary cylinders
    • F01B3/102—Changing the piston stroke by changing the position of the swash plate
    • 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
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with stationary cylinders
    • F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0668—Swash or actuated plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control
    • F03C1/0694—Control by changing the inclination of the axis of the cylinder barrel in relation to the axis of the actuated 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
    • 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
    • F04B1/20—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 rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/328—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the axis of the cylinder barrel relative to the swash plate

Definitions

  • the present invention refers to an axial piston pump for the supply of a fluid, where the pump is volumetric with flow regulation and with regulation of the maximum pressure that it is capable of giving in the discharge at the pump outlet; and where the pump is applicable to fluids of chemical products, and also to oleo-hydraulic plants, without ruling out its application to other fluids.
  • the pump includes a characteristic adjustable movement transmission system through which it is possible to adjust the flow rate of the fluid at the pump outlet; where the fluid can be a liquid such as oleohydraulic oil, or a gaseous fluid.
  • pumps with several membranes or pistons are known, in which the flow rate or the pressure of the liquid fluid they supply is not mechanically adjustable (it could be electrically with a frequency regulator to the motor).
  • Radial piston and axial piston pumps are also known, where at least the latter have the drawback that it is not possible to regulate the flow of liquid fluid.
  • Single axial piston pumps have the drawbacks of delivering a pulsating flow of liquid fluid and very low efficiency.
  • Vane pumps and gear pumps are also known, where in both it is not possible to regulate the flow of liquid fluid that they provide.
  • oleo-hydraulic axial piston pumps can be swash-plate or bent-axis. They are multi-piston pumps that provide a flow of liquid fluid without pulsations, at the same time that they are adjustable in flow and pressure, but they are not volumetric, they do not work with anti-returns and, unlike the pump of the invention, the axial pistons, in addition to having a reciprocating movement (axial movement in both directions), they rotate as a grouped set like a revolver mechanism
  • Volumetric piston pumps are known (excluding oleohydraulic ones): on the one hand, single axial piston pumps with flow and pressure regulation; and on the other hand, axial piston steam pumps, but without mechanical regulation of flow and pressure.
  • an axial piston pump comprising a static head with parallel cavities in which the pistons are housed, which are configured to move axially in both directions within said cavities to supply a fluid flow at the outlet of said cavities that are distributed in a circumferential path.
  • the invention enables the multi-piston, volumetric and adjustable flow and pressure concepts to be fulfilled simultaneously for the first time.
  • the pump of the invention comprises an adjustable movement transmission system that includes at least a first turntable, a second turntable that can be tilted with respect to the first turntable, a third turntable, a mobile carriage with linear movement, and a support. of ball joints in which ends of the pistons are coupled by means of end heads with double joints.
  • Each double articulation of the end heads that link the pistons with the ball joint support comprises a ball joint coupled between pairs of wings that form part of the ball joint support by means of an axis, and an intermediate articulation that joins each end head to the piston. through another axis.
  • the third plate is coupled to the mobile carriage by means of an idle turning coupling.
  • RECTIFIED SHEET perpendicular to the linear displacement of the mobile carriage; where the first plate drags the second plate and the third plate in its turn; and where the first, second and third chainrings, as well as the mobile carriage, together with a tensioning device of the transmission system are located within a main casing, which may contain an oil bath for lubrication.
  • the second chainring is linked to the third chainring by means of a crank mechanism that articulates at a first end on the third chainring by means of a first articulated connection, while a second end of the crank mechanism, opposite the first end, articulates on the second chainring by a second hinged connection.
  • the first plate includes some curved-concave female front seats on which are supported, in addition, some curved-convex male front seats of the second inclinable plate; where the curvature of one and the other front seats are equidistant from a common center located inside the main casing and coinciding with the center of the crosshead on which the ball joint support also rotates.
  • the ball joint support is frontally supported on a second axial bearing coupled to an extension of the second plate; where said ball joint support adopts the inclination of said second plate at all times, without rotational movement of the ball joint support.
  • the adjustable movement transmission system is configured to be able to control the stroke of the pistons in order to control the flow rate of the fluid at the outlet of the cavities; where said variation is carried out by means of the linear displacement of the mobile carriage that modifies the inclination of the second plate and the ball joint support through the third plate and the crank mechanism.
  • the ball-and-socket support it articulates a crosshead mechanism that includes two pairs of axes; where a first pair of axes articulates in two aligned holes of two tabs attached to the ball joint support, while in the second pair of axes of the crosshead mechanism articulates the tensioning device that includes a longitudinal axis in parallel with the cavities in which they are guided and the axial pistons run; where the longitudinal axis is guided inside the head.
  • RECTIFIED SHEET (RULE 91)
  • the transmission of rotary movement to the first plate is carried out by means of a planetary reduction device that is coupled to a shaft connected to the first plate; where said planetary reducer receives the rotary movement from an output shaft of an external motor element.
  • the planetary reduction device comprises a fixed bracket with an internal ring gear and a rotating planetary assembly coupled to the internal ring gear.
  • Said planetary set includes a mobile support in the form of a cross and several radial pinions that rotate loosely coupled to said mobile support; and where said radial pinions mesh on the one hand with the internal toothed crown, and on the other hand mesh with a central pinion embedded in the output shaft of the motor element.
  • the mobile carriage includes threaded rods that are coupled to pinions that mesh with an external toothing of a toothed ring; where one of said pinions meshes with an intermediate pinion and this with a driving pinion attached to an axis to which a control wheel is attached, which is configured to carry out the movement of the mobile carriage in one direction or another, depending on the direction rotation of said control wheel.
  • a reduction gear may or may not be necessary to reduce the manual force required for actuation. All these toothed elements make up a regulating mechanism that is housed inside a front casing that is closed by a cover; where the front casing and the cover include centered and facing through holes.
  • the front casing includes an annular groove around its centered through hole where a first axial bearing sits frontally on which a part of the first plate is embedded with an interposition of an internal bearing fitted in one of the two races of said first axial bearing, while that another part of the first plate directly fits into the other even track of said first axial bearing.
  • the second plate comprises parallel walls that include the front male seats, while the first plate includes parallel holes into which the parallel walls of the second plate fit complementary; where some front bottoms of said parallel holes constitute the curved-concave female front seats; and where the two articulated connections of the crank mechanism are perpendicular to the planes in which the parallel walls of the crank are contained.
  • the second thrust bearing comprises two opposing races, one of which is fitted onto a second inner bearing and this is embedded in one part of the extension, while the other paired race of the second thrust bearing is directly embedded in another part of the extension.
  • extension abutting against a front seat of the second plate itself; where the ball joint support frontally rests on the coupled track on the second internal bearing.
  • Each of the cavities of the head ends in an outlet zone that includes a first passage and a second passage in which a first non-return valve and a second non-return valve have been inserted; where the first and second passages end separately in a first fluid outlet slot during its impulsion and in a second fluid inlet slot during its aspiration/suction to fill the cavities.
  • the main casing includes a side opening that is closed by a lid; where the main casing has two extreme bases in opposition: first and second.
  • the head is fixed outside the main casing and on the second base.
  • the entire adjustable movement transmission system is housed within the main casing, as well as the rest of the elements related to said transmission system.
  • the common center of the concave-curved male front seats of the second chainring and the convex-curved female front seats of the first chainring is located in the center of the crosshead mechanism.
  • the crosshead moves when the tensioning device is actuated, and reaches its final position in which its center is equidistant from the first male front seat and the second female front seat, once the tensioner device has been fully actuated.
  • the tensioning device comprises a support structure in which two parallel collateral wings are guided with curved recesses in which the crosshead mechanism articulates through its second axes.
  • the tensioning device also comprises a longitudinal axis attached to a central pinion that meshes with two lateral pinions coupled by threading on two immobilized screws parallel to the two collateral wings.
  • RECTIFIED SHEET (RULE 91) through the mediation of their heads; where said pinions are retained axially; and wherein the longitudinal axis includes a hexagonal end section for being able to comfortably rotate said longitudinal axis to axially adjust said tensioning device in order to axially adjust the assembly of the transmission system within the main casing.
  • the third plate comprises an external part formed by an annular body that is coupled punctually by tangential contact on some bearings of the mobile carriage with crazy rotation, and an internal part that includes a central structure with holes in which the first frontal fins of the first fit. dish.
  • the support structure of the tensioning device is bolted to an intermediate plate that forms part of the main casing, while it is located parallel to and close to the second end base.
  • annular body arranged around the support structure is fixed on said intermediate plate; where said annular body includes some quadrangular holes in which the pieces attached to the pistons fit and guide; where the section of said pieces is coincident with the section of passage of the quadrangular holes; all this to avoid the rotation of the pistons.
  • the pistons are guided and adjusted axially in holes located in a front plate that is screwed into a front area of the head opposite a rear area where the outlet of the cavities is located; where said holes serve as a guide for the pistons.
  • Inner bearings are to support radial loads or forces, while axial bearings are to support axial loads or forces. However, replacing each pair of axial and radial bearings, a single bearing could be mounted to support both loads. axial as radial loads.
  • the plate tilts but does not rotate and it is the pistons that rotate, while in the pump of the invention it is the other way around, that is, the pistons do not rotate and it is the inclined plate. the one that turns Unlike the swash-plate pump where the aspiration and discharge of the fluid is done by facing the
  • That the pump is volumetric, that is, that regardless of the pressure it has to overcome, it always pumps the same volume of fluid in each revolution.
  • That the parts of the pump in contact with the fluid are made of chemically resistant materials.
  • the pump of the invention perfectly meets these two conditions, which is why it is a dosing pump for chemical products.
  • the pump When the pump is applied to an olehydraulic power station, it is perfectly capable of giving high pressures, so it could also work as a pump in hydraulic circuits.
  • the head In this application of the invention, the head would be inside the main casing and the lubricating fluid would be the same as the driven fluid.
  • this gaseous fluid provided by the pump accumulates in a tank that forms part of a compressor, just like the pump itself.
  • the head would be inside the main casing.
  • the technical advantages of the pump of the invention with respect to single piston pumps are that it is much more efficient, that it gives a flow without pulsations, it has a much lower and constant decibel level, and it is mechanically balanced, that is to say, the inertial and centrifugal forces of the mobile elements are very low.
  • volumetric piston steam pumps has flow and pressure regulation
  • oil-hydraulic pumps is that it is volumetric
  • Figure 1. Shows an exploded perspective view of the axial piston pump, object of the invention.
  • Figure 2.- Shows an elevation view of the pump of the invention.
  • Figure 3. Shows a plan view of the pump of the invention.
  • Figure 4.- Shows a cross-sectional elevation view according to section A-A of Figure 3, where an adjustable movement transmission system is located in a position of low or no pump flow.
  • Figure 5.- Shows another plan view of the pump.
  • Figure 6. Shows another sectional elevation view according to section B-B of figure 5, where the transmission system is located in an active position in which the pump provides a high flow rate of fluid.
  • Figure 7.- Shows a sectional view according to section C-C indicated in figure 3.
  • Figure 8.- Shows a sectional view according to section D-D indicated in figure 3.
  • Figure 9.- Shows another plan view of the pump of the invention.
  • Figure 10. Shows a sectional profile view according to section F-F of figure 9.
  • Figure 11. Shows a sectioned profile view according to section G-G of figure 9.
  • Figure 12. Shows a sectioned profile view according to section H-H of figure 9.
  • Figure 13. Shows a sectioned profile view according to J-J section of figure 9.
  • Figure 14. Shows a perspective view of a tensioning device that forms part of the pump of the invention.
  • Figure 15.- Shows a perspective view of a third plate coupled with crazy rotation on a mobile carriage.
  • the axial piston pump for the supply of fluid comprises an adjustable movement transmission system that allows the fluid flow rate at the pump outlet to be varied; where by means of said transmission system the stroke of the pistons 3 that move axially within respective cavities 16 without rotational mobility can be varied; and where the variation of the fluid flow is carried out by means of the linear displacement of a mobile carriage 9 that can move in both directions of a direction parallel to the direction of the
  • the adjustable movement transmission system comprises a first turntable 15 associated with a second turntable 17 that can be tilted with respect to the first turntable 15, and a third intermediate turntable 11 that is also turnable; where the second plate 17 is linked to the third plate 11 by means of a crank mechanism 10, while the third plate 11 externally comprises an annular configuration and is coupled to the mobile carriage 9 by means of a loose rotation coupling.
  • the third plate 11, as shown more clearly in figure 15, comprises an outer part formed by an annular body 11a that is coupled punctually by tangential contact on several bearings 54 of the mobile carriage 9, and an internal part that comprises a structure central 11b with holes into which the first front wings 32 fit in parallel with the first plate 15, whose rotation drags both the second plate 17 and the third plate 11.
  • This third plate 11 includes two annular stops 45 in opposition that delimit the width of a circular surface of the annular body 11a of the third plate 11 in which the bearings 54 of the mobile carriage 9 fit, so that through said annular stops 45 the axial movement is and relatively the second plate 17 with respect to the first plate 15 when the mobile carriage 9 is displaced axially; where said displacement causes the variation of the inclination of the second plate 17.
  • crank mechanism 10 that links both plates 15 and 17, articulates at a first end in the third plate 11 through a first articulated connection 10a, while a second end of the crank mechanism 10, opposite the first end, articulates in the second. plate 17 by means of a second articulated connection 10b.
  • the mobile carriage 9 includes threaded rods 23 that are coupled to pinions 24 that mesh with an external toothing of a toothed ring 25; where one of said pinions 24 meshes with an intermediate pinion 26 and this with a drive pinion 27 attached to an axis to which a control wheel 28 is attached, through which the displacement of the mobile carriage 9 is carried out in one or the other direction, depending on the direction of rotation of said control wheel 28.
  • the front casing 21 includes an annular groove around its centered through hole where a first axial bearing 7 sits frontally on which a part of the first plate 15 is embedded with an interposition of an internal bearing 33 embedded in one of the two tracks of said first axial bearing 7, while in the other even track of said first axial bearing 7 another part of the first plate 15 fits directly.
  • the transmission of rotary movement to the first plate 15 is carried out by means of a planetary reduction device 1 that is connected on one side to an output shaft 12a of a motor 12 (it could be electric or of any other type, also hydraulic), and on the other side, said planetary reduction device 1 is connected to a shaft 14 connected to the first plate 15.
  • the planetary reduction device 1 comprises a fixed support 22 with an internal ring gear 22a and a planetary assembly 29 that rotates coupled to the internal ring gear 22a; where said planetary assembly 29 includes a cross-shaped mobile support 29a and several radial pinions 29b that rotate coupled to said mobile support 29a.
  • said radial pinions 29b mesh on the one hand with the internal toothed crown 22a, and on the other hand mesh with a central pinion 30 embedded in the output shaft 12a of the motor 12; where said central pinion 30 is also part of the planetary set 29.
  • the first plate 15 includes some curved-concave female front seats 15a in the manner of a cradle on which are complementary supported some curved-convex male front seats 17a of the second tilting plate 17; where the curvature of one and the other front seats are equidistant from a common geometric center 46 of a crosshead mechanism 4 that will be described later.
  • the linear displacement of carriage 9 drags
  • the first plate 15 includes a central extension 47 centered on which the first axial bearing 7 is mounted with interposition of the second internal bearing 33.
  • the second plate 17 comprises second front fins 31 in parallel that include the male front seats 17a that rest on the female front seats 15a that are located in the first front fins 32 of the first plate 15; where the two articulated connections 10a and 10b of the crank mechanism 10 are perpendicular to the planes in which the second front flaps 31 of the second plate 17 and the first front flaps 32 of the first plate 15 are contained.
  • the second plate 17 includes a centered extension 34 on which a second axial bearing 35 is mounted interposed by a second internal bearing 8, such that one of the tracks of said second axial bearing 35 is engaged on said second internal bearing 8 and this is embedded in one part of the extension 34, while the other even track of the second axial bearing 35 is embedded directly in another part of the extension 34 abutting against a front seat of the second plate 17 itself.
  • a ball joint support 5 which includes, on its second front face (opposite to the first front face) pairs of fins 5a distributed in a circumferential contour, in such a way that in said pairs of fins 5a are coupled end heads 3a with double articulation that connect with the axial pistons 3.
  • Each double articulation of the end heads 3a linking the pistons 3 with the ball joint support 5 comprises a ball joint 36 coupled between pairs of wings 5a that form part of the ball joint support 5; and an intermediate articulation 43 that joins each end head 3a to the piston 3; where thanks to this intermediate articulation 43 the piston 3 can rotate with respect to the respective end head 3a.
  • the ball joints 36 are coupled to the pairs of wings 5a via shafts.
  • a part 44 is attached to the piston 3, to which the end head 3a is in turn attached by means of the intermediate articulation 43 that includes an axis.
  • Said part 44 is the one that allows the ball joint 36 to go up and down, but that the piston 3 is not affected, that is to say, that this part 44 is totally guided and only has one degree of freedom, being able to move only axially accompanying the piston 3.
  • the crosshead mechanism 4 that includes two pairs of axes; where a first pair of axes 4a articulates in two aligned holes of two tabs 5b attached to the ball joint support 5, while in the second pair of axes 4b of the crosshead mechanism 4 articulates a tensing device 13.
  • the tensioning device 13 comprises a support structure 48 in which two mobile collateral wings 48a are guided in parallel with curved recesses 49 into which the crosshead mechanism 4 fits/articulates through its second axes 4b.
  • the tensioning device 13 also comprises a longitudinal axis 50 attached to a central pinion 51 that meshes with two lateral pinions 52 attached to two coaxial nuts coupled to two screws 53 immobilized parallel to the two collateral wings 48a by means of their heads; where said pinions 51, 52 are axially retained to the support structure 48.
  • the longitudinal axis 50 includes a hexagonal end section 50a to be able to comfortably rotate said longitudinal axis 50 to axially adjust said tensioning device 13 in order to axially adjust the assembly system as a whole. transmission inside a prismatic main casing 19, so that during the rotation of said longitudinal axis 50 the two collateral wings 48a move axially backwards or forwards.
  • the support structure 48 is bolted to an intermediate plate 55 that forms part of the main casing 14, while being located parallel to and close to the second end base 19b.
  • annular body 56 On said intermediate plate 55 there is also fixed an annular body 56 arranged around the support structure 48; where said annular body 56 includes some quadrangular holes 56a in which the pieces 44 attached to the pistons 3 fit and guide in order to prevent them from turning. Obviously the section of said pieces 44 is
  • An end part of the longitudinal axis 50 in which the hexagonal end section 50a is located is located in a recess inside the head 2.
  • the pump of the invention further includes the main casing 19 with a side opening that is closed by a cover 18, such that the main casing 19 has two opposing end bases: first 19a and second 19b.
  • the motor 12 On the outside of the main casing 19, the motor 12 is fixed on its first base 19a by means of some first screws 38 and nuts not shown in the figures, while on the second base 19b and also on the outside of the casing 12, a head is fixed. 2 by means of second screws 39a and nuts 39b; where the head 2 includes the cavities 16 in which the axial pistons 3 are guided and run.
  • the entire adjustable movement transmission system is housed, as well as the ball joint support 5, the transmission mechanism to move the mobile carriage 9 and the end heads 3a of the pistons 3, the device tensor 13, as well as the rest of the elements related to them; where said adjustable movement transmission system comprises the planetary reduction device 1, the first plate 15, the second plate 17, as well as the other elements related to them.
  • Both the second base 19b and the intermediate plate 55 of the main casing 19 include holes through which the pistons 3 pass to the outside, and centered holes through which the longitudinal axis 50 of the tensioning device 13 passes.
  • the first base 19a of the main casing 19 includes a centered through hole through which the output shaft 12a of the motor 12 passes into the interior of the casing 12 to connect to the planetary reduction device 1.
  • each of the cavities 16 of the head 2 of the pump ends in an outlet zone that includes a first passage 41a and a second passage 41b in which
  • the pistons 3 move axially inside the cavities 16 in the forward direction to supply the fluid and in the backward direction (opposite the direction of advance) to suck the fluid filling the cavities 16 at least partially, to then return to drive said fluid towards the outlet and so on.
  • the pistons 3 are guided and adjusted axially in holes 57a located in a front plate 57 screwed in a front area of the head 2 opposite a rear area in which the non-return valves 40a, 40b are located; where said holes 57a serve as a guide for the pistons 3, so that the movement of the pistons 3 in any other direction than the axial one, would be limited by said front plate 57 and by the annular body 56 with its quadrangular holes 56a.
  • the flow rate variation provided by the pump of the invention at the outlet of its head 2 through its first slot 37a is achieved by varying the inclination of the second plate 17, and therefore an angle formed by the imaginary axis 41 of said second plate 17 with respect to the horizontal supports 42 of the end bases 19a, 19b of the casing 19, as shown more clearly in figure 5.
  • the variation of the inclination of the second plate 17 is achieved by moving the mobile carriage 9 that is linked to said second plate 17 by means of the crank mechanism.

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

Abstract

La pompe à pistons axiaux pour un fluide comprend un système de transmission de mouvement réglable qui permet de faire varier le débit de fluide à la sortie de la pompe; au moyen dudit système de transmission rotatif, on peut faire varier la course des pistons (3) qui se déplacent axialement à l'intérieur de cavités (16) respectives pour fournir un débit de fluide à la sortie desdites cavités (16) qui sont réparties selon un chemin circonférentiel. La variation du débit de fluide est réalisée par déplacement linéaire d'un chariot mobile (9) qui peut se déplacer dans les deux sens d'une direction parallèle à la direction de déplacement des pistons (3); par déplacement dudit chariot mobile (9), on fait varier l'inclinaison d'un support de rotules (5) au niveau duquel sont accouplés les pistons (3) à une de leurs extrémités.
PCT/ES2022/070364 2021-09-23 2022-06-10 Pompe a pistons axiaux WO2023047002A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP22741544.5A EP4407179B1 (fr) 2021-09-23 2022-06-10 Pompe à piston axial

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ESP202130892 2021-09-23
ES202130892A ES2937207B2 (es) 2021-09-23 2021-09-23 Bomba de pistones axiales

Publications (1)

Publication Number Publication Date
WO2023047002A1 true WO2023047002A1 (fr) 2023-03-30

Family

ID=82546947

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/ES2022/070364 WO2023047002A1 (fr) 2021-09-23 2022-06-10 Pompe a pistons axiaux

Country Status (3)

Country Link
EP (1) EP4407179B1 (fr)
ES (1) ES2937207B2 (fr)
WO (1) WO2023047002A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB551384A (en) * 1941-10-07 1943-02-19 Fawcett Preston & Co Ltd Improvements in swash-plate pumps for liquids
FR60486E (fr) * 1950-08-08 1954-11-03 Siam Pompe hydraulique à haute pression
US2737894A (en) * 1952-08-15 1956-03-13 Oilgear Co Axial type pump with stationary cylinders
DE2062184A1 (de) * 1970-12-17 1972-06-22 Maschinenfabrik Rudolf Hausherr & Söhne GmbH, 4322 Sprockhövel Axialkolbenpumpe
GB1327192A (en) * 1969-05-21 1973-08-15 Nat Res Dev Swashplate pumps

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL7900076A (nl) * 1979-01-05 1980-07-08 Philips Nv Drijfwerk voor een machine met heen- en weergaande zuigers met variabele slag.
EP0035867B1 (fr) * 1980-03-11 1985-07-31 Joseph Scalzo Transmission à plateaux oscillants
JP2626292B2 (ja) * 1991-03-30 1997-07-02 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
EP1435457A1 (fr) * 2003-01-03 2004-07-07 Lavorwash S.p.A. Pompe axiale avec dispositif automatique de réglage du débit
ITUB20155999A1 (it) * 2015-11-30 2017-05-30 Merlo Group Innovation Lab S R L Macchina idraulica a cilindri flottanti

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB551384A (en) * 1941-10-07 1943-02-19 Fawcett Preston & Co Ltd Improvements in swash-plate pumps for liquids
FR60486E (fr) * 1950-08-08 1954-11-03 Siam Pompe hydraulique à haute pression
US2737894A (en) * 1952-08-15 1956-03-13 Oilgear Co Axial type pump with stationary cylinders
GB1327192A (en) * 1969-05-21 1973-08-15 Nat Res Dev Swashplate pumps
DE2062184A1 (de) * 1970-12-17 1972-06-22 Maschinenfabrik Rudolf Hausherr & Söhne GmbH, 4322 Sprockhövel Axialkolbenpumpe

Also Published As

Publication number Publication date
ES2937207B2 (es) 2023-07-31
EP4407179B1 (fr) 2024-09-25
ES2937207A1 (es) 2023-03-24
EP4407179A1 (fr) 2024-07-31

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