EP4102069B1 - Pompe à mouvement alternatif - Google Patents

Pompe à mouvement alternatif Download PDF

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Publication number
EP4102069B1
EP4102069B1 EP22177920.0A EP22177920A EP4102069B1 EP 4102069 B1 EP4102069 B1 EP 4102069B1 EP 22177920 A EP22177920 A EP 22177920A EP 4102069 B1 EP4102069 B1 EP 4102069B1
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EP
European Patent Office
Prior art keywords
piston
casing
alternating pump
support pin
guide
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.)
Active
Application number
EP22177920.0A
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German (de)
English (en)
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EP4102069A1 (fr
Inventor
Luigi Quaretti
Fausto Foracchia
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Idromeccanica Bertolini SpA
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Idromeccanica Bertolini SpA
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Publication of EP4102069A1 publication Critical patent/EP4102069A1/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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/025—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel
    • F04B43/026—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel each plate-like pumping flexible member working in its own pumping chamber
    • 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

Definitions

  • the present pump is intended to be advantageously employed in the attainment of volumetric pumps, in particular of membrane type.
  • the present alternating pump is inserted in the industrial field of production of pumps for farming machinery and is in particular intended to be employed for picking up a fluid from a source, for example a cistern transported by the farming machinery, and for conveying the aforesaid fluid under pressure to a plurality of dispensing nozzles, so as to irrigate or disinfesting cultivations.
  • a source for example a cistern transported by the farming machinery
  • dispensing nozzles so as to irrigate or disinfesting cultivations.
  • the present alternating pump is therefore employable for example in the agriculture field for irrigation or disinfestation of the cultivations, or also in any other field of the art where it is necessary to pump large quantities of liquid.
  • a pumping chamber closed by a corresponding membrane, which is actuatable in an alternating manner in order to expand the volume of the pumping chamber, so as to convey a fluid to be pumped into the same pumping chamber through a corresponding suction channel, and in order to reduce the volume thereof, so as to expel the aforesaid fluid through a corresponding delivery channel.
  • the membranes of the heads of the alternating pump are moved by actuation means housed inside the casing.
  • the aforesaid actuation means are provided with a circular cam, mounted eccentric on a shaft that is actuatable in rotation, and with a thrust arm, extended between a first end having an annular connection body rotatably mounted on the cam and an opposite second end connected to a piston slidable in a corresponding guide jacket in order to move the membrane.
  • actuation means with circular cam is described in the patent EP 2381107 .
  • the main drawback lies in the fact that the eccentric circular cam and the thrust arm are associable with a mechanism of connecting rod-crank type, which is capable of moving the piston connected to the membrane only and exclusively with harmonic motion along the guide jacket.
  • alternating pumps are known that are provided with a thrust cam, which actuates the membrane, through the corresponding piston, to reduce the volume of the pumping chamber, and with a return spring mounted coaxially on each guide jacket and compressed between an external flange radially extended from the same guide jacket and a collar of the corresponding piston, as described for example in the patent KR 100888266 .
  • Such mechanism is likewise also applied in single-head pumps, in which the piston which carries the membrane fixed thereto is maintained pressed against a thrust cam by a spring interposed between an abutment portion of the guide jacket of the aforesaid piston and a pin placed to cross through the piston itself, as described for example in the patent US 6,171,081 .
  • the return spring constantly pushes the piston towards the thrust cam in order to actuate the membrane to expand the volume of the pumping chamber and it is therefore possible to employ a thrust cam having profile such to confer to the piston a particular desired motion law that differs from the harmonic motion conferred by a connecting rod-crank mechanism.
  • the main drawback lies in the fact that the return spring of each piston must be precompressed in order to maintain the corresponding piston in contact with the thrust cam, thus complicating the assembly of the alternating pump.
  • the return spring is coaxially mounted around the guide jacket of the corresponding piston and the piston is inserted in the guide jacket on the opposite side with respect to that at which the membrane is positioned, in a manner such that its collar abuts against the same return spring, which is completely extended. Consequently, a considerable force must be applied in order to mount the guide jacket (carrying the piston already inserted) on the casing and thus shorten the extension of the spring between collar of the piston and external flange of the guide jacket.
  • the piston since the piston is guided in the corresponding guide jacket and the return spring is coaxially mounted on the guide jacket, the piston must protrude from the corresponding guide jacket in order to allow the return spring to exert its own elastic force against the collar, with consequent increase of the piston and hence of the radial size of the alternating pump.
  • the return spring is the only component of the alternating pump which maintains the corresponding piston in contact with the thrust cam, the same return spring must be provided with a rigidity that is particularly high in order to exert a suitable elastic force.
  • the use of such return springs with high rigidity tends to increase the costs of the alternating pumps, since the cost of the same springs is proportion to their rigidity.
  • alternating pumps of type completely different from those described above.
  • Such alternating pumps are provided with two heads mounted on opposite sides of a same casing and each provided with an actuation piston of the membrane connected to the piston of the other head through a spring.
  • the aforesaid spring acts in order to bring back, on rotation, one of the two membranes to expand the volume of its own pumping chamber while the other membrane is actuated to reduce the volume of its corresponding pumping chamber.
  • the problem underlying the present invention is therefore that of eliminating the problems of the abovementioned prior art, by providing an alternating pump, whose membranes can be moved with any one motion law.
  • a further object of the present invention is to provide an alternating pump, which can be assembled in a quick manner.
  • a further object of the present invention is to provide an alternating pump, which has a particularly reduced radial size.
  • a further object of the present invention is to provide an alternating pump, which is simple and inexpensive to attain.
  • a further object of the present invention is to provide an alternating pump, which is entirely reliable in operation.
  • reference number 1 overall indicates an alternating pump according to the present invention.
  • the present invention is in particular inserted in the industrial field of production of volumetric pumps with multiple heads, which must be capable of pumping large flows of fluid with reduced dispensing discontinuities.
  • the present alternating pump 1 has particular application in the farming field of irrigation and disinfestation of cultivations, since it is advantageously intended to be used for pumping herbicide agents, insecticides or fertilizers, for example contained in a cistern mounted on farming machinery, and for dispensing them, for example through a distribution device having multiple dispensing nozzles, on a cultivated terrain.
  • the present alternating pump 1 comprises a casing 2 provided with at least three guide jackets 23, each of which defining a guide seat 3 extended along a corresponding radial direction X.
  • the present alternating pump 1 is provided with at least three heads 4, each of which mounted on the casing 2 at a respective guide seat 3 and at least partially defines a pumping chamber 5, and with at least three membranes 6 each of which delimiting a corresponding pumping chamber 5.
  • each head 4 is provided with a suction channel 34 in fluid connection with the pumping chamber 5, in order to allow the suction of a fluid to be pumped within the same pumping chamber 5, and with a dispensing channel 35 in turn in fluid connection with the pumping chamber 5, in order to allow the delivery dispensing of such fluid to be pumped.
  • the alternating pump 1 also comprises actuation means 7, which are housed within the casing 2 and comprise at least three pistons 8 and a drive shaft 9.
  • Each of the pistons 8 carries, fixed thereto, a corresponding membrane 6 and is susceptible of sliding in a guided manner in a corresponding guide seat 3, in particular along its radial direction X, between a release position, in which the corresponding membrane 6 expands the volume of the pumping chamber 5, and a compression position, in which the membrane 6 reduces the volume of the pumping chamber 5.
  • the pistons 8 are each provided with a thrust body 54 slidably inserted along the radial direction X in the guide seat 3 of the guide jacket 23.
  • each membrane 6 is fixed to the thrust body 54 of the corresponding piston 8, in particular by means of a retention screw 55 having its threaded stem placed to traverse the same membrane 6 and screwed to the thrust body 54 and by means of a support plate 56 maintained adhered against the face of the membrane 6 directed towards the pumping chamber 5 from the enlarged head of the same retention screw 55.
  • the drive shaft 9 carries, fixed thereto, at least one thrust cam 10, which abuts against each piston 8 and is actuatable to rotate around a rotation axis Y thereof, in particular substantially orthogonal to the radial direction X of the guide seats 3, in order to move each piston 8 from the release position to the compression position.
  • the aforesaid thrust cam 10 can be fit on the drive shaft 9, as illustrated in the enclosed figures, or it can be made in a single body with the same drive shaft 9.
  • the membrane 6 expands the volume of the pumping chamber 5 in order to generate reduced pressure within the same and thus suction the fluid to be pumped through the suction channel 34 and, when the piston 8 translates along the corresponding radial direction X from the release position to the compression position, the membrane 6 reduces the volume of the pumping chamber 5 in order to generate an overpressure within the pumping chamber 5 and expel the previously suctioned fluid in delivery through the dispensing channel 35.
  • the present alternating pump 1 preferably comprises an inlet manifold 39 mounted on the casing 2 and provided with at least one inlet mouth, intended to be connected to the aforesaid fluid source in order to receive therefrom the fluid to be pumped, and with multiple supply mouths 41, which are each connected to a corresponding suction channel 34 in order to supply the fluid to be pumped.
  • the present alternating pump 1 preferably comprises a delivery manifold 42 mounted on the casing 2 and provided with multiple reception mouths 43, which are each connected to a corresponding dispensing channel 35 in order to receive the fluid, and with at least one outlet mouth, which is intended to be connected to the aforesaid dispensing device in order to supply the pumped fluid thereto.
  • the present alternating pump 1 comprises three heads 4 and, hence, three corresponding guide jackets 23, three corresponding pistons 8 and three corresponding membranes 6.
  • the present alternating pump 1 can comprise more than three heads 4, e.g. four heads 4, and consequently an analogous number of guide jackets 23, of pistons 8 and membranes 6.
  • the guide jackets 23 (and hence also the guide seats 3 at which the heads 4 are mounted with their membranes 6 moved by the respective pistons 8) are angularly distributed equidistant from each other, in particular at an angular distance of 120° each from the adjacent one, as illustrated in the enclosed figures 3 , 4 and 6 .
  • each guide jacket 23 is advantageously provided with a lateral wall 24 placed to delimit the corresponding guide seat 3.
  • each piston 8 is slidably inserted substantially to size in the guide seat 3 delimited by the corresponding lateral wall 24.
  • each guide jacket 23 has cylindrical extension around the radial direction X and the thrust body 54 of the piston 8 has substantially circular shape in plan view.
  • the casing 2 also comprises a central support body 32 provided with at least three lateral openings 33, one for each head 4, which are each aligned with the radial direction X of a corresponding guide seat 3.
  • the central support body 32 of the casing 2 is extended along a main extension axis Z between two opposite bases 36, is provided with at least three lateral faces 37, one for each head 4, substantially planar (preferably parallel to the main extension axis Z and perpendicular to the bases 36) and at its interior delimits a containment chamber 38 for the actuation means 7, and from such containment chamber 38 the aforesaid lateral openings 33 are extended up to the lateral faces 37.
  • the rotation axis Y of the drive shaft 9 is preferably coinciding with the main extension axis Z of the central support body 32 of the casing 2.
  • a corresponding access opening 52 to the containment chamber 38 is made, so as to allow a facilitated assembly of the actuation means 7.
  • the aforesaid access opening 52 is closed by a first lid 53, which is preferably provided with a through opening 57 traversed by the drive shaft 9 of the actuation means 7.
  • an access opening 52 is made, of which one of the access openings 52 is closed by a corresponding first lid 53 and the other of the access openings 52 is closed by a second lid 53'.
  • the first lid 53 is provided with the aforesaid through opening 57 traversed by the drive shaft 9 and the second lid 53' is provided with a blind seat 58, in which a terminal portion of the same drive shaft 9 is inserted (rotatably around the rotation axis Y).
  • each guide jacket 23 comprises a positioning flange 27 transversely extended starting from the lateral wall 24 and retained at least between the corresponding head 4 and the central support body 32 of the casing 2.
  • the lateral wall 24 of the guide jacket 23 is extended along the radial direction X at least partially within the corresponding lateral opening 33, in a manner such that the guide seats 3 are in turn extended inside the central support body 32 of the casing 2, thus reducing the overall size of the present alternating pump 1.
  • each head 3 is preferably retained between the corresponding head 4 and the central support body 32 of the casing 2.
  • each lateral opening 33 is provided with an enlarged portion 60 at the respective lateral face 37, in order to at least partially house the positioning flange 27 of the corresponding guide jacket 23.
  • each lateral opening 33 defines, on the central support body 32, corresponding abutment portions 47 against which the positioning flanges 27 are placed.
  • the positioning flanges 27 are completely housed in the enlarged portion 60 of the corresponding lateral openings 33 and placed in abutment against the respective abutment portion 47, and the membranes 6 are pressure pressed against the positioning flanges 27 by the corresponding heads 4 mounted on the casing 2.
  • the positioning flanges 27 and the enlarged portions 60 of the lateral openings 33 have shape that is substantially counter-shaped with respect to each other.
  • the positioning flanges 27 and the enlarged portions 60 of the corresponding lateral openings 33 can have circular shape, in accordance with the preferred embodiment, or otherwise they can have polygonal shape.
  • Each head 4 advantageously comprises a shaped body 48 provided with a rear face 49, directed in the sense opposite the central support body 32 and hence intended to remain visible, and with a front face 50, which, like the lateral faces 37 of the same central support body 32, has substantially planar extension, so as to be mechanically coupled to one of these.
  • a front face 50 which, like the lateral faces 37 of the same central support body 32, has substantially planar extension, so as to be mechanically coupled to one of these.
  • multiple through holes are preferably made on the shaped body 48 of the head 4 and multiple threaded holes are made on each lateral face 37 of the central support body 32 that correspond to the through holes of the heads 4, in order to make a bolted connection between each head 4 and the central support body 32.
  • the pumping chamber 5 of each head 4 is made by means of a concavity with substantially cap-shaped form on the front face 50 and is closed by a corresponding membrane 6, which is advantageously retained between head 4 itself and central support body 32 of the casing 2, in particular between front face 50 of the head 4 and positioning flange 27 of the corresponding guide jacket 23 in abutment against the abutment portion 47, as described above.
  • a seat 51 is advantageously made, around the concavity which at least partially defines the pumping chamber 5, and such seat 51 at least partially houses the membrane 6, in turn preferably at least partially housed in the enlarged portion 60 of the corresponding lateral opening 33.
  • each guide jacket 23 does not have to be inserted within a corresponding lateral opening 33 but rather it can be extended protruding with respect to the corresponding lateral face 37 of the central support body 32.
  • each guide jacket 23 comprises a first fixing flange, which is extended radially starting from a first end of the lateral wall 24 and is mechanically coupled to the corresponding lateral face 37 of the central support body 32, e.g. by means of screws, and a second fixing flange, which is radially extended starting from an opposite second end of the lateral wall 32 and carries, mounted thereon, a corresponding head 4, with the corresponding membrane 6 retained interposed between head 4 and second fixing flange.
  • the actuation means 7 comprise at least three return springs 11, each of which placed to connect between two adjacent pistons in order to move each piston 8 from the compression position to the release position.
  • each return spring 11 exerts, on each piston 8 to which it is connected, an elastic force directed towards the adjacent piston 8, in a manner such that the same elastic force is provided with at least one component lying on the radial direction X of the guide seat 3 in which the corresponding piston 8 is slidably inserted and directed towards the thrust cam 10.
  • the return springs 11 always maintain the pistons 8 in abutment against the thrust cam 10, and thus allow employing a thrust cam 10 having a profile such to be able to move the pistons 8 with any one motion law along the radial direction X of the corresponding guide seat 3.
  • each return spring 11 is extended between two opposite ends 16 thereof, of which one is connected to a piston 8 and the other is connected to one of the two adjacent pistons.
  • each piston 8 comprises at least two retention eyelets 12, each of which engaged by an end 16 of a corresponding return spring 11 placed to connect between the piston 8 itself and one of the two pistons 8 adjacent thereto.
  • the ends 16 of the retention springs 11 are shaped substantially hook-like, in a manner such that the same ends 16 do not risk disconnection from the retention eyelets 12 during the use of the present alternating pump 1.
  • the retention eyelets 12 are made in a single body with the thrust body 54 of the piston 8, so as to reduce the overall number of the different components which must be assembled together in order to compose the present alternating pump 1.
  • each piston 8 advantageously comprises a support pin 15 extended along an axis thereof transverse to the radial direction X, in particular substantially perpendicular thereto, and the retention eyelets 12 are made on at least one connection flange 17 having an annular body 18 inserted on the aforesaid support pin 15.
  • connection flange 17 on which the retention eyelets 12 are obtained with having to substitute the entire piston 8 or its thrust body 54, as instead would occur in the event in which the retention eyelets 12 were made in a single body with the thrust body 54 itself.
  • each connection flange 17 preferably comprises two retention eyelets 12 engaged by the ends 16 of the return springs 11 which connect the corresponding piston 8 with the two adjacent pistons.
  • the retention eyelets 12 are angularly spaced around the annular body 18 by a spacing angle substantially comprised between 45° and 75° and, still more preferably, substantially equal to 60°.
  • each connection flange 17 is rotatably mounted on the support pin 15 of the corresponding piston 8, in a manner such that the same connection flange 17 is free to rotate with respect to the support pin 15 under the action of the elastic forces exerted by the return springs 11.
  • the retention eyelets 12 can be made on different connection flanges 17, each of which comprises only one retention eyelet 12 and a corresponding annular body 18 mounted on the support pin 15.
  • each connection flange 17 is free to rotate around the corresponding support pin 15, under the action of the elastic force exerted by the respective return spring 11, in a manner entirely independent from the other connection flange 17 on which the other retention eyelet 12 is made.
  • the pistons 8 each advantageously comprise a cam follower 13 provided with at least one bearing 14, which rotates in contact with the thrust cam 10.
  • the aforesaid bearing 14 is rotatably mounted on the support pin 15 of the corresponding piston 8.
  • the same cam follower 13 can comprise more than one bearing 14 mounted on the support pin 15, e.g. two bearings 14 placed side-by-side each other and placed in contact with the thrust cam 10.
  • the support pin 15 is fixed to the thrust body 54 of the corresponding piston 8 or is made in a single body therewith.
  • the aforesaid support pin 15 can be extended along the axis thereof transverse to the radial direction X starting from a corresponding shoulder extended protruding from the thrust body 54 along the radial direction X towards the thrust cam 10, in particular hence on the side opposite that on which the membrane 6 is fixed, and a bearing 14 and a connection flange 17 can be rotatably mounted, placed adjacent to each other.
  • each piston 8 advantageously comprises two annular shoulders 20 facing each other, which carry inserted therein the support pin 15 and carry interposed between them the bearing 14 of the corresponding cam follower 13, and possibly more than one bearing 14.
  • annular shoulders 20 are extended protruding from the thrust body 54 of the corresponding piston 8 along the radial direction X towards the thrust cam 10, in particular hence on the side opposite that on which the membrane 6 is fixed.
  • each connection flange 17 is advantageously mounted on the support pin 15 of the corresponding piston 8 adjacent to one of the two annular shoulders 20.
  • a sliding bushing 19 is coaxially interposed, so as to reduce the rotation friction between annular body 18 and support pin 15 itself.
  • the support pin 15 carries mounted thereon at least one first spacer element 21 interposed between the annular body 18 of the connection flange 17 and an annular shoulder 20 of the corresponding piston 8.
  • connection flanges 17 along the support pins 15 are reduced, so as to limit therefore possible elongations and shortenings of the return springs 11 not caused by the action of the thrust cam 10.
  • the aforesaid first spacer element 21 is mounted on the support pin 15 of the corresponding piston 8 at the sliding bushing 19, in a manner such that the aforesaid sliding bushing 19 is coaxially interposed, between the support pin 15 and the annular body 18 of the connection flange 17, as well as between the same support pin 15 and the first spacer element 21 itself.
  • each piston 8 preferably carries, mounted thereon, at least one stop ring 61, e.g. a Seeger ring, interposed at least between the connection flange 17 and the guide jacket 23, i.e. in particular between the connection flange 17 and the lateral wall 24 of the guide jacket 23.
  • stop ring 61 e.g. a Seeger ring
  • stop ring 61 is arranged for maintaining at least the first spacer element 21 and the connection flange 17 placed against the respective annular shoulder 20 of the corresponding piston 8.
  • each support pin 15 carries, mounted thereon, a second spacer element 62 interposed between the connection flange 17 and the stop ring 61, in a manner such that the same connection flange 17 does not come directly in contact with the stop ring 61.
  • the second spacer element 62 is mounted on the support pin 15 of the corresponding piston 8 at the sliding bushing 19, in a manner such that the aforesaid sliding bushing 19 is also coaxially interposed between the same support pin 15 and the second spacer element 62 itself.
  • each pair of adjacent pistons is advantageously connected by two return springs 11 placed adjacent to opposite sides 22 of the thrust cam 10.
  • the actuation means 7 comprise at least six return springs 11 (i.e. in particular two return springs 11 placed to connect each piston 8 and one of the two pistons 8 adjacent thereto), of which at least three return springs 11 are placed on a first lying plane placed adjacent to one side 22 of the thrust cam 10 and the other three are placed on a second lying plane parallel to the first and placed adjacent to the opposite side 22 of the thrust cam 10.
  • connection flanges 17 are preferably mounted on the support pin 15 of each piston 8, each placed adjacent to a corresponding annular shoulder 20 and each provided with two retention eyelets 12.
  • the retention eyelets 12 of each connection flange 17 are engaged by the ends 16 of two return springs 11 lying on the same first or second lying plane.
  • both the connection flanges 17 mounted on a same support pin 15 have - coaxially interposed between them - their annular body 18 and the support pin 15 itself with corresponding sliding bushing 19, they are maintained spaced from the corresponding annular shoulder 20 by a first spacer element 21 thereof and are maintained in position along the pin 15 by a corresponding stop ring 61 and by the second spacer 62.
  • the lateral wall 24 of each guide jacket 23 is advantageously provided with at least one longitudinal opening 25 extended along the radial direction X of the corresponding guide seat 3 and slidably carrying, inserted therein, one end 26 of the support pin 15 of the corresponding piston 8.
  • each guide jacket 23 is provided with two longitudinal openings 25 that face each other and have, slidably inserted therein, the two opposite ends 26 of the corresponding support pin 15.
  • the thrust body 54 of each piston 8 has, in plan view, substantially polygonal shape, e.g. rectangular, and the lateral wall 24 of the guide jacket 23 delimits a corresponding guide seat 3 substantially counter-shaped with respect to the thrust body 54, always in order to prevent the rotation of the piston 8 around the radial direction X.
  • the casing 2 comprises suitable centering elements 28, each connected to the central support body 32 and to the positioning flange 27 of a corresponding guide jacket 23 and configured for blocking the rotation of the aforesaid positioning flange 27, with respect to the central support body 32, around the radial direction X.
  • each piston 8 around the radial direction X thereof is locked by the ends 26 of the corresponding support pin 15 inserted in the longitudinal openings 25 on the lateral wall 24 of the guide jacket 23 and since the rotation of each guide jacket 23 around the aforesaid radial direction X is locked by a suitable centering element 28 connected to the central support body 32 of the casing 2 and to the corresponding positioning flange 27, it is possible to prevent the bearing 14 of each cam follower 13 modifies the tilt thereof around the radial direction X with respect to the thrust cam 10.
  • the centering element 28 comprises multiple retention pins extended protruding from the central support body 32 of the casing 2 and/or from the positioning flange 27 of the respective guide jackets 23 and inserted in corresponding seats made on the positioning flanges 27 and/or on the central support body 32.
  • the central support body 32 of the casing 2, at each head 4, comprises at least one first centering hole 29 and the positioning flange 27 of each guide jacket 23 comprises at least one corresponding second centering hole 30.
  • the centering element 28 comprises at least one pin 31 at least partially inserted in the first centering hole 29 of the central support body 32 and in the second centering hole 30 of the positioning flange 27.
  • the invention thus conceived therefore attains the pre-established objects.

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

Claims (10)

  1. Pompe à mouvement alternatif (1), laquelle comprend:
    - un carter (2) muni d'au moins trois chemises de guidage (23), chacune desquelles définit un siège de guidage (3) correspondant se développant le long d'une direction radiale (X) correspondante;
    - au moins trois têtes de pompe (4), chacune desquelles est montée sur ledit carter (2) au niveau dudit siège de guidage (3) respectif et définit au moins partiellement une chambre de pompage (5),
    - au moins trois membranes (6) chacune desquelles délimite ladite chambre de pompage (5);
    - des moyens d'actionnement (7) qui sont logés à l'intérieur dudit carter (2) et comprennent:
    - au moins trois pistons (8), chacun desquels porte de manière fixe ladite membrane (6) correspondante et est susceptible de coulisser de façon guidée dans ledit siège de guidage (3) correspondant entre une position de libération, dans laquelle ladite membrane (6) correspondante augmente le volume de la chambre de pompage (5) et une position de compression, dans laquelle ladite membrane (6) réduit le volume de ladite chambre de pompage (5);
    - un arbre de transmission (9) portant de manière fixe au moins une came de poussée (10), laquelle est en appui sur chacun desdits pistons (8) et peut être entraîné en rotation autour de son propre axe de rotation (Y) pour le déplacer de ladite position de libération à ladite position de compression;
    ladite pompe à mouvement alternatif étant caractérisée en ce que lesdits moyens d'actionnement (7) comprennent au moins trois ressorts de rappel (11), chacun desquels est placé en connexion entre deux pistons (8) adjacents pour déplacer chaque piston (8) de ladite position de compression à ladite position de libération.
  2. Pompe à mouvement alternatif (1) selon la revendication 1, caractérisée en ce que chaque piston (8) comprend au moins deux anneaux de retenue (12), chacun desquels est engagé par un embout (16) d'un ressort de rappel (11) correspondant, placé en connexion entre ledit piston (8) et l'un desdits deux pistons (8) adjacents à celui-ci.
  3. Pompe à mouvement alternatif (1) selon la revendication 2, caractérisée en ce que chaque piston (8) comprend un pivot de support (15) se développant le long d'un propre axe transversal à ladite direction radiale (X) correspondante;
    les anneaux de retenue (12) de chacun desdits pistons (8) étant obtenus sur au moins une bride de raccordement (17) ayant un corps annulaire (18) inséré sur le pivot de support (15) dudit piston (8) correspondant.
  4. Pompe à mouvement alternatif (1) selon la revendication 3, caractérisée en ce que lesdits pistons (8) comprennent chacun un galet suiveur de came (13) pourvu d'au moins un palier (14), qui est monté de manière rotative sur le pivot de support (15) dudit piston (8) correspondant et tourne en contact avec ladite came de poussée (10).
  5. Pompe à mouvement alternatif (1) selon la revendication 3 ou 4, caractérisée en ce qu'une douille de coulissement (19) est interposée de manière coaxiale entre le corps annulaire (18) de chaque bride de raccordement (17) et le pivot de support (15) dudit piston (8) correspondant.
  6. Pompe à mouvement alternatif (1) selon la revendication 4 ou 5, caractérisée en ce que chaque piston (8) comprend deux épaulements annulaires (20) faisant face l'un à l'autre, qui portent ledit pivot de support (15) correspondant, inséré à l'intérieur de ceux-ci, et portent l'au moins un palier (14), interposé entre eux, dudit galet suiveur de came (13) correspondant;
    le corps annulaire (18) de chaque bride de raccordement (17) étant monté sur le pivot de support (15) dudit piston (8) correspondant de manière adjacente audit épaulement annulaire (20) et ledit pivot de support (15) portant au moins un premier élément d'espacement (21), monté, interposé entre le corps annulaire (18) de ladite bride de raccordement (17) et ledit épaulement annulaire (20).
  7. Pompe à mouvement alternatif (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que chaque paire de pistons (8) adjacents est reliée par deux ressorts de rappel (11) disposés de manière adjacente sur les côtés opposés (22) de ladite came de poussée (10).
  8. Pompe à mouvement alternatif (1) selon l'une quelconque des revendications 3 à 7, caractérisée en ce que chacune desdites chemises de guidage (23) est pourvue d'une paroi latérale (24) placée pour délimiter ledit siège de guidage (3) correspondant;
    la paroi latérale (24) de ladite chemise de guidage (23) étant pourvue d'au moins une ouverture longitudinale (25) se développant le long de la direction radiale (X) dudit siège de guidage (3) correspondant et portant une extrémité (26), insérée de manière coulissante, du pivot de support (15) dudit piston (8) correspondant.
  9. Pompe à mouvement alternatif (1) selon la revendication 8, caractérisée en ce que ledit carter (2) comprend un corps de support central (32) pourvu d'au moins trois ouvertures latérales (33), l'une pour chacune desdites têtes de pompe (4), qui sont chacune alignées avec la direction radiale (X) dudit siège de guidage (3) correspondant;
    chacune desdites chemises de guidage (23) comprenant une bride de positionnement (27) s'étendant transversalement à partir de la paroi latérale (24) et retenue au moins entre la tête de pompe (3) correspondante et le corps de support central (32) dudit carter (2);
    ledit carter (2) comprenant des éléments de centrage (28) chacun reliés audit corps de support central (32) et à ladite bride de positionnement (27) de l'une desdites chemises de guidage (23) correspondante et chacun configurés pour bloquer la rotation de ladite bride de positionnement (27) correspondante, par rapport audit corps de support central (32), autour de ladite direction radiale (X).
  10. Pompe à mouvement alternatif (1) selon la revendication 9, caractérisée en ce que le corps de support central (32) dudit carter (2), au niveau de chaque tête de pompe (4), comprend au moins un premier orifice de centrage (29) et la bride de positionnement (27) de chaque chemise de guidage (23) comprend au moins un second orifice de centrage (30) correspondant;
    l'élément de centrage (28) comprenant au moins un goujon (31) au moins partiellement inséré dans le premier orifice de centrage (29) du corps de support central (32) dudit carter (2) et dans le second orifice de centrage (30) de ladite bride de positionnement (27).
EP22177920.0A 2021-06-09 2022-06-08 Pompe à mouvement alternatif Active EP4102069B1 (fr)

Applications Claiming Priority (1)

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IT202100015101 2021-06-09

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EP4102069B1 true EP4102069B1 (fr) 2024-03-06

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Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3291055A (en) * 1965-08-02 1966-12-13 Alexander S Limpert Self-purging proportioning pump for corrosive liquids
GB1356485A (en) * 1972-01-15 1974-06-12 Gen Motors France Diaphragm pumps
US6171081B1 (en) * 1998-02-17 2001-01-09 Keihin Corporation Fuel pump assembly
KR100888266B1 (ko) 2008-05-23 2009-03-10 천세산업 주식회사 등속도 캠을 이용한 3 연식 무맥동 정량펌프 및 제어방법
US20110171045A1 (en) * 2010-01-14 2011-07-14 Briggs & Stratton Corporation Pressure washer pump
IT1399533B1 (it) * 2010-04-22 2013-04-19 Bertolini Idromeccanica Pompa alternativa

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WO2022259177A1 (fr) 2022-12-15

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