EP0167635A1 - Circuit hydraulique pour le contrôle de pompes à piston alternatif - Google Patents

Circuit hydraulique pour le contrôle de pompes à piston alternatif Download PDF

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Publication number
EP0167635A1
EP0167635A1 EP84104810A EP84104810A EP0167635A1 EP 0167635 A1 EP0167635 A1 EP 0167635A1 EP 84104810 A EP84104810 A EP 84104810A EP 84104810 A EP84104810 A EP 84104810A EP 0167635 A1 EP0167635 A1 EP 0167635A1
Authority
EP
European Patent Office
Prior art keywords
cylinders
circuit
valve
pumping
oleodynamic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP84104810A
Other languages
German (de)
English (en)
Other versions
EP0167635B1 (fr
Inventor
Alfredo Brandi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
COMPAGNIA ITALIANA FORME ACCIAIO S P A
Original Assignee
COMPAGNIA ITALIANA FORME ACCIAIO S P A
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 COMPAGNIA ITALIANA FORME ACCIAIO S P A filed Critical COMPAGNIA ITALIANA FORME ACCIAIO S P A
Priority to EP84104810A priority Critical patent/EP0167635B1/fr
Priority to DE8484104810T priority patent/DE3479911D1/de
Priority to AT84104810T priority patent/ATE46745T1/de
Publication of EP0167635A1 publication Critical patent/EP0167635A1/fr
Application granted granted Critical
Publication of EP0167635B1 publication Critical patent/EP0167635B1/fr
Expired legal-status Critical Current

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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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • F04B7/0233—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated a common distribution member forming a single discharge distributor for a plurality of pumping chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F04B9/1178—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders

Definitions

  • the present invention concerns an open oleodynamic circuit with automatic sequence, having an indirect piloting system for the control of reciprocating piston pumps, particularly of concrete pumps, of the type comprising two cylinders for pumping the material and two cylinders for the control of a valve deviating said material in synchronism with the pumping cylinders.
  • the oleodynamic circuit according to the present invention proposes and allows to overcome all the heretofore specified drawbacks, which are typical of the already known solutions.
  • It is of the type comprising two pumping cylinders, two cylinders for the control of a deviating valve, through which the pumping cylinders are alternately placed in communication with a delivery pipe and with a charging hopper, and hydraulic valves for controlling the direction of movement of the pistons in said cylinders, and it is essentially characterized in that said hydraulic valves are controlled by means of auxiliary hydraulic valves, acting as relays forming part of said circuit, each of said auxiliary hydraulic valves operating as the two cylinders controlled by the other valve reach the wanted positions.
  • the oleodynamic circuit comprises two hydraulic pumping cylinders 1 and 3, to which are connected the pistons 34 thrusting the material (concrete); two hydraulic cylinders 2 and 4 controlling the deviating valve, both connected to a handle; a two-position hydraulic valve 5, with floating slider for feeding the two valve cylinders 2 and 4; a two-position hydraulic valve 6, with floating slider for feeding the hydraulic pumping cylinders 1 and 3; a three-position auxiliary hydraulic valve 7, controlled by the flow under pressure determined by the position of the deviating valve and sent, through pipes 21 and 22, from the cylinders 2 and 4, said hydraulic valve 7 acting as relay for piloting the hydraulic valve 6; a three-position auxiliary hydraulic valve 8, controlled by the flow under pressure determined by the position of the hydraulic pumping cylinders and sent, through pipes 17 and 18, from the cylinders 1 and 3, said hydraulic valve 8 acting as relay for piloting the hydraulic valve 5; two solenoid valves 9 and 10 (or, where required, manually controlled valves), for remote controlling of the hydraulic valve 5; two solenoid valve
  • the pipe 21 will connect itself to exhaust like the pipe 22, creating the conditions whereby the slider of the hydraulic valve 7 moves to the center, causing the slider of the hydraulic valve 6 to remain in a steady closing position.
  • the pumping cylinder 3, through the pipe 20a, remains connected to the pump, parallely to the pipe 29b, throughout the stroke length of the cylinders 4 and 2 controlling the deviating valve.
  • two holes 13 and 38 are provided in correspondence of the end-of-stroke inlet position.
  • the first hole more or less coincides with the center of the piston, which is apt to close the same; the second hole is spaced from the first by a distance such as to make sure that, during the return stroke of the piston, the first hole closes upon opening of the second hole.
  • the hydraulic valves 7 and 8 designed to process the signals issued from the cylinders, are apt to guarantee stability to the slider of the respective main hydraulic valves 6 and 5, in any pressure conditions of the hydraulic circuit and in any intermediate position of the cylinder pistons. This means that the change of situation occurs only when each of the cylinders 1 to 4 has reached its end-of-stroke position.
  • phase III starts, as illustrated in figure 3.
  • the cylinder 3 completes its stroke slightly in advance in respect of the cylinder 1 and, in this situation, all the piloting conditions already examined in phase I are reproduced.
  • the relay-hydraulicvalve 8 moves from the central position to the outer position and, consequently, the hydraulic valve 5 changes position, causing the pipe 29a to go into pressure and the pipe 29b to discharge.
  • the cylinder 2 starts its stroke, which causes the deviating valve to take up a new position.
  • the slider of the relay-hydraulicvalve 7 takes up the central position, keeping the hydraulic valve 6, which controls the pumping cylinders in a steady closed position.
  • the relay-hydraulicvalve 8 holds the final taken up position or, at the most, in the event of the pressure in the system being very low, it takes up the central position.
  • Phase IV which is the last phase of the cycle, is illustrated in figure 4:
  • An oleodynamic circuit as that described guarantees for each cylinder movement to take place only if the previous movement has been accomplished; it operates at a regular rate and keeps the synchronism in each situation; as well as being realized with standardized components (cylinders excluded), which have the merit to be easily found at limited costs. Furthermore, it works with an automatic sequence of the various phases and it can thus be stopped and started again without any preferential positions. If, for any special reasons (which are obviously not analysed herein), the pumping cylinders should miss the synchronism, due to excess or want of oil in the slave circuit, it is not necessary to resort to expedients or supplementary operations, as the circuit self-synchronizes.
  • the cylinder 1 ends its inlet stroke in advance in respect of the outgoing cylinder 3, and produces the sequence signal; the cylinder 3 in turn performs its inlet stroke and the cylinder 1 its outlet stroke, and so on.
  • the two pumping cylinders will gradually perform longer and longer strokes as, in the slave circuit, a predetermined amount of oil continually flows through the capacity regulator 14, up to reaching the full stroke.
  • this operation is carried out by acting on the solenoid valves 9 and 10, exciting them for the length of time required to remove the obstacle.
  • Figure 7 shows a phase of the suction cycle referring to a previous situation, as that of figure 4.
  • a third function can be provided to complete the first two, namely that allowing to bring the deviating valve adherent to the pumping cylinders, when these latter are working, and to keep it instead slightly apart (it may even be enough to simply eliminate the coupling force) when having to move from one cylinder to the other.
  • FIG 8 illustrates a phase of the cycle wherein the pumping cylinders have ended their stroke.
  • the cylinder 3 puts simultaneously under pressure the pipes 18 and 43, while the slave circuit is already at the exhaust by way of the single-acting valve 19.
  • the flow under pressure simultaneously affects the pipes 44 and 45, which connect the opposite ends of the slider of the hydraulic valve 46.
  • the flow entering the pipe 44 has to cross the throttle 50, and since it is furthermore connected to the pipe 16, which is at this moment positioned in exhaust, there will no doubt be a difference in pressure JL p between the pipes 44 and 45, such as to overcome the opposing force of the positioning spring provided on the hydraulic valve 46.
  • Figure 9 illustrates the phase which follows the one heretofore described; in this latter, the cylinder of the valve 4 has performed its stroke and created the conditions for the starting of the pumping cylinder 1.
  • the pipe 20b goes into pressure simultaneously with the slave circuit of the pumping cylinders, whereupon also the pipes 44 and 45 have the same pressure.
  • the positioning spring of the hydraulic valve 46 acts so as to drain the pipe 45 into the pipe 44 through the throttle 50, whereby the pipe 48 goes into pressure and the pipe 47 discharges.
  • the cylinder 49 then moves from left to right, so performing the pulling function (forced drawing ⁇ f the valve close to the pumping cylinder).
  • the cylinder 49 when working in the pulling sense (T), has no stroke limitation, which means that it can recover with time the slack produced by wear, whereas when working in the parting sense (S), it has stroke limitations, in that the possible stroke is that deriving from the yielding of the seals on the piston and from the compressibility of the hydraulic fluid. Furthermore, the amount of oil required for this function is low comparatively to that placed in circulation in the hydraulic system, and namely such as not to cause perceptible delays in the piloting system.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP84104810A 1984-06-05 1984-06-05 Circuit hydraulique pour le contrôle de pompes à piston alternatif Expired EP0167635B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP84104810A EP0167635B1 (fr) 1984-06-05 1984-06-05 Circuit hydraulique pour le contrôle de pompes à piston alternatif
DE8484104810T DE3479911D1 (en) 1984-06-05 1984-06-05 Hydraulic circuit for the control of reciprocating pistons pump
AT84104810T ATE46745T1 (de) 1984-06-05 1984-06-05 Hydraulischer kreislauf fuer pumpen mit hin- und hergehenden kolben.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP84104810A EP0167635B1 (fr) 1984-06-05 1984-06-05 Circuit hydraulique pour le contrôle de pompes à piston alternatif

Publications (2)

Publication Number Publication Date
EP0167635A1 true EP0167635A1 (fr) 1986-01-15
EP0167635B1 EP0167635B1 (fr) 1989-09-27

Family

ID=8191908

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84104810A Expired EP0167635B1 (fr) 1984-06-05 1984-06-05 Circuit hydraulique pour le contrôle de pompes à piston alternatif

Country Status (3)

Country Link
EP (1) EP0167635B1 (fr)
AT (1) ATE46745T1 (fr)
DE (1) DE3479911D1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997018395A1 (fr) * 1995-11-13 1997-05-22 Putzmeister Aktiengesellschaft Procede et dispositif pour commander une pompe a liquides epais a deux cylindres
EP0931934A1 (fr) * 1998-01-27 1999-07-28 Dosiertechnik und Pneumatik AG Dopag Dispositif de pompage des matériaux visqueux
WO2003001062A1 (fr) * 2001-06-22 2003-01-03 Viking Technology As Pompe a haute pression
WO2006103219A1 (fr) * 2005-03-29 2006-10-05 Stefano Baiardo Circuit hydraulique pour une unite de pompage de beton
EP1847710A1 (fr) * 2006-04-20 2007-10-24 COMPAGNIA ITALIANA FORME ACCIAIO S.p.A. Systeme à circuit ouvert de distribution oleodynamique pour une pompe à béton.
CN104196786A (zh) * 2014-07-29 2014-12-10 徐州五洋科技股份有限公司 一种矿用湿喷机用全液压控制泵送液压系统
CN104329306A (zh) * 2014-10-31 2015-02-04 徐州徐工施维英机械有限公司 一种液压控制系统、方法和泵
WO2020120234A1 (fr) * 2018-12-14 2020-06-18 Schwing Gmbh Pompe à piston et procédé pour faire fonctionner une pompe à piston

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3327641A (en) * 1965-03-08 1967-06-27 Air Placement Equipment Co Inc Concrete pump
LU56224A1 (fr) * 1968-01-03 1969-04-22
FR2291374A1 (fr) * 1974-11-14 1976-06-11 Af Hydraulics Perfectionnements apportes a des dispositifs a commande hydraulique
DE2731122A1 (de) * 1977-07-09 1979-01-25 Hausherr & Soehne Maschf Schaltungsanordnung fuer eine kolbenpumpe zur foerderung von dickstoffen
EP0027654A1 (fr) * 1979-10-20 1981-04-29 SCHLECHT, Karl Pompe à béton avec un tiroir à soulagement hydraulique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3327641A (en) * 1965-03-08 1967-06-27 Air Placement Equipment Co Inc Concrete pump
LU56224A1 (fr) * 1968-01-03 1969-04-22
FR2291374A1 (fr) * 1974-11-14 1976-06-11 Af Hydraulics Perfectionnements apportes a des dispositifs a commande hydraulique
DE2731122A1 (de) * 1977-07-09 1979-01-25 Hausherr & Soehne Maschf Schaltungsanordnung fuer eine kolbenpumpe zur foerderung von dickstoffen
EP0027654A1 (fr) * 1979-10-20 1981-04-29 SCHLECHT, Karl Pompe à béton avec un tiroir à soulagement hydraulique

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997018395A1 (fr) * 1995-11-13 1997-05-22 Putzmeister Aktiengesellschaft Procede et dispositif pour commander une pompe a liquides epais a deux cylindres
EP0931934A1 (fr) * 1998-01-27 1999-07-28 Dosiertechnik und Pneumatik AG Dopag Dispositif de pompage des matériaux visqueux
WO2003001062A1 (fr) * 2001-06-22 2003-01-03 Viking Technology As Pompe a haute pression
WO2006103219A1 (fr) * 2005-03-29 2006-10-05 Stefano Baiardo Circuit hydraulique pour une unite de pompage de beton
EP1847710A1 (fr) * 2006-04-20 2007-10-24 COMPAGNIA ITALIANA FORME ACCIAIO S.p.A. Systeme à circuit ouvert de distribution oleodynamique pour une pompe à béton.
CN104196786A (zh) * 2014-07-29 2014-12-10 徐州五洋科技股份有限公司 一种矿用湿喷机用全液压控制泵送液压系统
CN104196786B (zh) * 2014-07-29 2017-06-20 徐州五洋科技股份有限公司 一种矿用湿喷机用全液压控制泵送液压系统
CN104329306A (zh) * 2014-10-31 2015-02-04 徐州徐工施维英机械有限公司 一种液压控制系统、方法和泵
WO2020120234A1 (fr) * 2018-12-14 2020-06-18 Schwing Gmbh Pompe à piston et procédé pour faire fonctionner une pompe à piston
US11891987B2 (en) 2018-12-14 2024-02-06 Schwing Gmbh Piston pump and method for operating a piston pump

Also Published As

Publication number Publication date
EP0167635B1 (fr) 1989-09-27
ATE46745T1 (de) 1989-10-15
DE3479911D1 (en) 1989-11-02

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