EP3265680B1 - Pompe à piston à deux cylindres - Google Patents

Pompe à piston à deux cylindres Download PDF

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Publication number
EP3265680B1
EP3265680B1 EP16711787.8A EP16711787A EP3265680B1 EP 3265680 B1 EP3265680 B1 EP 3265680B1 EP 16711787 A EP16711787 A EP 16711787A EP 3265680 B1 EP3265680 B1 EP 3265680B1
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EP
European Patent Office
Prior art keywords
cylinder
operating mode
cylinder piston
pump
piston pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16711787.8A
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German (de)
English (en)
Other versions
EP3265680A1 (fr
Inventor
Thorsten Koch
Rudolf Rabsahl
Joseph SCHNITTKER
Manfred Schwarz
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.)
Friedrich Wilhelm Schwing GmbH
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Friedrich Wilhelm Schwing GmbH
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Publication date
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Publication of EP3265680A1 publication Critical patent/EP3265680A1/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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type

Definitions

  • the invention relates to a two-cylinder piston pump, for example for pumping thick materials, such. Sewage sludge or concrete, such as those used in truck-mounted concrete pumps, stationary concrete pumps or towed concrete pumps.
  • a two-cylinder piston pump which is operated with hydraulic drive cylinders, which are usually designed as a differential cylinder, can be operated in a piston-side and a rod-side mode. While hydraulic pressure is applied to the full surfaces of the hydraulic pistons in the hydraulic cylinder during piston-side operation, only a partial area of the pistons is acted upon during rod-side operation because the surface on which the piston rod is attached to the hydraulic piston is not effective for the hydraulic pressure in the rod-side drive. As a result, in the case of rod-side operation, the pump is operated with a higher delivery volume but a low delivery pressure, while the piston-side operation is carried out with a higher delivery pressure, but with a lower delivery volume.
  • a change in the operating mode is useful, for example, in stationary concrete pumps in the construction of a building in which at the beginning of concrete application concrete with higher flow, but low discharge pressure is applied in lower-lying Stockwecke.
  • a higher delivery pressure may be necessary to reach the concrete through the delivery line to a corresponding height from reaching a certain height of the structure Building height to pump, but for which a lower concrete yield is accepted.
  • the hydraulic oil is passed into the chamber 54 instead of into the chamber 53, whereby first the piston 9 of the second differential cylinder 23 is driven and the hydraulic oil via the bridge oil line 13 from the rod-side chamber 54 of the second hydraulic cylinder 23 is conducted into the rod-side chamber 53 of the first hydraulic cylinder 22.
  • FIG. 2 circuit shown in principle includes a switching block 14 which is connected via hydraulic lines 15, 16, 17, 18 with the chambers of the differential cylinder 22, 23.
  • the arrows in FIG. 2 show the hydraulic oil flow in the piston-side mode of operation of the two-cylinder piston pump 1.
  • a suitable switching device in the switching block 14 of the hydraulic oil flow switched so that the two-cylinder piston pump 1 is operated rod side.
  • the DE 10 2004 015 419 A1 relates to a two-cylinder slurry pump, wherein the drive cylinder on the bottom side via hydraulic lines of the hydraulic circuit by means of a reversing pump can be acted upon with pressure oil and hydraulically connected to each other at its rod end via a swing oil line.
  • the direction of movement of the drive piston can be reversed by reversing the flow direction of the reversing pump via a reversing device.
  • DE 30 30 005 A1 discloses a concrete pump with two counter-sucking or pressing pump cylinders whose delivery piston either piston or rod side pressure lines are acted upon by pressure medium.
  • a disadvantage of such a switching device according to the prior art is that often tightness problems due to the many joints for the hydraulic lines occur and high pressure losses occur due to the many system components that complicates an economical application of such hydraulic circuits.
  • many hydraulic lines are required, which cause a high installation and cost and the tubing effort increases the risk of leaks.
  • a hydraulically driven two-cylinder piston pump comprises a first hydraulically operated differential cylinder with a piston-side chamber and a rod-side chamber, which drives a first delivery piston via a first piston rod; a second differential cylinder having a piston-side chamber and a rod-side chamber, which drives a second delivery piston via a second piston rod, and a switching device which adjusts a piston or rod-side mode of operation of the two-cylinder piston pump by switching the hydraulic oil flow to the chambers, wherein the switching device the bottoms of the piston-side chambers of the differential cylinder is arranged as a bridge-forming connection between the differential cylinders.
  • the invention is characterized the switching device comprises passage channels for the hydraulic oil for driving the differential cylinders via which the piston-side chambers of the differential cylinders without hydraulic oil lines are connected to the switching device.
  • the two-cylinder piston pump according to the invention has the advantage over the prior art that on the one hand a particularly non-positive connection of the components with each other results, so that not with damage (eg cracking, fractures) at or in the region of the connection points between the differential cylinders and the switching device is to be expected.
  • the two-cylinder piston pump according to the invention over the prior art has the advantage that the risk of bursting hydraulic hoses is greatly reduced because hydraulic hoses are only necessary between the rod-side chambers of the differential cylinder and the Umschaltblock. In addition, the effort for assembly and the screwing of the hydraulic hoses is greatly reduced.
  • the switching device is attached by means of adapter flanges to the bottoms of the differential cylinder.
  • the particular advantage of this embodiment of the invention is that a modification of the switching device is omitted if the switching device to be mounted on differential cylinders with different diameters than on the adapter flanges with different diameters, which are respectively adapted to the inner diameter of the piston side chambers of the differential cylinder can the switching device of the same type are adapted to differential cylinders with different diameters.
  • the adapter flanges can be arranged in corresponding recesses in the Umschaltblock The recesses in the Umschaltblock increase the stability of the assembly and at the same time relieve the attachment / screwing the adapter flanges.
  • the hydraulically driven two-cylinder piston pump may comprise flanges arranged on the differential cylinders with which the differential cylinders are fastened, preferably screwed, to the switching device.
  • flanges allow easy attachment / Screwing the differential cylinder with the switching device.
  • the flanges are for example mounted on the tubular differential cylinder by means of a welded or screwed connection or already form a unit with the cylinder tubes during production.
  • the bottoms of the piston-side chambers of the differential cylinders include fitting seats in which the adapter flanges are fitted.
  • the adapter flanges optimally positively absorb the radial forces emanating from the differential cylinders and thus avoid the transverse force load of the flange bolts between the differential cylinders and the control block.
  • the adapter flanges increase the mechanical strength / durability of the connection between the differential cylinders and the switching device.
  • expansion sleeves for receiving screws are arranged on the flanges. In this way, a secure screw connection between the flanges and the switching device can be ensured.
  • the expansion sleeves may use longer screws and the expansion sleeve will absorb some of the strain, e.g. by thermal loads and pressure loads, in the material and thus acts as a buffer, whereby the tightness of the high-pressure cylinder chambers is always guaranteed and high safety standards are met.
  • a further preferred embodiment of the invention is characterized in that the switching means comprises an input for a control line for switching the operating mode of the two-cylinder piston pump.
  • This control line can be designed, for example, hydraulically or electrically.
  • the operating mode of the two-cylinder piston pump is switched via a pilot valve, which is controlled via the control line.
  • This pilot valve is preferably held by a locking device even when the control line is switched off, or in the absence of a signal on the control line, for example when the pump is switched off, in its last switching position. This will Prevents, for example, when restarting the pump unintentionally in a different operating mode than the last used operating mode is started.
  • the invention is characterized by a method that controls the changeover of the mode of operation of the two-cylinder piston pump during commissioning of the pump. Another method relates to the changeover of the operating mode during the ongoing pumping process.
  • FIGS. show a particularly preferred embodiment of the invention.
  • the invention is not limited to the embodiment shown.
  • the invention includes, as far as is technically feasible, any combination of the technical features that are listed in the claims or described in the description as being relevant to the invention.
  • the two-cylinder piston pump 1 according to FIG. 1 comprises two delivery cylinders 2, 3 with delivery pistons 4, 5 which are respectively driven by piston rods 6, 7 of differential cylinders 22, 23 with hydraulic pistons 8, 9.
  • a water tank 10 is arranged, in which there is water, which flows around the delivery piston 8, 9 at the rear to cool the piston and lubricate.
  • Hydraulikzu- / drain hoses 11, 12 are connected, via which the hydraulic oil for driving the differential cylinder 22, 23 is fed by a hydraulic pump, not shown.
  • the rod-side chambers 53, 54 are connected to one another via a bridge oil line 13.
  • a bridge oil line 13 At the end of the piston-side chambers 51, 52 is in each case a cylinder bottom 49, 50.
  • the arrows in FIG. 1 show the flow direction of the hydraulic oil for the piston-side drive of the two-cylinder piston pump. 1
  • FIG. 2 shows a two-cylinder piston pump 1 accordingly FIG. 1 , which is equipped with a switching device 14 for switching between rod and bottom-side mode.
  • the switching device 14 consists in The rule of a solid metal block in the control valves and passageways are introduced for arranged in the switching device 14 hydraulic valves and is therefore also referred to as a control block or switching block.
  • the terms switching block and switching device 14 are used synonymously in the following.
  • the switching block 14 includes a hydraulic circuit that is adapted to control the hydraulic oil flow to the cylinder chambers 51, 52, 53, 54 so that a corresponding operating mode can be set.
  • the hydraulic oil supply and discharge lines 11, 12 are connected to the switching block 14.
  • the arrows point in FIG. 2 the flow direction of the hydraulic oil and the moving direction of the delivery pistons for a piston-side operation of the two-cylinder piston pump 1.
  • FIG. 3 shows an embodiment according to the invention of a two-cylinder piston pump 1, which comprises a first differential cylinder 22 with a piston-side chamber 51 and a rod-side chamber 53, wherein the differential cylinder 22 drives a first delivery piston 4 via a first piston rod 6. Furthermore, the two-cylinder piston pump 1 comprises a second differential cylinder 23 with a piston-side chamber 52 and a rod-side chamber 54, which drives a second delivery piston 5 via a second piston rod 7.
  • the two-cylinder piston pump 1 further comprises a switching device 14 which sets by switching the hydraulic oil flow to the chambers 51, 52, 53, 54 of the differential cylinder 22, 23 a piston or rod-side operation of the two-cylinder piston pump 1.
  • the switching device 14 is arranged on the bottoms 48, 49 of the piston-side chambers 51, 52 of the differential cylinder 22, 23 as a bridge-forming connection between the differential cylinders 22, 23.
  • the switching block 14 includes two passageways 28, 29 (see also FIG Figure 6 ), via which the piston-side chambers 51,52 of the differential cylinders 22, 23 are connected to the switching device 14 directly. Via the passage channels 28, 29, the hydraulic oil is passed directly from the switching device 14 to the piston side chambers 51, 52 of the differential cylinder 22, 23, resulting in an error-prone Hydraulikverschlauchung according to the prior art between the switching block 14 and the piston-side chambers 51, 52 can be avoided.
  • the hydraulic oil which is supplied from a hydraulic pump (not shown) at high pressure via the hydraulic oil pipe 11 into the switching block 14, is transferred from the switching block 14 into the piston-side chamber 51 of the differential cylinder 22 directed.
  • the chamber 51 causes the larger volume in connection with the larger piston area than the rod-side drive (see Figure 4 ), that the delivery piston 4 with high force, but relatively slowly in the first delivery cylinder 2 is pushed to the left.
  • the hydraulic oil in the rod-side chamber 53 is conveyed in the course of the movement via the hydraulic line 16, the switching block 14 and the hydraulic line 18 in the rod-side chamber 54 of the differential cylinder 23 and causes the hydraulic piston 9 is pushed to the right.
  • the hydraulic oil is discharged from the piston-side chamber 52 of the differential cylinder 23 via the switching block 14 and the hydraulic line 12.
  • the delivery cylinder 2 is located in FIG. 3 in the pumping mode while the delivery cylinder 3 is in the intake mode.
  • the hydraulic oil flow is switched over and the hydraulic oil flows from the hydraulic pump through the line 12 into the switching block 14 and drives First, the hydraulic piston 9 via the piston-side chamber.
  • This mode causes now the delivery cylinder 3 operates in the pumping mode, while the delivery cylinder 2 operates in the intake mode.
  • FIG. 4 is the two-cylinder piston pump 1 off Fig. 3 shown, in which the switching block 14 is changed over the control line 19 from the piston-side mode in the rod-side mode of operation of the two-cylinder piston pump 1. That is in the Figure 4 Hydraulic oil coming from the hydraulic supply line 11 is first guided via the switching block 14 into the rod-side chamber 53 of the differential cylinder 22, whereby the delivery cylinder 2 is in the intake mode with the delivery piston 4 at a comparatively high speed but less force. In this case, the hydraulic oil is guided from the piston-side chamber 51 of the differential cylinder 22 via the switching block 14 in the piston-side chamber 52 of the differential cylinder 23 and drives the hydraulic piston 9 and the delivery piston 5 in the pumping mode. After switching the hydraulic oil flow, the pumping direction of the delivery piston of the two-cylinder piston pump 1 is reversed, the rod-side drive is maintained as long as the switching block 14 is not switched over the control line 19 in the piston-side mode.
  • FIG. 5 shows a perspective view of the switching block 14 according to the invention with mounted adapter flanges 20, 21 with the passage channels 28, 29.
  • the adapter flanges 20, 21 are inserted into corresponding recesses in the Umschaltblock 14 and preferably screwed with six screws with the Umschaltblock.
  • the adapter flanges 20, 21 could also be screwed onto the switching block 14 without the recesses in the switching block 14.
  • the recesses in the Umschaltblock 14 increase the stability of the assembly and at the same time relieve the screwing of the adapter flanges 20, 21.
  • Inlet / outlet channels 26 are shown for the hydraulic lines.
  • On top of the switching block 14 is the housing of a pilot valve 33 (see also FIG. 8 ), which is acted upon by the control line 19 electronically with the control signal for the mode setting.
  • FIG. 6 shows the switch block 14 together with the differential cylinders 22, 23, which are preferably screwed on flanges 24, which are preferably connected by means of welded joints 26 to the differential cylinders 22, 23 attached to the switching block 14.
  • the screwing of the flanges 24 with the switching block 14 is not shown in this drawing, there are only the boreholes 25 visible for the screw connection.
  • the flanges 24 may for example also be screwed to the cylinder tubes or made in one piece.
  • FIG. 7 shows in a perspective cross section, the connection of the differential cylinder 22 via the adapter flange 20 with the switching block 14.
  • a fitting seat 55 is provided, so that the adapter flange 20 is positively fitted into the differential cylinder 22.
  • two sealing rings 30 are inserted into grooves in the adapter flange 20.
  • the adapter flange 20 has on the switching block 14 side facing an outer diameter d1, which fits into a prepared recess in the switching block 14.
  • the adapter flange 20 On the side facing the differential cylinder 22, the adapter flange 20 has the diameter d2, which is adapted to the inner diameter of the interference fit 55 of the differential cylinder 22.
  • the switching block 14 is preferably also equipped with fits / fits with the diameter d1 for receiving the adapter flanges 20, 21 in the recesses provided for this purpose.
  • a bore is centrally arranged through which the hydraulic oil from the passage 28 of the switching block 14 in the piston-side chamber 51 of the differential cylinder 22 flows.
  • the switching block 14 can be operated together with differential cylinders 22, 23 of different diameters.
  • the center of the differential cylinder is often equal to each other, so that a switching block 14 of the same type to different differential cylinders 22, 23 can be connected.
  • the differential cylinder 22 is screwed over the welded flange 24 with the switching block 14 with screws 27.
  • the screw connections have expansion sleeves 36, which increase the safety of the screw connection even under high pressure and high thermal loads, because the hydraulic pressure can be up to more than 400 bar for concrete pumps.
  • FIG. 8 is a possible, arranged in Umschaltblock 14, hydraulic circuit shown, which is adapted to make the changeover of the mode of operation of the two-cylinder piston pump 1.
  • the hydraulic circuit mainly comprises six cartridge valves 41-46, which are controlled by an electromagnetically controlled pilot valve 33. Hydraulic oil is supplied to the pilot valve 33 for controlling the cartridge valves 41-46 via the control oil inlet 35 secured with a check valve 34. About the Hydrauliköllein- / outputs 47 and 48, the necessary for the operation of the differential cylinder 22,23 hydraulic oil to the switching block 14 is added or removed.
  • the cartridge valves 41-45 control the hydraulic oil flow to the piston / rod side chambers of the differential cylinders in the respective set operating mode.
  • the cartridge valve 46 is dimensioned slightly larger than the other cartridge valves 41-45.
  • the valve 46 opens or closes the connection between the two piston-side chambers 51, 52 of the differential cylinder 22, 23 via the in FIG. 8 schematically illustrated passageways 28, 29th
  • the pilot valve 33 is in FIG. 8 set so that the cartridge valves 41,45 and 44 are closed by the control oil pressure via the control line 32 and the cartridge valves 42, 43 and 46 are opened spring loaded. By this valve position, the rod-side mode of operation of the two-cylinder piston pump 1 is set.
  • the pilot valve 33 is reversed in a known manner by means of two electromagnets which are located laterally on the valve body.
  • a mechanical locking device 56 ensures that the pilot valve 33 remains in the last adjusted position even when the control line 19 is switched off (for example after the entire machine has been switched off).
  • the pistons 8, 9 move faster than in the piston-side mode, and therefore, the amount of hydraulic oil to be passed through the cartridge valve 46 between the piston-side chambers is particularly large, which requires a larger sizing of this valve.
  • the hydraulic lines 16, 18 and the hydraulic ports 47, 48 are shown here in duplicate, because the amount of hydraulic oil to be passed through is so great that a simple tubing with thicker hydraulic lines would not be practical, so that a parallel tubing with thinner hydraulic lines is provided.
  • FIGS. 9 and 10 show flowcharts for methods for controlling a two-cylinder piston pump 1, which relates to the switching operation between the rod-side and the piston-side mode.
  • step 100 the operating mode set in the last operation of the pump 1 is initially determined, for example based on a memory entry, in step 101.
  • step 102 the operator is asked, for example via a display on the control of the machine or on a remote control, whether the pump is to be used in the last set operating mode, which is also displayed, at the start again. If the operating mode is to be maintained, the pump is started in step 105 in this operating mode via step 103. If the operating mode is to be changed because the pumping conditions have changed (eg higher or lower concrete application location during the new startup), the operating mode is switched over in step 104 by switching the pilot valve 33, and then the pump is started in step 105.
  • the process could also be designed so that the operator of the pump can relatively easily acknowledge the maintenance of the operating mode in step 102, while the changeover of the operating mode requires a separate acknowledgment which expressly informs the operator of the changed pumping behavior. It is also conceivable that the operating mode is maintained in step 102 after a certain waiting time (for example 5 or 10 seconds) and the pump is automatically started in step 105 if the operator makes no input within the waiting time.
  • a certain waiting time for example 5 or 10 seconds
  • FIG. 10 shows a method for switching the operating mode of the pump 1 during operation, in which the pressure of the pumped medium or the hydraulic pressure of the hydraulic oil at a suitable location, for example in one or both delivery cylinders 2, 3 in one or both differential cylinders 22, 23 or Switching block 14 is measured to switch the pump in a suitable operating mode.
  • step 110 the pump 1 is in normal pumping operation.
  • the pumping pressure is queried in step 111 and, in step 113, based on the set operating mode 112, it is checked whether the pumping pressure is within a tolerance range for the operating mode.
  • the pumping pressure should not exceed a certain tolerance limit, because from this limit u.U. the piston side operation is more suitable so as not to overload the hydraulic system.
  • the operator is first asked in step 114, if the mode is to be maintained. If so, pumping continues normally in step 110.
  • the pilot valve 33 is switched over and the pumping operation is continued in step 117 with the operating mode changed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)

Claims (12)

  1. Pompe à pistons à deux cylindres (1) à entraînement hydraulique, comportant :
    - un premier cylindre différentiel (22) doté d'une chambre (51) côté piston et d'une chambre (53) côté tige, qui entraîne un premier piston de refoulement (4) par le biais d'une première tige de piston (6),
    - un deuxième cylindre différentiel (23) doté d'une chambre (52) côté piston et d'une chambre (54) côté tige, qui entraîne un deuxième piston de refoulement (5) par le biais d'une deuxième tige de piston (7),
    - un dispositif de commutation (14) qui, par commutation du flux d'huile hydraulique vers les chambres (51, 52, 53, 54) des cylindres différentiels (22, 23), règle un mode de fonctionnement côté piston ou côté tige de la pompe à pistons à deux cylindres (1), dans laquelle le dispositif de commutation (14) est disposé sur les fonds (48, 49) des chambres (51, 52) côté piston des cylindres différentiels (22, 23) en tant que liaison formant pont entre les cylindres différentiels (22, 23),
    caractérisée en ce que
    le dispositif de commutation (14) comporte des canaux de passage (28, 29) pour l'huile hydraulique pour l'entraînement des cylindres différentiels (22, 23), par le biais desquels les chambres (51, 52) côté piston des cylindres différentiels (22, 23) sont reliées au dispositif de commutation (14) sans conduites d'huile hydraulique.
  2. Pompe à pistons à deux cylindres (1) à entraînement hydraulique selon la revendication 1, caractérisée par des brides (24) disposées sur les cylindres différentiels (22, 23), à l'aide desquelles les cylindres différentiels (22, 23) sont fixés au dispositif de commutation (14), de préférence vissés sur celui-ci.
  3. Pompe à pistons à deux cylindres (1) à entraînement hydraulique selon la revendication 1 ou 2, caractérisée par des brides d'adaptation (20, 21) disposées entre le dispositif de commutation (14) et les fonds (49, 50) des cylindres différentiels (22, 23).
  4. Pompe à pistons à deux cylindres (1) à entraînement hydraulique selon la revendication 3, caractérisée en ce que les brides d'adaptation (20, 21) sont insérées dans des logements à justement serré (55) qui sont ménagés dans les fonds (49, 50) des cylindres différentiels (22, 23) .
  5. Pompe à pistons à deux cylindres (1) à entraînement hydraulique selon la revendication 2, caractérisée en ce que des douilles extensibles (36) servant à recevoir des vis sont disposées sur les brides (24).
  6. Pompe à pistons à deux cylindres (1) à entraînement hydraulique selon l'une des revendications précédentes, caractérisée en ce que le dispositif de commutation (14) comporte une entrée pour une ligne de commande (19) pour la commutation du mode de fonctionnement.
  7. Pompe à pistons à deux cylindres (1) à entraînement hydraulique selon la revendication 6, caractérisée par une soupape pilote (33) pour la commutation du mode de fonctionnement du dispositif de commutation (14), laquelle soupape pilote peut être commandée par la ligne de commande (19).
  8. Pompe à pistons à deux cylindres à entraînement hydraulique selon la revendication 7, caractérisée par un dispositif d'encliquetage (56) qui maintient la soupape pilote (33) dans sa position de commutation lorsque la ligne de commande (19) est coupée.
  9. Dispositif de commutation (14), le dispositif de commutation (14) étant conçu pour régler le mode de fonctionnement d'une pompe à pistons à deux cylindres (1) selon les revendications précédentes.
  10. Procédé de fonctionnement d'une pompe à pistons à deux cylindres (1) à entraînement hydraulique selon l'une des revendications précédentes, caractérisé en ce qu'avant le démarrage de la pompe à pistons à deux cylindres (1), le mode de fonctionnement réglé en dernier est déterminé (101), une interrogation a lieu pour déterminer si le mode de fonctionnement réglé en dernier doit être utilisé pour le démarrage de la pompe (102), et en ce qu'en fonction de cela, le mode de fonctionnement est maintenu ou commuté (104) avant que la pompe ne démarre (105).
  11. Procédé selon la revendication 10, caractérisé en ce que le mode de fonctionnement réglé en dernier est prédéfini en tant que mode de fonctionnement lors de la mise en marche de la pompe.
  12. Procédé de fonctionnement d'une pompe à pistons à deux cylindres à entraînement hydraulique selon l'une des revendications 1 à 8, caractérisé en ce que pendant le fonctionnement de la pompe à pistons à deux cylindres (1), la pression de pompe est déterminée (112) ; on détermine si la pression de pompe déterminée est comprise dans les limites d'une tolérance prédéfinie pour le mode de fonctionnement réglé (112, 113), et une interrogation a lieu pour déterminer si le mode de fonctionnement doit être maintenu (114), et en ce qu'en fonction du résultat de l'interrogation, le mode de fonctionnement est maintenu ou commuté (115).
EP16711787.8A 2015-03-05 2016-03-07 Pompe à piston à deux cylindres Active EP3265680B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015103180.9A DE102015103180A1 (de) 2015-03-05 2015-03-05 Zweizylinder-Kolbenpumpe
PCT/EP2016/054779 WO2016139367A1 (fr) 2015-03-05 2016-03-07 Pompe à pistons à deux cylindres

Publications (2)

Publication Number Publication Date
EP3265680A1 EP3265680A1 (fr) 2018-01-10
EP3265680B1 true EP3265680B1 (fr) 2019-10-09

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EP16711787.8A Active EP3265680B1 (fr) 2015-03-05 2016-03-07 Pompe à piston à deux cylindres

Country Status (4)

Country Link
US (1) US20180045186A1 (fr)
EP (1) EP3265680B1 (fr)
DE (1) DE102015103180A1 (fr)
WO (1) WO2016139367A1 (fr)

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US10315850B2 (en) 2017-07-13 2019-06-11 1875452 Alberta Ltd. Proppant conveyor systems and methods of use
DE102018208263A1 (de) 2018-05-25 2019-11-28 Putzmeister Engineering Gmbh Vorrichtung zur Förderung von Dickstoff
DE102018129363A1 (de) * 2018-11-21 2020-05-28 Liebherr-Betonpumpen Gmbh Betonpumpenaggregat
US11891987B2 (en) 2018-12-14 2024-02-06 Schwing Gmbh Piston pump and method for operating a piston pump
DE102019120825A1 (de) * 2019-08-01 2021-02-04 Putzmeister Engineering Gmbh Umschalteinrichtung für eine Betonpumpe
WO2023230238A1 (fr) * 2022-05-26 2023-11-30 Schwing Bioset, Inc. Pompe à pistons multiples à écoulement continu

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2433318A1 (de) * 1974-07-11 1976-01-22 Scheele Maschf W Steuervorrichtung fuer eine druckmittelbetaetigte betonpumpe
US4194529A (en) * 1976-07-15 1980-03-25 W-K-M Wellhead Systems, Inc. Control valve having integral visual indicator for fluid safety systems
DE2925674C2 (de) 1979-06-26 1986-01-23 Maschinenfabrik Walter Scheele GmbH & Co KG, 4750 Unna-Massen Hydraulischer Antrieb für eine Zweizylinder-Betonpumpe
DE3030005A1 (de) * 1980-08-08 1982-02-18 Maschinenfabrik Walter Scheele GmbH & Co KG, 4750 Unna-Massen Betonpumpe mit zwei pumpenzylindern
US5388965A (en) * 1990-10-10 1995-02-14 Friedrich Wilhelm Schwing Gmbh Sludge pump with monitoring system
US4477232A (en) * 1983-01-10 1984-10-16 Mayer James R Hydraulically actuated reciprocating piston pump
ATE139824T1 (de) * 1992-03-21 1996-07-15 Schwing Gmbh F Dickstoffpumpe
US5330327A (en) * 1993-04-27 1994-07-19 Schwing America, Inc. Transfer tube material flow management
DE4403213A1 (de) * 1994-02-03 1995-08-10 Putzmeister Maschf Einrichtung zur Antriebssteuerung einer Zweizylinder-Dickstoffpumpe
DE19744986C1 (de) * 1997-10-13 1999-02-11 Karl Hehl Formschließeinheit für eine Spritzgießmaschine
DE102004015419A1 (de) * 2004-03-26 2005-10-13 Putzmeister Ag Vorrichtung und Verfahren zur Steuerung einer Dickstoffpumpe
CN101793246B (zh) * 2010-03-16 2013-08-28 三一汽车制造有限公司 混凝土泵送结构和混凝土泵送结构的控制方法
EP2895714B1 (fr) * 2012-06-26 2017-06-07 Deutz AG Moteur à combustion interne muni d'une douille d'écartement à centrage central

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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US20180045186A1 (en) 2018-02-15
EP3265680A1 (fr) 2018-01-10
WO2016139367A1 (fr) 2016-09-09
DE102015103180A1 (de) 2016-09-08

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