EP0668441A1 - Commande d'entraînement pour une pompe à deux cylindres pour liquides épais - Google Patents

Commande d'entraînement pour une pompe à deux cylindres pour liquides épais Download PDF

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Publication number
EP0668441A1
EP0668441A1 EP95101113A EP95101113A EP0668441A1 EP 0668441 A1 EP0668441 A1 EP 0668441A1 EP 95101113 A EP95101113 A EP 95101113A EP 95101113 A EP95101113 A EP 95101113A EP 0668441 A1 EP0668441 A1 EP 0668441A1
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EP
European Patent Office
Prior art keywords
valve
pressure
drive
cylinder
control
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
EP95101113A
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German (de)
English (en)
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EP0668441B1 (fr
Inventor
Bruno Neuburger
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.)
Putzmeister Concrete Pumps GmbH
Original Assignee
Putzmeister Werk Maschinenfabrik GmbH
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Publication of EP0668441A1 publication Critical patent/EP0668441A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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 invention relates to a device for the drive control of a two-cylinder thick matter pump, the pump pistons of which can be driven in counter-clocking filling and delivery strokes by means of one drive cylinder each, which are hydraulically connected in series, and with the further generic features mentioned in the preamble of claim 1 .
  • Such a device for drive control is known in connection with a concrete pump from DE 38 14 824 A1.
  • a hydraulically controllable changeover valve is provided for the cyclical control of the filling and delivery strokes carried out alternately by the two delivery cylinders, which changeover valve can be switched between alternative functional positions 0 and I by alternately acting with control pressure and pressure relief, in which the piston in each case one of the drive cylinders executes the working strokes corresponding to the filling stroke of the conveying cylinder driven by the latter and the pistons of the other drive cylinder perform the working strokes corresponding to the conveying stroke of the conveying cylinder driven thereby.
  • two pressure-controlled pilot valves are provided which alternately emit a control pressure pulse to one of the two control chambers of the main changeover valve whenever the piston moves one of the two drive cylinders into its end of the filling stroke of the feed cylinder driven by it or the end positions corresponding to the end of the delivery stroke of this delivery cylinder.
  • the level of these control pressure pulses is determined by the pressure difference that can be tapped in the respective end position of the drive cylinder piston between the bottom-side and the rod-side drive pressure space of the respective drive cylinder as soon as and as long as the drive cylinder piston assumes a position between radial pressure-sensing bores, one of which in each case must be run over by the piston.
  • a latching device is provided, the holding force of which must be overcome by the control pressure pulses being applied to the control chambers.
  • a further disadvantage is that in order to detect the pressure difference between its bottom-side and its rod-side drive pressure chamber in the two possible end positions of the piston of the drive cylinder which is used for stroke monitoring, it is necessary that the drive piston must pass over a radial housing bore , which inevitably leads to wear of the piston seals, which can only be kept fairly low by using expensive and expensive piston seals in order to achieve acceptable service life of the drive cylinder. Nevertheless, relatively frequent replacements of piston seals consisting of resistant and relatively hard material are required, which requires additional work and undesirable downtimes of the pump.
  • the pilot valves provided for actuating the changeover valve are at least one of the two by the piston (s) hydraulic drive cylinder mechanically against the restoring force developed by a restoring element, which urges the respective pilot valve into its basic position, designed 2-position valves which can be hydraulically locked in the switching position assumed by the mechanical actuation by the drive cylinder piston by pressurizing a control chamber.
  • a mechanical latching device that supports its function and is effective with moderate holding force can be provided, which provides a force-locking fixation of the hydraulically locked switching position.
  • the hydraulic locking and unlocking of the pilot valves is achieved in a simple manner in that the pressurization of the control chamber of the pilot valve to be locked in each case takes place via a flow path released in the basic position of the other pilot valve, via which the output pressure of the pressure supply unit into the control chamber of the valve to be locked can be coupled in, and that the pressure relief of the control chamber of the pilot valve, in the basic position of which the control chamber of the pilot valve to be locked is acted upon by control pressure, takes place via a flow path of the pilot valve to be locked or locked, which is released by the mechanical actuation of this pilot valve.
  • pilot valves In the construction of the pilot valves and the way in which they are actuated, which are indicated by the features of claim 2, these can be mounted in a position favorable for assembly outside the housing of the drive cylinder (s) on the floor and / or the rod-side end wall of the cylinder housing.
  • the two pilot valves are each mounted on the outside of the bottom of the respective drive cylinder, they can, as proposed according to claim 4, also with the changeover valve and / or an ON / OFF switching valve provided for initiating and ending the conveying operation of the thick matter pump to form a control valve block be summarized, which can be attached to the two drive cylinders as a pre-assembled unit.
  • both control valves on a drive cylinder indicated by the features of claim 5 can also be expedient, e.g. when the pump is mounted on a vehicle and the hydraulic control elements are to be accessible from a vehicle side.
  • Simple pilot valves designed as 3/2-way valves of the same type are suitable for both applications.
  • An ON / OFF switching valve designed according to claim 11 is suitable both as a manually controlled valve and also as an electrically controllable valve for integration into a control valve unit comprising the pilot valves and the changeover valve.
  • hydraulically parallel pressure relief valve to the pressure supply pump can also be used for a needs-based feeding of rocking oil, which is done such that a maximum amount of rocking oil is fed into the hydraulically connected drive pressure chambers of the drive cylinders, so that the pistons of both Drive cylinders reach their associated end positions and then one of the two drive cylinders is subjected to drive pressure in such a way that the portion of the rocking oil it absorbs is displaced back into the reservoir of the pressure supply unit via the pressure relief valve.
  • the thick matter pump designated overall by 10 in FIG. 1, is designed as a piston pump with two linear delivery cylinders 11 and 12, for driving two hydraulic drive cylinders 13 and 14 designed as double-acting differential cylinders, the pistons 16 and 17 of which are provided via piston rods 18 and 19 with the pistons 21 and 22 of the feed cylinders 11 and 12 - each individually - are rigidly connected.
  • the conveying cylinders 11 and 12 of the thick matter pump 10 can be driven by means of the hydraulic drive cylinders 13 and 14 in such a "push-pull" manner that their pistons 21 and 22 alternately carry out filling and conveying strokes, through which the material to be conveyed from a material feed container (not shown)
  • a material feed container not shown
  • a slide element which communicates the communicating connection of its pump chamber 23 or 24 with the material feed container during the filling stroke of the respective delivery cylinder 11 or 12, and shuts off this connection again during the delivery stroke of the respective delivery cylinder 11 or 12, and the pipe switch 27, which in turn provides the communicating connection of the delivery line 26 mediated with the pump chamber 23 or 24 of the delivery cylinder 11 or 12, the piston 21 or 22 of which carries out the delivery stroke, can be driven together, for example by means of a further, not shown, double-acting drive cylinder.
  • the two delivery cylinders 11 and 12 can, however, also be designed in the manner of piston pumps, which are each provided with an inlet and an outlet check valve, which act as a ball or plate back impact valves can be formed.
  • a hydraulic control unit, designated 34 overall is provided only schematically in FIG. 1, in circuit-specific details in FIG. 2, to which reference is now also made , in the sense of a sequential control, a periodically changing connection of the rod-side drive chambers 32 and 33 of the drive cylinders 13 and 14 to the high-pressure outlet 36 of a pressure supply pump 37 and its pressureless reservoir 38 mediates in such a way that during that a rod-side drive chamber 32 or 33 of the respective Drive cylinder 13 or 14 is exposed to the high output pressure of the pressure supply pump 37, the rod-side drive chamber 33 or 32 of the other drive cylinder 14 or 13 is relieved of pressure to the unpressurized reservoir 38 of the pressure supply unit.
  • the bottom-side drive chambers 39 and 41 are permanently connected to one another by a pressure line 42, the orifices 43 and 44, via which the pressure line 42 opens into the bottom-side drive chambers 39 and 41 of the two drive cylinders 13 and 14, in the immediate vicinity of the respective cylinder base 46 and 47 or are arranged on the cylinder base itself and cannot be run over by the pistons 16 and 17 of the two drive cylinders 13 and 14 when they enter their end positions on the base side.
  • This changeover valve 48 via which in the conveying operation of the thick matter pump 10, which essentially consists of the two drive cylinders 13 and 14 existing hydraulic power circuit, is formed in the illustrated embodiment as a pressure-controlled 4/2-way valve, which by filling alternately and in time - and delivery strokes of the delivery cylinders 11 and 12 and their drive cylinders 13 and 14 alternating pressurization and discharge of two control chambers 49 and 51 can be switched between its possible functional positions 0 and I; In one of these functional positions, which is also used as the basic position 0 for the start-up operation of the thick matter pump 10, the changeover valve 48 is pushed by a valve spring 52, which is only able to develop a relatively weak (return) actuating force, which is greater than that from an action the one, as shown in FIG.
  • left control chamber 51 of the changeover valve 48 with the output pressure of the pump 37 resulting actuating force, by means of which the changeover valve 48 can be switched into its functional position I is small, but is sufficient in amount to the changeover valve in the functional position Hold 0 as long as the two control chambers 49 and 51 are depressurized or pressurized with the same control pressure, the actuating force resulting from the application of pressure to the other right control chamber 49 of the changeover valve 48 with the output pressure of the pressure supply pump 37, which the changeover valve 48 in its functional position 0 urges, according to the amount of the from the Pressurization of the left control chamber 51 corresponds to the resulting actuating force and is therefore also large compared to that of the valve spring 52.
  • latching devices can be provided which act in a force-locking manner and develop a moderate holding force which corresponds only to part of the maximum restoring force of the restoring spring 52.
  • the drive pressure which can be provided at the high pressure outlet 36 of the pressure supply pump 37 is via a flow path 56, which is released in this basic position 0 and connects the P supply connection 53 of the changeover valve 48 to its B output 54 and a B output 54 of the Changeover valve 48 with the rod-side drive chamber 32 of the pressure medium line 57 connecting the right drive cylinder 13 according to FIG. 2 into the rods Side drive chamber 32 of the drive cylinder 13 can be coupled in and at the same time the rod-side drive chamber 33 of the drive cylinder 14 on the left in FIG. 2 via a second pressure medium line 58 and a flow path 62 connecting the A output 59 of the changeover valve 48 with its unpressurized T-connection 61 to the unpressurized reservoir 38 the pressure supply pump 37 relieved of pressure.
  • This functional position 0 of the changeover valve 48 which is also its spring-centered basic position, is assigned to the operating state of the thick matter pump 10 in which one, "right” drive cylinder 13 executes its intake stroke and thus the one delivery cylinder 11 performs its filling stroke, while the piston 17 accordingly Fig. 2 left drive cylinder 14 its outward stroke and thus the movement-coupled piston of the other delivery cylinder 12 executes its delivery stroke.
  • switch position I which the changeover valve 48 assumes when its left control chamber 51, as shown in FIG. 2, is exposed to the high output pressure of the pressure supply pump 37 and its right control chamber 49 is depressurized, the rod-side is via a flow path 63 of the changeover valve 48 that is released in this functional position I.
  • the drive chamber 33 of the left drive cylinder 14 can be acted upon by the high output pressure of the pressure supply pump 37, while the rod-side drive chamber 32 of the right drive cylinder 13 is relieved of pressure via the further flow path 64 released in this functional position I of the changeover valve.
  • This functional position I of the changeover valve 48 is assigned to the operating state of the thick matter pump 10 in which its "left" drive cylinder 14 executes its intake stroke and the feed cylinder 12 driven by it performs its filling stroke, while the right drive cylinder 13 performs its outward stroke and that driven by the right drive cylinder 13 Delivery cylinder 11 executes its delivery stroke.
  • two pilot valves 66 and 67 are provided, which can be actuated mechanically by the pistons 16 and 17 of the two drive cylinders, ie can be switched from a spring-centered basic position 0 against the restoring force of a valve spring 68 or 69 to a switching position I and can be hydraulically locked in this switching position I.
  • a mechanical latching device that supports its function and is effective with moderate holding force can be provided, which provides a force-locking fixation of the hydraulically locked switching position.
  • pilot valves 66 and 67 are mounted on the outside on the cylinder bottoms 46 and 47 of the drive cylinders 13 and 14 and are provided with actuating plungers 71 and axially protruding into the bottom-side drive pressure spaces 39 and 41 of the drive cylinders 13 and 14 72, which pass through central bores 73 and 74 of the respective cylinder base 46 and 47 in a pressure-tight manner.
  • the respective pilot valve 66 or 67 is hydraulically locked in the switching position I assumed by the changeover by coupling control pressure into a respective control chamber 76 or 77 of the respective pilot valve 66 or 67.
  • the pilot valves are designed as 3/2-way valves, in the basic position 0 of which a flow path 78 or 79 is released, via which the high output pressure of the pressure supply pump 37 is coupled into one of the two control chambers 49 or 51 of the changeover valve 48, whereby this can be switched into its functional position 0 or its switching position I, and on the other hand is coupled into the control chamber 76 or 77 of the other pilot valve 66 or 67, whereby this pilot valve 66 or 67 is locked in its switching position I.
  • a manually switchable or electrically controllable ON / OFF switching valve 81 is provided, which is designed as a 2/2-way valve with an open basic position 0 and a blocking switching position I, in which reason Position 0 of this switching valve 81, the high-pressure output 36 of the pressure supply pump 37 is connected to the unpressurized reservoir 38, so that the pump 37 in the basic position 0 of the switching valve 81 operates in circulation mode and the drive cylinders 13 and 14 cannot be acted upon by drive pressure while in In the blocking switching position I of the switching valve 81, the output pressure of the high-pressure pump 37 is present at the P connection 53 of the changeover valve 48 and, via the pilot valves 66 and 67, also in one of the control chambers 49 or 51 of the changeover valve 48 and one of the control chambers 76 and 77 of the pilot valves 66 and 67 is coupled.
  • the circulation operation of the pressure supply pump 37 is ended and its pressure supply operation is initiated in which the high pressure at the high pressure outlet 36 of the pump 37 builds up at the P connection 53 of the Changeover valve 48 is present and via its flow path 56 and the pressure medium line 57 is coupled into the rod-side drive chamber 32 of one "right” drive cylinder 13, and the rod-side drive chamber 33 of the other - “left” - drive cylinder 14 via the pressure medium line 58 and the other, in the basic position 0 of the changeover valve 48, the flow path 62 is connected to the tank connection 61 of the changeover valve and via the return line 82 to the unpressurized reservoir 38 of the pressure supply unit 37, 38.
  • the piston 16 of the right-hand drive cylinder 13 executes the pull-in stroke linked to the filling stroke of the feed cylinder 11 and directed towards the bottom 46 of the drive cylinder 13, as a result of which pressure medium from the bottom-side drive chamber 39 of this drive cylinder 13 via the pressure line 42 into the bottom-side drive chamber 41 of the other drive cylinder 14 is displaced, the piston 17 thereby executing its outward stroke linked to the conveying stroke of the conveying cylinder 12.
  • both control chambers 49 and 51 are initially acted upon via their flow paths 78 and 79 with the pressure building up at the pressure outlet 36 of the high-pressure pump 37, the changeover valve, however - essentially - by the action the valve spring 52 remains in its basic position 0.
  • the pilot valve 66 mounted on this drive cylinder 13 is switched to its switching position I, in which the control chamber 77 of the pilot valve 67 mounted on the bottom of the left drive cylinder 14 via a valve in the switching position I of the pilot valve 66 of the right drive cylinder 13, the flow path 83 and a relief line 84 to the reservoir 38 are relieved of pressure, and that control chamber 49 of the changeover valve 48 is relieved of pressure, by the pressurization of which a switching force which is rectified with the force of the valve spring 52 can be generated.
  • the pilot valve 67 which it can actuate is mechanically switched to its switching position I, in which the control chamber 76 of the other pilot valve 66 is relieved of pressure via the flow path 86 which is released in it , whereby the previously existing hydraulic locking of this pilot valve 66 in its switching position I is canceled and this pilot valve 66 switches back to its basic position 0, in which the control chamber 77 of the previously mechanically actuated pilot valve 67 with a high level is activated via the flow path 78 released in this basic position 0 Pressurized and this pilot valve 67 is thereby locked in its switching position I and on the other hand that control chamber 49 of the switching valve 48 is exposed to high pressure, the pressure of which causes the switching valve 48 to return to its basic position 0 is definable.
  • the other control chamber 51 of the changeover valve 48 is relieved of pressure via the pilot valve 67 mounted on the left drive cylinder 14 to the reservoir 37 of the pressure supply unit, so that the changeover valve 48 also switches reliably into its basic position 0, in which the two drive cylinders 13 and 14 now again are driven with the reverse direction of movement of their pistons 16 and 17.
  • the hydraulic drive system of the thick matter pump 10 is now in its "steady" operating state, in which the two delivery cylinders 11 and 12 perform their filling and delivery strokes alternating periodically, which are automatically controlled by the hydraulic sequence control described.
  • a manually switchable compensation valve 87 is provided in the exemplary embodiment selected for explanation, which is designed as a 3/3-way valve, which has a central position as the blocking neutral position 0 and two alternative switching positions I and 11, in one of which - the switching position I - hydraulic oil can be displaced into the bottom-side drive chambers 39 and 41 of the two drive cylinders 13 and 14 by means of the high-pressure pump 37 via a compensating line 88 which is connected to the connecting line 42, and in the other - the switch position 11 - hydraulic oil can be drained from the two bottom-side drive chambers 39 and 41 via the compensating line 88 and a flow path 89 released in this switch position 11 to the unpressurized reservoir 38 of the pressure supply unit 37, 38.
  • a check valve 91 is connected, which can be actuated in the opening direction by relatively higher pressure at the line-side connection 92 than in the compensating line 88 or the bottom-side drive chambers 39 and 41 of the two drive cylinders 13 and 14, and by relatively higher Pressure in the compensating line 88 is pushed into its blocking position at this valve connection 92 and is mechanically unlocked in the switching position 11 of the compensating valve 87, in which hydraulic oil must be able to be drained from the rocking oil circuit.
  • a pressure relief valve 93 which is hydraulically connected in parallel with the high pressure pump 37, is provided, by means of which the outlet pressure of the pump 37 is reduced to a predetermined limit value of e.g. 200 bar is limited, when the excess pressure valve 93 opens a relief path 94 leading to the reservoir 38.
  • the other possible malfunction is that the amount of rocking oil, e.g. has decreased due to a leak in the rocking oil circuit, it can be seen that the delivery and filling strokes of the thick matter pump 10 decrease in amount.
  • This malfunction can - while the thick matter pump 10 is in operation - thereby eliminated - compensated for - that the compensating valve 87, if necessary several times, is switched over to its functional position I for a short period of time in the hydraulic oil via a flow path 96 released in this functional position I.
  • the compensating line 88 can be displaced into the connecting line 42 and via this into the bottom drive chambers 39 and 41 of the two drive cylinders 13 and 14.
  • Such a switching of the compensation valve 87 is repeated until the maximum values of the filling and delivery strokes of the thick matter pump are achieved again.
  • pilot valves 66 and 67 of their hydraulic drive unit are each mechanically actuated and hydraulically locked in the functional positions achieved by the mechanical actuation when the pistons 16 or 17 of the two hydraulic drive cylinders 13 and 14 enter their bottom-side setting
  • the hydraulic drive unit 13, 14, 48, 36 with an equivalent function in such a way that the pilot valves 66 and 67 are assigned to a single one of the drive cylinders 13 or 14 and one of these two pilot valves is then actuated, when the drive cylinder piston 16 or 17 runs into its bottom end position and the other of the two pilot valves is actuated when the same drive cylinder piston 16 or 17 runs into its end position away from the floor.
  • this pipe switch can also be controlled by the pressure output signals of the pilot valves 66 and 67.
  • FIG. 3 a hydraulic control unit as a whole analogous to the hydraulic control unit 34 according to FIG. 2 is denoted by 34 '.
  • this hydraulic control unit 34 'shown in FIG. 3 and the drive cylinder are provided with the same reference numerals as the element of the control unit 34 shown in FIGS. 2 and 2a, this is intended to indicate their structural and functional equality 1 or 2a, in order to avoid repetitions and to be able to restrict the description of the exemplary embodiment according to FIG. 3 essentially to its structural differences compared to the exemplary embodiment according to FIG. 2 .
  • the pressure supply pump 37' is a reversible variable displacement pump, e.g. designed as a swash plate axial piston pump which, depending on the position of its swash plate represented by arrow 97, can be operated in two alternative conveying directions, in which one of the two supply connections 36 'and 36 "each has the high-pressure outlet and the other the return connection of the variable displacement pump 37 ' form.
  • a hydraulic actuating cylinder 98 designed as a double-acting hydraulic linear cylinder is provided, whose piston 99, which forms the axially movable, pressure-tight delimitation of the two drive chambers 101 and 102 of the double-acting actuating cylinder 98, via one or both of them to the Piston rods 103 and 104 emerging from the end faces of the cylinder housing and sealed against this in a pressure-tightly displaceable manner, as illustrated by a schematically indicated mechanical actuating element 106, are coupled in motion to the swivel plate 97 of the variable displacement pump 37 '.
  • deflections of the actuating cylinder piston 99 to the right are linked to deflections of the swivel plate 97 in a clockwise direction, the pump 37 ', if its swivel plate 97, from a neutral central position, which is marked by the reference plane 107 shown in broken lines, a clockwise positive angular distance ( 3, hydraulic fluid is displaced into the rod-side drive pressure chamber 32 of the right drive cylinder 13 via its right supply connection 36 'and the pressure medium line 57 and hydraulic fluid flowing out of the rod-side drive pressure chamber 33 of the left drive cylinder 14 via its left supply connection 36 " Liquid returns to the reservoir 108 of the pressure supply unit, and in the event that the swivel plate 97 from the reference plane 107 is at a negative counterclockwise angular distance (- 4 » via its left supply connection 36" as H High-pressure outlet hydraulic fluid is displaced via the pressure medium line 58 to the rod-side drive pressure chamber 33 of the left drive cylinder 14 and drains hydraulic fluid flowing out
  • a check valve 113 or 114 is connected, which is due to relatively higher pressure at the supply connection 36 'or 36 "of the pressure supply pump 37' than at the input connections 111 and 112 of the two pilot valves 66 and 67 in ⁇ direction of opening and is otherwise blocking.
  • control output 116 connected to the control chamber 77 of the left pilot valve 67, which in the basic position 0 of the right pilot valve 66 is connected to its input port 111, is connected via a control line 117 to the left drive chamber 102 of the actuating cylinder 98 according to FIG. 3, during the in the basic position 0 of the left pilot valve 67 with its input port 112 communicating control output 118 of the left pilot valve 67 is connected via a further control line 119 to the right drive chamber 101 of the actuating cylinder 98 according to FIG. 3.
  • actuating force of which is significantly lower than the actuating forces which can be generated by pressurizing the right drive chamber 101 while simultaneously relieving pressure on the left drive chamber 102 of the actuating cylinder 98 or relieving pressure on the left drive chamber 102 and relieving pressure on the right drive chamber 101
  • that pivot position of the swivel plate 97 of the pressure supply pump 37 ' is distinguished as the starting position in which the pressure supply pump 37' when the thick matter pump 10 starts up first allows its right delivery cylinder 11 to carry out its filling stroke, ie the right drive cylinder 13 executes its inward stroke.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
EP95101113A 1994-02-03 1995-01-27 Commande d'entraînement pour une pompe à deux cylindres pour liquides épais Expired - Lifetime EP0668441B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4403213A DE4403213A1 (de) 1994-02-03 1994-02-03 Einrichtung zur Antriebssteuerung einer Zweizylinder-Dickstoffpumpe
DE4403213 1994-02-03

Publications (2)

Publication Number Publication Date
EP0668441A1 true EP0668441A1 (fr) 1995-08-23
EP0668441B1 EP0668441B1 (fr) 1996-12-11

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EP95101113A Expired - Lifetime EP0668441B1 (fr) 1994-02-03 1995-01-27 Commande d'entraînement pour une pompe à deux cylindres pour liquides épais

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EP (1) EP0668441B1 (fr)
AT (1) ATE146257T1 (fr)
DE (2) DE4403213A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3657015A1 (fr) * 2018-11-21 2020-05-27 Liebherr-Betonpumpen GmbH Unité de pompe à béton

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19507354B4 (de) * 1995-03-03 2009-12-10 Continental Automotive Gmbh Saugmodul für einen Ottomotor
US6550368B2 (en) * 2000-10-31 2003-04-22 Festo Corporation Fluid power interlock system
DE10336196A1 (de) * 2003-08-07 2005-03-03 Daimlerchrysler Ag Saugmodul für eine Brrennkraftmaschine
DE102009021833A1 (de) 2009-05-19 2010-11-25 Robert Bosch Gmbh Hydraulischer Antrieb und Drehschieberventil für einen hydraulischen Antrieb
DE102012014336A1 (de) * 2012-07-19 2013-11-14 Technotrans Ag Fördersystem zum Fördern eines Schmiermittels einer Blechtiefziehmaschine und korrespondierendes Verfahren
DE102015103180A1 (de) * 2015-03-05 2016-09-08 Schwing Gmbh Zweizylinder-Kolbenpumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2549851A (en) * 1946-06-24 1951-04-24 Louis C Pope Hydraulic pumping apparatus
DE1296524B (de) * 1964-04-14 1969-05-29 Royal Industries Kolbenpumpe fuer dickfluessige, breiige Massen, insbesondere Beton od. dgl.
DE3814824A1 (de) * 1988-05-02 1989-11-16 Putzmeister Maschf Steuerungsanordnung fuer eine zweizylinder-dickstoffpumpe

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1019563B (de) * 1956-05-07 1957-11-14 Haniel & Lueg Gmbh Hydrostatischer Antrieb fuer doppeltwirkende Kolbenpumpen, insbesondere fuer Spuelpumpen von Tiefbohranlagen in Duplex-Anordnung
DE1267982B (de) * 1961-07-10 1968-05-09 Eugene Lee Sherrod Antrieb fuer eine mehrzylindrige Kolbenpumpe zum Foerdern von Beton u. dgl.
DE1910107A1 (de) * 1969-02-28 1970-09-17 Scheele Kg Walter Zwillingsanordnung zweier hydraulisch gegenlaeufig angetriebener Kolbenmaschinen
DE2126446A1 (de) * 1971-05-27 1972-12-07 Wilhelm Reich Kg, 7900 Ulm Hydraulischer Zwillingskolbenantrieb, insbesondere für Betonpumpen
DE4017029A1 (de) * 1990-05-26 1991-11-28 Delmag Maschinenfabrik Hydrobaer
DE4029718C2 (de) * 1990-09-19 1995-03-16 Paul Pleiger Gmbh & Co Kg Steuerung für eine Kolbenpumpe
JPH05268687A (ja) * 1992-03-19 1993-10-15 Sony Corp スピーカーネットの取付構造

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2549851A (en) * 1946-06-24 1951-04-24 Louis C Pope Hydraulic pumping apparatus
DE1296524B (de) * 1964-04-14 1969-05-29 Royal Industries Kolbenpumpe fuer dickfluessige, breiige Massen, insbesondere Beton od. dgl.
DE3814824A1 (de) * 1988-05-02 1989-11-16 Putzmeister Maschf Steuerungsanordnung fuer eine zweizylinder-dickstoffpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3657015A1 (fr) * 2018-11-21 2020-05-27 Liebherr-Betonpumpen GmbH Unité de pompe à béton

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ATE146257T1 (de) 1996-12-15
EP0668441B1 (fr) 1996-12-11
DE59500057D1 (de) 1997-01-23
DE4403213A1 (de) 1995-08-10

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