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
  • F04B7/0019—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers
  • F04B7/0026—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers and having an oscillating movement
• • 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
• • 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
  • 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
  • F04B15/023—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 supply of fluid to the pump by gravity through a hopper, e.g. without intake valve
• • 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
  • F04B23/02—Pumping installations or systems having reservoirs
• • 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
• • 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
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/002—Hydraulic systems to change the pump delivery
• • 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
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
• • 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
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
  • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
• • 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
  • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means

Definitions

• the invention relates to a device for controlling the drive of a Zweizylin- the Dickstoffpumpe specified in the preamble of claim 1 genus.
• Two-cylinder thick matter pumps of this type have two delivery openings opening into a material feed container via end openings, the delivery pistons of which can be actuated alternately by means of hydraulically actuated drive cylinders while carrying out a filling stroke and a delivery stroke.
• a pipe switch is arranged, which is connected by means of a hydraulic drive mechanism on the inlet side alternately to the opening of one of the delivery cylinder and the opening of the respective other delivery cylinder releases, and the outlet side is connected to a delivery line for the conveyed thick materials.
• the sludge pump further has a motor-driven hydraulic variable displacement pump which has a suction inlet connected to a reservoir and a high-pressure outlet.
• the drive cylinders for the delivery pistons can be alternately connected to the high-pressure outlet of the variable-displacement pump via a pressure line, and to the reservoir via a return line via a respective hydraulic connection located at one end thereof by means of a first reversing valve. At the other end, the drive cylinders are connected to each other via a swing oil line.
• the hydraulic drive mechanism of the pipe switch on a two-sided controlled cylinder arrangement for example in the form of two series Plunger cylinders, their connections via a second reversing valve alternately leading to the high pressure output of the hydraulic variable delivery pressure line and leading to the reservoir return line can be connected.
• a central control is provided, which responds to end position signals of the passing drive piston at least one of the drive cylinder.
• the thick matter delivery and the diverter diverter take place alternately in a single-circuit system via the same variable-displacement pump, which can be adjusted continuously between a zero delivery and a predetermined maximum delivery.
• the adjustment in the thick matter delivery depends on a specified by the operator on a setting, adapted to the demand flow rate, while for the reversal of the pipe switch, regardless of the set in the machine flow rate a defined switching time is sought.
• the variable displacement pump has a flow regulator, the control input is acted upon in the delivery phase with a variable, adapted to the set flow control pressure, while it is acted upon in the Um Kunststoffphase with a defined Um Kunststoff Kunststoff.
• control input of the flow control valve in the delivery phase and in the reversal phase must be acted upon with different pressure control signals, including in the prior art designed as a directional valve switch-over valve (SOS valve) is used.
• SOS valve directional valve switch-over valve
• a disadvantage of this type of control is that two control signals which are generated independently of one another are used for the regulation of the variable-displacement pump, for the intended selection of which an electromagnetically actuated switch-over valve is required in the course of the conveying and reversing phase. This requires both hardware and control a considerable effort. Proceeding from this, the present invention seeks to improve the known device for controlling the drive of a sludge pump to the effect that a simplification of the hydraulic circuit arrangement can be achieved without loss of functionality.
• the solution according to the invention consists essentially in that in the pressure line between the high pressure output of the variable displacement pump and the first reversing valve a setting throttle is arranged, that is branched off from the pressure line downstream of the adjusting a directly leading to an adjustment mechanism of the variable displacement control line, and that of the pressure line upstream of the variable throttle is branched off to a supply connection of the second reversing valve connecting line, in which a fixed throttle can be arranged if necessary.
• a special feature of the invention is therefore that the adjusting mechanism containing a load-sensing controller of the variable displacement is controlled only via a control line, and that thus eliminates the known switch-over valve.
• the variable displacement pump additionally includes a pressure regulator for regulating the delivery rate when a predetermined maximum pressure at the high-pressure outlet is exceeded. This maximum pressure is always reached when the drive piston reach its end stop in the course of the delivery process and the pressure difference which can be tapped off at the setting throttle becomes zero. This is exactly the state in which the reversal of the pipe switch is initiated via the second reversing valve.
• the maximum pressure which adjusts itself to the high-pressure outlet of the variable-displacement pump is present at the fixed throttle, leading to a delivery flow leading via the defined flow cross-section of the connecting line to the plunger cylinder which is currently pressurized.
• This flow can so Preferably over the flow cross section of a fixed throttle in the connecting line and the maximum pressure can be preset that the Rohr Hughesum facedung takes place in a predetermined time, for example, 200 ms. It follows that the variable displacement pump is flow-regulated during the actual delivery process, whereas it is pressure-controlled over the predetermined maximum pressure during the changeover process, unlike previously.
• a further preferred embodiment of the invention provides that the load-sensing hydraulic has a arranged in the variable displacement, mechanically adjustable swash plate as an adjustment member and connected to the swash plate, the force side spring-assisted pressure compensator, to which the load side, the downstream of the setting throttle branched off control line is connected ,
• the drive cylinder have at least two responsive to the drive piston cylinder switch sensors, the output side connected to signal inputs of the central control are.
• the drive mechanism of the pipe switch also has at least one pipe path which responds to the position, the speed or the end positions of the pipe switch. on the output side is connected to a signal input of the central control.
• the reversing valves are designed as directional control valves with electromagnetic pilot control elements whose pilot control elements are each connected to a control output of the central control.
• FIG. 1 shows a detail of a two-cylinder slurry pump in partially cut perspective view
• Fig. 2 is a circuit diagram of a drive hydraulic for the two-cylinder slurry pump.
• the drive hydraulic system shown in the hydraulic circuit diagram of FIG. 2 is determined for a two-cylinder slurry pump according to FIG. 1.
• the sludge pump has two delivery cylinders 14, 14 'whose front-side openings 12, 12' open into a material supply container 10.
• the delivery pistons 16, 16 'of the slurry pump can be actuated alternately in push-pull manner by hydraulically controlled drive cylinders 18, 18' while carrying out a filling stroke (arrow 19 ') and a delivery stroke (arrow 19 "). which is connectable on the inlet side alternately to the opening 12 of one of the delivery cylinders 14 by means of a hydraulic drive mechanism 24, while it releases the opening 12 'of the respective other delivery cylinder 14.
• the transfer tube 22 is connected to a delivery line 26.
• a motor 27 driven hydraulic variable displacement pump 28 is provided, which has a suction port 32 connected to a non-pressurized reservoir 30 and a high pressure port 36 connected to a pressure line 34.
• the drive cylinders 18,18 ' are connected to each other at the other end via a swing oil pipe 44.
• the hydraulic drive mechanism 24 of the pipe switch 22 comprises two plunger cylinders 46 connected in series, which can be connected alternately via a second changeover valve 48 to the pressure line 34 leading to the high pressure outlet 36 of the hydraulic variable displacement pump 28 and to a return line 50 leading to the reservoir 30.
• a central control 56 which responds to end position signals of the passing drive pistons 20, 20 'of at least one of the drive cylinders 18, 18' is provided, via which sequence control for the first and the second reversing valves 40, 48 can be triggered.
• a setting throttle 58 is arranged in the pressure line 34 between the high-pressure outlet 36 of the variable displacement pump 28 and the first reversing valve 40 and is infinitely adjustable by the operator.
• a peculiarity of the invention is that of the pressure line 34 downstream (58 ') of the setting throttle 58 is fed back directly to an adjusting mechanism 60 of the variable displacement pump 28 leading control line 62, and that of the pressure line 34 upstream (58 ") of the setting 58 a branching to a supply connection 64 of the second reversing valve 48 connecting line 66 is branched off, in which, if necessary, a fixed throttle 68 is arranged.
• the adjustment mechanism 60 includes a load-sensing hydraulic 70 that provides hydraulic power control in which both the pressure and the flow rate of the adjustment pump 28 are adjusted to the conditions required by the consumer. As a controlled variable, the pressure drop at the setting throttle 58 is used.
• the load-sensing hydraulic system 70 has a mechanically adjustable swashplate 72 arranged as an adjusting element in the variable-displacement pump 28 and a pressure-compensated spring-based pressure compensator 73 connected to the swash plate 72, to which the downstream side of the adjusting throttle 58 branches off on the load side Control line 62 is connected.
• the variable displacement pump 28 is infinitely adjustable from zero flow rate to full delivery. In the zero position of the 4/3-way valves formed Um tenuventile 40,48 flows except for leakage oil losses no hydraulic oil through the lines. At the same time, the variable displacement pump 28 maintains a standby pressure.
• variable displacement pump 28 conveys only so much hydraulic fluid to maintain the currently required delivery pressure at the required delivery volume.
• the variable displacement pump 28 additionally comprises a pressure regulator, not shown, for regulating the flow rate when a predetermined maximum pressure is exceeded. This Abregelungsfunktion is used in the control of the drive mechanism 24 for the pipe switch 22.
• the drive cylinder 18,18 'two on the passing drive piston 20,20' responsive Zylinderschaltsensoren Have 52.54, the output side with signal inputs 52 ', 54' of the central control 56 are connected.
• the anti-knocking mechanism 24 of the pipe switch 22 has a pipe switch sensor 74, which responds to the position, the speed or the end positions of the pipe switch, and which is connected on the output side to a further signal input 74 'of the central control 56.
• the changeover valves 40, 48 are designed as directional control valves with electromagnetic pilot control elements 76, 78.
• the pilot control elements are each connected to a control output 76 ', 78' of the central control 56.
• the control signals for the changeover valves 40, 48 of the delivery piston drive and the tube transfer drive are calculated from the signals coming from the cylinder shift sensors 52, 54 and optionally from the tube deviation sensor 74.
• hydraulic oil flows from the variable displacement pump 28 via the pressure line 34, the setting throttle 58 and the reversing valve 40 into the drive cylinder 18, 18 'for the delivery piston 16, 16' for the delivery stroke 19.
• the oil quantity of the variable displacement pump 28 during the Feed phase via the load-sensing hydraulic 70 is set by adjusting a pressure drop across the setting throttle 58 via the control line 62.
• hydraulic oil flows via the connecting line 66 and the reversing valve 48 into the plunger cylinder 46 performing a pressure stroke Drive piston 20,20 'at their end stops, so that sets the maximum pressure at the high pressure outlet 36 of the variable displacement 28.
• the amount of oil passing through the connecting line 66 under the effect of the maximum pressure is such that the diverter 22 via the plunger cylinder 46 in a defined time in size 200 ms within the material feed container 10 is reversed. If necessary, a fixed throttle 68 can be arranged in the connecting line for this purpose.
• the invention relates to a device for controlling the drive of a two-cylinder slurry pump with a arranged in a material feed container 10 manifold 22 and a motor-driven hydraulic variable displacement pump 28, via which both the drive cylinder 18,18 'of the slurry pump and the drive mechanism 24 of the pipe switch are controlled.
• a special feature of the invention is that a setting throttle 58 is arranged in a pressure line 34 between the high-pressure outlet 36 of the variable displacement pump 28 and the drive cylinders 18, 18 'of the thick matter pump, that of the pressure line 34 downstream of the setting throttle 58 directly to an adjusting mechanism 60 of the variable displacement pump 28 leading control line 62 is fed back and that is branched off from the pressure line 34 upstream of the adjusting throttle 58 leading to a supply port 64 of the cross-over hydraulic connection line 66, in which a fixed throttle 68 may be arranged.
• This ensures that the oil flow in the delivery phase is flow-regulated, while it is pressure-controlled in the reversal phase.
• the variable displacement pump 28 additionally comprises a pressure regulator for regulating the flow rate when a predetermined maximum pressure is exceeded.

Landscapes

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

Priority Applications (6)

Applications Claiming Priority (2)

Publications (1)

Family

ID=48703508

Family Applications (1)

Country Status (8)

Cited By (1)

Families Citing this family (9)

Citations (2)

Family Cites Families (12)

• 2012
  • 2012-09-13 DE DE102012216242.9A patent/DE102012216242A1/de not_active Withdrawn
• 2013
  • 2013-06-27 KR KR1020157006026A patent/KR102020700B1/ko active IP Right Grant
  • 2013-06-27 BR BR112015004524A patent/BR112015004524A2/pt not_active IP Right Cessation
  • 2013-06-27 JP JP2015531495A patent/JP6194360B2/ja not_active Expired - Fee Related
  • 2013-06-27 CN CN201380042703.4A patent/CN104541054B/zh active Active
  • 2013-06-27 EP EP13732483.6A patent/EP2895743B1/de active Active
  • 2013-06-27 WO PCT/EP2013/063530 patent/WO2014040769A1/de active Application Filing
  • 2013-06-27 US US14/419,492 patent/US20150211503A1/en not_active Abandoned

Patent Citations (2)

Also Published As

Similar Documents

Legal Events