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
  • 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
  • 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
  • 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
  • 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
  • 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
• • 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
  • F04B2203/00—Motor parameters
  • F04B2203/09—Motor parameters of linear hydraulic motors
  • F04B2203/0903—Position of the driving piston

Definitions

• the present invention relates to a method for operating a two-cylinder high-pressure pump or a drive device for a two-cylinder high-pressure pump according to the preamble of claim 1 or to the preamble of claim 8.
• Zweizylinderdickstof ⁇ umpen be used for example for the promotion of concrete.
• the concrete z. B. pumped via appropriate distribution booms on significant heights and distances.
• the delivery cylinders are connected via a switch, in particular a diverter valve to a common delivery line, wherein the switch alternately connects the one or the other delivery cylinder with the delivery line, so that there is a total of a nearly continuous flow of the thick material or concrete.
• FIG. 2 shows a hydraulic drive for a Zweizylinderdickstof ⁇ umpe with a pipe switch.
• the block diagram shown is a so-called single-circle system in which the drive cylinders 1, 2 of the delivery cylinders FR, FL and the setting cylinders SZ of the transfer tube are supplied with hydraulic oil only by means of a supply device or the working pressure is generated.
• This single supply device has two pumps Pl and P2, which are connected via the oil lines Ll and L2 with a switching block 3, depending on the operating state of the pumped by the pumps Pl and P2 oil via lines L4 the one drive cylinder 1 or the drive cylinder 2 for the delivery cylinder FR and FL or via further lines L4a the adjusting or swivel cylinder SZ of the pipe switch RW is available.
• the control block 3 is switched so that the entire capacity of the pump Pl and P2 is the adjusting or swivel cylinder SZ is made available.
• the disadvantage here is that two separate pumping devices must be present, in particular, the pump Pl must be made correspondingly large in order to provide the necessary hydraulic oil volume flow for the operation of the drive cylinder 1 and 2 available.
• a portion of the fluid volume flow preferably hydraulic oil volume. Menstroms can be provided for the actuation of the adjusting or swivel cylinder of the switch.
• the determination device used therefor can be of a mechanical, electrical or hydraulic nature, with the latter in particular offering itself when the entire control of the drive largely takes place by means of a fluid or hydraulic oil. Namely, corresponding switching valves can be used in a simple manner, which are controlled via known hydraulic control lines.
• a corresponding detection device for detecting the piston position of the adjusting cylinder of the pipe switch may be provided to use this information for the switching operation.
• the hydraulic circuit can be constructed so that two pumping devices used to provide a corresponding fluid flow or operating pressure are used, which are comparable to the two-circuit system primarily independent on the one hand for driving the drive cylinder and on the other hand for driving the actuating or pivoting cylinder for the switch. Due to the idea according to the invention that shortly before the required switching operation of the switch, the drive power for the Antriebsl. Delivery cylinder must not be 100%, the two independent pumping devices can be combined with each other in such a way that during the piston stroke of the drive cylinder or delivery cylinder, the second pumping device provides their capacity for the drive or delivery cylinder, while shortly before the switching operation the second pumping means exclusively for the actuation of the Stellitati. Swing cylinder of the switch is used. In this way, it is possible to effectively use the pumping or delivery of the drive or to use components with lower power.
• the drive is designed so that the operating pressure in particular of the second pumping device is present during the entire operation of the actuating or swivel cylinder.
• the deflection of the fluid volume flow can be realized in a simple manner by a corresponding switching valve, so that the circuit complexity can be kept very low overall.
• Fig. 1 is a block diagram of a drive device according to the invention
• Fig. 2 is a block diagram of a known recirculating system
• Fig. 3 is a block diagram of a known two-circuit system.
• Fig. 1 shows a block diagram of a hydraulic drive of a Zweizylinderdickstof ⁇ umpe with a first drive cylinder 1 and a second drive cylinder 2, which are connected via the corresponding piston with a first delivery cylinder FR and a second delivery cylinder FL.
• the delivery cylinders FL and FR are connected via a pipe switch RW to a common delivery line, so that a nearly continuous delivery rate for the thick material is achieved by the alternating stroke of the delivery cylinders FL and FR.
• the pipe switch RW must be alternately brought into a connecting position between the first conveyor cylinder FR and the common conveyor line or second conveyor cylinder FL and common conveyor line via a control or swivel cylinder SZ.
• the pumping devices P1 and P2 are connected via the supply lines L1 and L2 to the control block 3, in which switching valves 3.1 and 3.2 are received, which in turn are connected to the hydraulic lines L4 and L4a.
• an intermediate line for mutual connection is provided, in which a switching valve 6 is installed, so that hydraulic oil, which is conveyed in the supply line Ll through the first pumping device Pl can be pumped into the second supply line L2.
• the switching valve 6 has the task that hydraulic oil, which is pumped by the second pumping device P2 in the supply line L2, to maintain a sufficient flow of oil to actuate the drive cylinder 1 and 2 can pass into the first supply line Ll.
• the hydraulic oil in the supply line Ll is then alternately through the switching valve 3.2 via the supply lines L4 the first drive cylinder 1 and the second drive cylinder 2 provided to operate on these the delivery cylinders FR and FL. Via the line L9 the oil return occurs.
• switching valves VFR and VFL are provided, by means of which the alternating stroke movement of the drive cylinders 1 and 2 is controlled. Because of the alternating stroke movement of the drive cylinders 1 and 2, these are hydraulically coupled to one another via the control lines SL5, SL6, SL7 and SL9.
• the switching valves VFR and VFL also simultaneously form so-called proximity switches, by means of which the piston position in the drive cylinders 1 and 2 can be determined. At the same time are acted upon by the corresponding positions of the piston in the drive cylinders 1 and 2 connected to the switching valves VFR and VFL control lines SL8 and SL10, which in turn control the switching valves 3.1 and 3.2 in the control block 3 and the switching valve 6 accordingly.
• the actuating cylinder SZ is supplied via the switching valve 3.1 through the second pumping device P2 and the supply lines L2 and L4a with corresponding hydraulic oil or pressurized.
• the switching valve 6 is triggered by the hydraulic signals by means of the control lines SL8 and SL10, the switching valve 3.1 and the switching valve 6 are switched over the switching valve 6 before reaching the respective Kolbenend too the drive cylinder 1 or 2 accordingly.
• the switching valve 6 blocks in this case the connecting line between the supply lines Ll and L2 in such a way that no more oil flow from the supply line L2 in the supply line Ll and thus can reach the supply of the drive cylinder 1 and 2. Rather, the delivery rate of the second pumping device P2 is completely provided to the swivel cylinder SZ, wherein by the corresponding hydraulic control lines SL18 and SL19 and the switching valve VSZ for controlling the actuating or Swivel cylinder SZ is actuated or this outputs corresponding control signals to the changeover valve 6.
• the switching valve 6 Through the use of the switching valve 6, the oil volume flow, which is usually used by the second pumping device P2 for the actuation of the drive cylinders 1 and 2, in the final movement of the respective drive cylinders 1 and 2, in which this volume flow is not absolutely necessary, early for an operation of the swing cylinder are used, so that the delivery interruption of the Dickstof ⁇ umpe is reduced.
• the second pumping device P2 is connected via the supply line L2 directly to the switching valve 3.1 or via the hydraulic lines L4a to the swivel or actuating cylinder SZ, the operating pressure of the second pumping device P2 is available to the swivel cylinder SZ during the entire operation.
• the Aus collirungsbeispiel shown is thus an advantageous combination of a single-circuit and a dual-circuit system, in which the delivery rate of the second pumping device is used variably both for the actuation of the drive cylinder 1 and 2 and the pivoting or actuating cylinder SZ.
• the advantageous possibility already provides a part of the oil flow rate for the actuation of the actuating or pivoting cylinder of the transfer tube, so as to minimize the flow interruption to a minimum.

Landscapes

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

Priority Applications (8)

Applications Claiming Priority (2)

Publications (1)

Family

ID=34965057

Family Applications (1)

Country Status (13)

Families Citing this family (3)

Citations (5)

Family Cites Families (7)

• 2004
  • 2004-05-27 DE DE102004025910A patent/DE102004025910B4/de not_active Expired - Fee Related
• 2005
  • 2005-04-18 DE DE502005004346T patent/DE502005004346D1/de not_active Expired - Fee Related
  • 2005-04-18 BR BRPI0511335-0A patent/BRPI0511335A/pt not_active IP Right Cessation
  • 2005-04-18 RU RU2006140233/06A patent/RU2358154C2/ru active
  • 2005-04-18 KR KR1020067024894A patent/KR20070026538A/ko not_active Application Discontinuation
  • 2005-04-18 ES ES05733928T patent/ES2289973T3/es active Active
  • 2005-04-18 CA CA002567445A patent/CA2567445A1/en not_active Abandoned
  • 2005-04-18 AU AU2005250538A patent/AU2005250538A1/en not_active Abandoned
  • 2005-04-18 US US11/569,497 patent/US20070274850A1/en not_active Abandoned
  • 2005-04-18 JP JP2007513716A patent/JP2008500483A/ja not_active Withdrawn
  • 2005-04-18 EP EP05733928A patent/EP1749152B1/de not_active Not-in-force
  • 2005-04-18 WO PCT/EP2005/004113 patent/WO2005119057A1/de active IP Right Grant
  • 2005-04-18 CN CN2005800171767A patent/CN1961152B/zh not_active Expired - Fee Related
  • 2005-04-18 AT AT05733928T patent/ATE397726T1/de not_active IP Right Cessation

Patent Citations (5)

Also Published As

Similar Documents

Legal Events