EP1651870B1 - Hydraulic control system for building machinery, particularly excavators - Google Patents

Hydraulic control system for building machinery, particularly excavators Download PDF

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Publication number
EP1651870B1
EP1651870B1 EP04762373A EP04762373A EP1651870B1 EP 1651870 B1 EP1651870 B1 EP 1651870B1 EP 04762373 A EP04762373 A EP 04762373A EP 04762373 A EP04762373 A EP 04762373A EP 1651870 B1 EP1651870 B1 EP 1651870B1
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EP
European Patent Office
Prior art keywords
pump
hydraulic
passage
control system
pressure
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.)
Expired - Lifetime
Application number
EP04762373A
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German (de)
French (fr)
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EP1651870A1 (en
Inventor
Volker BÖSEBECK
Erik Lautner
Jürgen Weber
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CNH Industrial Baumaschinen GmbH
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CNH Baumaschinen GmbH
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Publication of EP1651870A1 publication Critical patent/EP1651870A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0871—Channels for fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31582—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having multiple pressure sources and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a hydraulic control system for construction machines, in particular for controlling hydraulic consumers of an excavator, according to the preamble of patent claim 1.
  • LUDV load-sensing system
  • a widely used hydraulic control system is also the Negative Flow Control (NFC).
  • NFC Negative Flow Control
  • the spool deflection leads to a reduction in the volume flow in the open-center channel and thus to a reduction in the control flow used at the negative flow control valve.
  • the change in the control flow rate is converted into a pressure difference, which is used as a control signal for pump control.
  • load compensation is not done by pressure compensators.
  • the object of the invention is to develop a hydraulic control system with which the disadvantages of the series supply can be overcome and a need-based supply of the consumer with a hydraulic fluid while maintaining the advantages of simple internal summation of pump flow rates and the ability to operate with different Systemdrückem allows becomes.
  • Another object of the invention is also to be able to extend the existing main control block optional to integrate more hydraulic consumers without considerable design effort in the hydraulic control system can.
  • this complex and apparently multifaceted task can be solved by providing, in addition to the existing pump channels P01 and P02, which ensure the serial supply of the hydraulic consumers with a hydraulic fluid, two further pump channels arranged parallel to these and not passing through the spool valves P1 and P2 are provided for ensuring a parallel supply of the hydraulic consumers by means of the spool of the main control block of the construction machine.
  • a second bridge channel is provided in each section of the main control block, which forms a ring bridge together with the first bridge channel. From the pump parallel channels P1 and P2, the ring bridge can be assigned an additional volume flow.
  • the metering can be realized in a flexible manner by various valve functions, such as throttle, throttle check valve, Pressure balance etc.
  • the existing hydraulic control system is flexible expanded to the effect that now each consumer is supplied by means of its associated spool as needed in terms of the desired volume flow, as far as it allows the installed maximum flow rate of the machine.
  • All consumers can be operated simultaneously; in the case of the use of pressure compensators also load pressure compensated and independently. This leads to a higher level of comfort and to a safer operation.
  • Operational management means all those operations which the operator of the construction machine makes use of the hydraulic consumers, e.g. of the spoon, the jib or the driving, complete.
  • the additional pump passages P1 and P2 extend in the direction of the longitudinal axis of the main control block parallel to the existing pump passages P01 and P02, the pump passages P1 and P01 being supplied by a first pump and the pump passages P2 and P02 being supplied by the second pump.
  • the pump channels P01 and P02 supply the hydraulic consumers in a conventional manner in series and the pump channels P1 and P2 additionally supply the hydraulic consumers in parallel via the associated control valves.
  • the first pump and the second pump thus each feed a series channel and a parallel channel, namely the pump channels P01 and P1 and the pump channels P02 and P2.
  • the main control block can consist of a monolithic casting or a plurality of similar castings joined together.
  • the main control block is divided into several sections, in each of which a control slide is arranged for a consumer.
  • All pump passages extend in the direction of the longitudinal axis of the main control block from entry into the main control block to a closing element.
  • the individual to a main control block juxtaposed and hydraulically coupled sections with 8/3-way spools have, as disclosed in the patent DE 23 64 282 C3, each having a first bridge channel, the pump channels P01 and P02 with the consumer-side control edges A and B connects.
  • the spool sections according to the invention on a second bridge channel, via which the 8/3-way spool and thus the consumer-side control edges A and B are supplied by means of the additional pump ports P1 and P2 with the hydraulic fluid.
  • These two bridge channels are arranged in such a ring and hydraulically coupled together that they form a common ring bridge, from the volume flow for the consumer-side control edges A and B can be removed.
  • connection from the pump passages P1 and P2 to the ring bridge may optionally be formed by check valves and / or throttle check valves and / or pressure compensators and / or blind plugs.
  • the main control block be supplemented by attachable option blocks to the extent that additional hydraulic consumers or attachments can be integrated into the hydraulic system, without having to make a costly and unfavorable additional hoses.
  • the option blocks have the same channel structure as the main control block.
  • the arrangement of the option blocks takes place between the end plate and the main control block, which preferably includes the basic functions of a construction machine.
  • the limitation of the volume flow of the powered by an option block hydraulic consumer can be realized in a particularly advantageous manner by a stroke limitation of the control rod.
  • the option block has a conventional pressure compensator.
  • a desired volume flow for the additional consumers connected to this spool can be provided independent of the load pressure.
  • the consumer powered by the option block remains unaffected by other hydraulic consumers of the main control block.
  • the arrangement of the pressure compensator can be done either between the pump channels P1 and / or P2 and the annular bridge channel.
  • a controllable hammer valve in the main control block is arranged.
  • the hammer valve has a main stage and a pilot stage for driving them, wherein the valve inserts used in the main stage for cost and standardization reasons are identical to those of the check valves described later.
  • this hammer valve can be functionally assigned to both the spool of section 6 and the spool of an option block.
  • a summing valve is provided, which is arranged in a closing element of the main control block. If necessary, this summing valve can be used to realize a combination of volume flows of the hydraulic fluid flowing in the pump passages P1 and P2 with the aim of supplying this combined volume flow to a single hydraulic consumer.
  • implements that require more volume flow to fulfill their function than can be provided by a single hydraulic pump can thus be supplied according to the invention.
  • the pump channel P02 can be provided.
  • the inserted and fixed pressure valve With a specific response pressure realized as a pilot stage, the necessary pressure level in the parallel channel P2, so that the additional functions in the option blocks are provided with increased priority, before the remaining volume flow is provided to the hydraulic system in the entire pump channel P02.
  • the hydraulic control system according to the invention is basically designed as a two-pressure system, wherein the two pumps arranged in parallel can, if necessary, cooperate hydraulically such that the hydraulic control system can be operated as an impression system with a summation of the volume flows of the first and second pump.
  • each pump supplies hydraulic fluid to an existing pump channel and pump channel according to the present invention, double action of each spool with hydraulic fluid can be realized, resulting in a desired redundancy with respect to the hydraulic supply.
  • Fig. 1 illustrates the basic hydraulic structure of the hydraulic control system 1 of the invention.
  • the main control block generally indicated by reference numeral 2, comprises, as exemplified, six sections 3, an option block 11 and a closure element 14 which are hydraulically and mechanically connected together to form a solid block , Within the sections 3 and the option block 11 displaceable spool 19 are arranged, with which the individual hydraulic consumers are supplied with hydraulic fluid.
  • Orthogonal to the control valves 19, the existing pump channels P01 17.1 and P02 17.2 are formed, which extend in the direction of the longitudinal axis of the main control block 2. In this pump channels 17.1, 17.2, the hydraulic fluid pressurized by means of the pumps 5, not shown, flows to the spools 19.
  • the additional pump passages P1, 17.3 and P2 17.4 extend in the direction of the longitudinal axis of the main control block 2 parallel to the existing pump passages P01, 17.1 and P02, 17.2.
  • the pump channels P1 17.3 and P01 17.1 being supplied by a first pump 5.1 and the pump channels P2 17.4 and P02 17.2 being supplied by a second pump 5.2.
  • the pump channels P01 17.1 and P02 17.2 the hydraulic consumers 18, not shown in series in a conventional manner and the pump channels P1 17.3 and P2 17.4, the hydraulic consumers 18 via the associated spool 19 in addition to parallel.
  • the first pump 5.1 and the second pump 5.2 thus each feed a series channel and a parallel channel, namely the pump channels P01 17.1 and P1 17.3 or the pump channels P02 17.2 and P2 17.4.
  • the pressurized pump lines PL1 20.1 and PL2 20.2 in the main control block 2 branch into the pump channels P01 17.1 and P1 17.3 or P02 17.2 and P2 17.4.
  • All pump channels 17 extend in the direction of the longitudinal axis of the main control block 2 from the entry into the main control block 2 via the option block 11 up to a closing element 14.
  • the channel structure in each section 3 is almost identical, ie all sections 3 have similar breakthroughs for the formation of the pump channels 17 on.
  • each spool 19 With hydraulic fluid, as shown in more detail in Fig. 2, via a first bridge channel 6.1, which has two load-holding valves 24.
  • a desired position of the opening paths of the 8/3-way valve achieved.
  • two additional pump channels P1 17.3 and P2 17.4 are provided, which extend parallel to the existing pump channels P01 17.1 and P02 17.2 in the longitudinal axis of the main control block 2.
  • each individual section 3 has an opening for each channel 17.3, 17.4, so that a connection to the bridge channel 6.2 is given.
  • Fig. 2 shows a detailed view of a section 3 of the main control block 2, as an example of the spool 19 of the hydraulic consumer 18, not shown, bucket cylinder.
  • the section 3 comprises at least one spool 19 with its consumer-side control edges A and B 21, two bridge channels 6.1, 6.2, two load-holding valves 24, a throttle check valve 7, a blind plug 8 and two secondary pressure limiting valves 10th
  • the existing first bridge channel 6.1 is arranged to the right of the spool valve 19 and the second bridge channel 6.2 according to the invention to the left of the spool valve 19.
  • Both bridge channels 6.1, 6.2 are arranged to each other such that they together form a ring bridge 6.
  • the existing pump channels P01 17.1 and P02 17.2 and the spool 19 with its consumer-side control edges A and B 21 are arranged in a first imaginary plane, which is vertically aligned in the illustrated figure.
  • the two additional pump channels P1 17.3 and P2 17.4 are arranged in a second imaginary plane, which is aligned parallel to the first plane.
  • the pump channels P1 17.3 and P01 17.1 are arranged mirror-symmetrically to the pump channels P2 17.4 and P02 17.2 with respect to a mirror axis which is aligned orthogonal to the first and to the second plane.
  • the first bridge channel 6.1 with the pump channels P01 17.1 and P02 17.2 and the consumer-side control edges A and B 21 of the spool 19 of section 3 and the invention second bridge channel 6.2 with the pump channels P1 17.3 and P2 17.4 and also with the consumer side Control edges A and B 21 of the spool 19 of the section 3 hydraulically coupled. Consequently, the spool 19 can be used to supply e.g. of the bucket cylinder are supplied with hydraulic fluid through the pump channels P01 17.1, P02 17.2 and P1 17.3.
  • the blind plug 8 closes in the illustrated figure the pump channel P2 17.4.
  • the first bridge channel 6.1 has two load-holding valves 24, while a throttle check valve 7 and a blind plug 8 are arranged in the second bridge channel 6.2 are. It will be apparent to those skilled in the art that the secondary pressure relief valves 10 are placed on the consumer side of the spool valve 19. The check valves 16 close in this arrangement, the unspecified labeled consumer channels A and B such that no further externally arranged check valve blocks to fulfill the function are necessary.
  • a pressure compensator 9 may be arranged, whereby the spool 19 of the section 3 and thus the entire hydraulic control system 1 is very flexible configurable for the requirements of the user.
  • the section 3, which is not shown for the hydraulic consumer 18 / boom, has no second bridge 6.2. Since the hydraulic supply of the cylinder of the boom is provided with a sufficiently high priority with respect to an undersupply, this section 3 can also be formed without the second bridge 6.2 according to the invention.
  • the cylinder of the boom is supplied for lifting primarily from the existing pump channels P01 17.1 and P02 17.2. The lowering of the boom takes place using its own weight and a specially designed hollow control slide, wherein from the piston chamber of the cylinder, a partial volume flow through the spool 19 is used to fill the annular space of the cylinder. Due to this regenerative function, no pump 5 is necessary for the sinking operation.
  • a similarly designed regenerative function can also be used for the control of the handle cylinder.
  • the use of check valves 16 is optionally possible, for example, if an unwanted lowering of the boom at a longer Service life should be avoided by leakage losses of the hydraulic circuit.
  • check valves 16 and pipe rupture protection can be used to meet the required safety regulations in relation to the use of the construction machine as a hoist.
  • the second bridge 6.2 in addition to a pressure compensator 9 an additional blanking plug 8.
  • FIG. 3 illustrates a detailed representation of the section 6 of the main control block 2 in conjunction with an option block 11 and a closure element 14.
  • section 6 of the main control block 2 is a spill valve 13, a hammer valve 12, a pressure compensator 9, a current regulator 27 for load pressure relief, a first part of the shuttle valve chain 26 and a spool 19th
  • the option block 11 is connected to the front side of the main control block 2 and includes a further spool 19, a pressure compensator 9, the load pressure limiting 23 and a second part of the shuttle valve chain 26.
  • the summing valve 15 according to the invention is arranged within the end element 14, which is frontally to the option block 11th followed.
  • connection between the main control block 2, option block 11 and end element 14 is carried out by a respective flange, which are additionally secured by pressure-tight and temperature-resistant seals.
  • flange-mounted option blocks 11 can be arranged on one end face of the main control block 2 in order to integrate further hydraulic consumers 18, not shown, into the hydraulic control system 1 without additional effort for the tubing.
  • the option block 11 has a second bridge channel 6.2, which is formed together with the first bridge channel 6.1 to form a ring bridge 6.
  • the option blocks 11 have an identical channel structure 17 as the main control block 2.
  • a pressure compensator 9 is arranged, which establishes the connection between P2 17.4 and the second bridge channel 6.2 to ensure the desired load independence of the hydraulic consumer 18.
  • two secondary pressure limiting valves 10 are arranged, which protect the hydraulic control system 1 against inadmissible external load pressures.
  • FIG. 5 illustrates a detailed illustration of an overflow valve 13 which is arranged in the main control block 2.
  • the overflow valve 13 connects the pump channel P2 17.4 and the pump channel P02 17.2 such that the non-illustrated hydraulic consumers 18 in the option blocks 11 or by the hydraulic consumer section 6 unnecessary volume flow, which is provided by a pump 5.2, upon reaching a defined pressure from the pump channel P2 17.4 to the pump channel P02 17.2 can flow.
  • the fixed pressure relief valve 13.1 as a pilot stage of the spill valve 13 realizes the necessary pressure level in the pump channel P2 17.4, whereby the priority supply of attachments is ensured with hydraulic fluid.
  • the pilot valve 13.1 acts in an advantageous manner to the internal pilot pressures of the spill valve 13.
  • a connected to an additional nozzle current regulator 27 is provided, which contributes to the discharge of the hydraulic signaling channel in that no undesirable hydraulic restraints occur.
  • the supply of the hydraulic consumers 18 of the option block 11 or of the consumer in section 6 of the main control block 2 is realized by the pump channel P2 17.4, while the pump channel P02 17.2 transfers the hydraulic volume flow not required by these consumers to the overall system.
  • the residual volume flow of the pump 5.2 which is not used by the optional consumers, is also available to the overall system.
  • a controllable inventive summing valve 15 can then be provided if a hydraulic consumer 18 requires more volumetric flow than can be provided by the pump 5.2. These are usually attachments, which are supplied by means of the spool 19 primarily in the option blocks 11 by the pump 5.2 via the pump port P2 17.4 with hydraulic fluid.
  • This summing valve 15 is arranged in the closing element 14 of the main control block 2, as shown in FIG. 6 can be seen. If necessary, the volume flows of the pump channels P1 17.3 and P2 17.4 are combined and fed to a hydraulic consumer 18. Structurally, the summing valve 15 is such designed such that the hydraulic fluid volume flow from the pump passage P1 17.3 flows into the pump passage P2 17.4.
  • the pump channel P1 17.3 has in the region of the end element 14 to a check valve 22 to prevent backflow of the hydraulic fluid.
  • the hammer valve 12 has a main stage and a pilot stage 12.1, wherein for cost and standardization reasons, the valve core of this main stage is the valve insert of the check valves 16 identical.
  • the Druckabgriffsblende 12.2 allows an intrinsic control pressure tap for the pilot stage 12.1, which is used for control pressure relief or for Steuerettabeetzwegung, respectively for opening or closing, the main stage.
  • the actuation of the spool 19 of all sections 3 and the spool 19 of the option blocks 11 are preferably carried out by an electro-hydraulic pilot control, whereby a conventional hydraulic pilot control is possible.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

The invention relates to a hydraulic control system for building machinery, particularly for controlling hydraulic consumers of an excavator. According to the invention, pump channels which ensure that the hydraulic consumers are supplied in parallel by means of a spool valve of the main control unit of the piece of building machinery are provided in addition to previously existing pump channels that ensure said hydraulic consumers are serially supplied with hydraulic fluid. The additional pump channels are arranged parallel to the previously existing ones.

Description

Die Erfindung betrifft ein hydraulisches Steuersystem für Baumaschinen, insbesondere zur Steuerung von hydraulischen Verbrauchern eines Baggers, gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control system for construction machines, in particular for controlling hydraulic consumers of an excavator, according to the preamble of patent claim 1.

Bekannt aus dem Stand der Technik ist ein Load-Sensing-System (LUDV) mit proportionaler Förderstromabsenkung für alle hydraulischen Verbraucher, wenn der durch die Pumpe bereitgestellte Hydraulikfluidvolumenstrom nicht zur Versorgung aller hydraulischen Verbraucher ausreicht. Diese Regelstrategie wird durch Druckwaagen umgesetzt, die in Bezug zum Steuerschieber nachgeschaltet angeordnet sind. Mittels der Druckwaagen wird die Druckdifferenz über der verbraucherseitigen A-B-Steuerkante konstant und damit lastunabhängig gehalten.Known from the prior art is a load-sensing system (LUDV) with proportional flow reduction for all hydraulic consumers when the provided by the pump hydraulic fluid flow is not sufficient to supply all hydraulic consumers. This control strategy is implemented by pressure compensators, which are arranged downstream with respect to the spool. By means of the pressure compensators, the pressure difference over the consumer-side A-B control edge is kept constant and thus load-independent.

Ein weit verbreitetes hydraulisches Steuersystem ist auch das Negative-Flow-Control (NFC). Hierbei führt die Steuerschieberauslenkung zu einer Reduzierung des Volumenstroms im open-center-Kanal und damit zu einer Absenkung des am Negative-Flow-Control-Ventils genutzten Steuervolumenstroms. Im Negative-Flow-Control-Ventil wird die Änderung des Steuervolumenstroms in eine Druckdifferenz gewandelt, die als Steuersignal zur Pumpenregelung genutzt wird. Im Gegensatz zu den Load-Sensing-Systemen erfolgt keine Lastkompensation durch Druckwaagen.A widely used hydraulic control system is also the Negative Flow Control (NFC). In this case, the spool deflection leads to a reduction in the volume flow in the open-center channel and thus to a reduction in the control flow used at the negative flow control valve. In the negative flow control valve, the change in the control flow rate is converted into a pressure difference, which is used as a control signal for pump control. In contrast to the load-sensing systems, load compensation is not done by pressure compensators.

Im Stand der Technik ist des Weiteren aus der Patentschrift DE 23 64 282 C3 das Bedarfssteuerungssystem (PMSIII) bekannt. Kennzeichnend für dieses Steuersystem ist, dass die Pumpen bei steigendem Steuerdruck auf ein größeres Verdrängungsvolumen gemäß dem "Positiv-Control-Prinzip" eingestellt werden. Dabei verringert sich der Querschnitt der pumpenseitigen Steuerkanten C1 und C2, wobei der Fluidvolumenstrom vor diesen Steuerkanten C1 und C2 angestaut wird. Gleichzeitig beginnen sich die verbraucherseitigen Steuerkanten A und B zu öffnen, wodurch sowohl der Lastdruck der Verbraucher wie auch der durch die Steuerkanten C1 und C2 aufgebaute Systemdruck auf die Lasthalteventile wirken, bis der Systemdruck die Lasthalteventile öffnet, so dass der Fluidvolumenstrom über die sich vergrößernden Querschnitte der verbraucherseitigen Steuerkanten A und B fließen kann.In the prior art is further known from the patent DE 23 64 282 C3 the demand control system (PMSIII). Characteristic of this control system is that the pumps are set with increasing control pressure to a larger displacement volume according to the "positive control principle". This reduces the cross section of the pump-side control edges C1 and C2, wherein the fluid volume flow before these control edges C1 and C2 is accumulated. At the same time, the consumer-side control edges A and B start to open, whereby both the load pressure of the consumer and the system pressure built up by the control edges C1 and C2 act on the load-holding valves until the system pressure opens the load-holding valves, so that the fluid volume flow over the increasing cross-sections the consumer-side control edges A and B can flow.

Nach der Gegenüberstellung der in der Praxis am meisten angewendeten Steuersysteme für Baumaschinen wird deutlich, dass gemäß des referierten Bedarfssteuerungssystems (PMSIII) mittels der 8/3-Wege-Steuerschieber und der entsprechenden Blockstruktur ein Verbraucher ohne zusätzliche Komponenten mit einem Fluidvolumenstrom versorgt werden kann, der sich durch die blockinterne Summierung von zwei Pumpen ergibt. Daneben gestattet die Blockstruktur durch die Verwendung von zwei Pumpen, mit denen seriell die Steuerschieber mit Hydraulikfluid beaufschlagt werden, dass auf einfache Weise mit zwei, in Verbindung mit dem Schwenkenkreis sogar mit drei, verschiedenen Systemdrücken operiert werden kann. Ein weiterer nicht zu unterschätzender Vorteil liegt darin begründet, dass durch die parallele Ansteuerung der beiden Pumpen und Steuerschieber verschiedene Systemabstimmungen erzielt werden können, die in Abhängigkeit des Einsatzes der Baumaschine oder des Kundenwunsches zu sehr unterschiedlichem Maschinenverhalten führen. Dadurch, dass die einzelnen hydraulischen Funktionen nicht lastdruckkompensiert angesteuert werden, bleibt für den Bediener jederzeit das Gefühl für den Grabprozess erhalten.After comparing the most widely used in practice control systems for construction machinery is clear that according to the referenced demand control system (PMSIII) by means of the 8/3-way spool and the corresponding block structure, a consumer can be supplied without additional components with a fluid flow, the resulting from the block-internal summation of two pumps. In addition, the block structure, by the use of two pumps which serially apply hydraulic fluid to the spools, can be easily operated with two, in conjunction with the pan, even with three different system pressures. Another advantage not to be underestimated lies in the fact that the parallel control of the two pumps and spool different system harmonizations can be achieved, which lead to very different machine behavior depending on the use of the construction machine or the customer's request. The fact that the individual hydraulic functions are not controlled load pressure compensated, the feel for the excavation process remains for the operator at any time.

Die hydraulische Entkopplung der einzelnen Funktionen erfolgt zudem auf einfachem Wege mittels der C-Steuerkanten der Steuerschieber, die bei Ansteuerung bzw. Auslenkung der Steuerschieber die Pumpenkanäle hubabhängig verschließen. Ferner werden auch keine ventilartigen Druckwaagen benötigt, was zum einen energetisch effizient ist und zum anderen zu einem einfach aufgebauten hydraulischen Steuersystem führt.The hydraulic decoupling of the individual functions also takes place in a simple way by means of the C-control edges of the spool, the control or deflection the spool closes the pump channels depending on the stroke. Furthermore, no valve-like pressure compensators are needed, which is both an energetically efficient and on the other hand leads to a simple design hydraulic control system.

Trotz dieses ausgereiften Steuersystems gemäß dem Patent DE 23 64 282 C3 ergeben sich einige Missstände, die in der Natur der Hauptsteuerblockarchitektur liegen. Beispielsweise haftet der Reihenschaltung von Steuerschiebern in Verbindung mit den C-Kanten der Nachteil an, dass gegebenenfalls Verbraucher unterversorgt werden. Insbesondere bei denen in der Mitte des Hauptsteuerblocks angeordneten Steuerschiebern besteht die Gefahr, dass die von diesen Steuerschiebern mit einem Hydraulikfluid unterversorgten Verbraucher in der ihr zugedachten Aufgabe beschränkt werden. Diese z.T. eingeschränkte Versorgung von Verbrauchern wird zusätzlich noch von der begrenzten Steuerbarkeit von Optionen oder Zusatzfunktionen ergänzt, insbesondere für den Bedarfsfall eines definierten Volumenstroms. In der Vergangenheit musste mit Inbetriebnahme einer Zusatzfunktion, wie z.B. einer Fräse oder einer Magnetanlage, ein definierter Volumenstrom mittels Fixierung einer der beiden Hauptpumpen auf ein definiertes Verdrängungsvolumen eingestellt werden. Dadurch wurde das übrige hydraulische System in seinem Funktionsumfang stark eingeschränkt, da eine der beiden Hauptpumpen nur exklusiv dieser Zusatzfunktion zur Verfügung stand. Eine stirnseitige Erweiterung des bisherigen Hauptsteuerblocks durch sogenannte Sandwich-Elemente für Sonderfunktionen ist technisch nicht möglich. Die Einbindung von Sonderfunktionen muss daher mit zusätzlichen Ventilen und Verschlauchungen vorgenommen werden, was zu nicht unerheblichem technischen Aufwand und damit verbundenen Kosten führt.Despite this sophisticated control system according to the patent DE 23 64 282 C3, there are some deficiencies that lie in the nature of the main control block architecture. For example, the series connection of control slides in conjunction with the C edges has the disadvantage that, if necessary, consumers are underserved. In particular, in which arranged in the middle of the main control block spools there is a risk that the undersized by these spools with a hydraulic fluid consumers are limited in their intended task. This sometimes limited supply of consumers is additionally supplemented by the limited controllability of options or additional functions, in particular for the need of a defined volume flow. In the past, when commissioning an additional function, such as a tiller or a magnetic system, a defined volume flow had to be set by fixing one of the two main pumps to a defined displacement volume. As a result, the rest of the hydraulic system was severely limited in its scope of functions, since one of the two main pumps was only available exclusively for this additional function. A frontal extension of the previous main control block by so-called sandwich elements for special functions is not technically possible. The integration of special functions must therefore be carried out with additional valves and tubing, which leads to not inconsiderable technical complexity and associated costs.

Die Aufgabe der Erfindung besteht darin, ein hydraulisches Steuersystem zu entwickeln, mit dem die Nachteile der Reihenversorgung überwunden werden und eine bedarfsgerechte Versorgung der Verbraucher mit einem Hydraulikfluid bei gleichzeitiger Beibehaltung der Vorteile der einfachen internen Summierung von Pumpenvolumenströmen und der Möglichkeit mit verschiedenen Systemdrückem zu operieren ermöglicht wird. Eine weitere Aufgabe der Erfindung besteht zudem darin, den vorhandenen Hauptsteuerblock optional erweitern zu können, um weitere hydraulische Verbraucher ohne erheblichen konstruktiven Aufwand in das hydraulische Steuersystem einbinden zu können.The object of the invention is to develop a hydraulic control system with which the disadvantages of the series supply can be overcome and a need-based supply of the consumer with a hydraulic fluid while maintaining the advantages of simple internal summation of pump flow rates and the ability to operate with different Systemdrückem allows becomes. Another object of the invention is also to be able to extend the existing main control block optional to integrate more hydraulic consumers without considerable design effort in the hydraulic control system can.

Diese Aufgabe wird erfindungsgemäß durch die Merkmale des Anspruchs 1 gelöst; die Unteransprüche zeigen weitere vorteilhafte Ausgestaltungen der Erfindung.This object is achieved by the features of claim 1; the dependent claims show further advantageous embodiments of the invention.

Überraschenderweise lässt sich diese komplexe und in ihrer Vielgestaltigkeit scheinbar unvereinbare Aufgabe dadurch lösen, indem zusätzlich zu den vorhandenen Pumpenkanälen P01 und P02, die die serielle Versorgung der hydraulischen Verbraucher mit einem Hydraulikfluid gewährleisten, parallel zu diesen angeordnete, nicht durch die Steuerschieber hindurchgehende zwei weitere Pumpenkanäle P1 und P2 zur Sicherstellung einer Parallelversorgung der hydraulischen Verbraucher mittels der Steuerschieber des Hauptsteuerblocks der Baumaschine vorgesehen sind. Erfindungsgemäß ist zusätzlich zu einem ersten Brückenkanal ein zweiter Brückenkanal in jeder Sektion des Hauptsteuerblocks vorgesehen, der gemeinsam mit dem ersten Brückenkanal eine Ringbrücke bildet. Von den Pumpenparallelkanälen P1 und P2 kann der Ringbrücke ein zusätzlicher Volumenstrom zugemessen werden. Die Zumessung kann dabei in flexibler Weise durch verschiedene Ventilfunktionen realisiert werden, wie Drossel, Drosselrückschlagventil, Druckwaage etc..Surprisingly, this complex and apparently multifaceted task can be solved by providing, in addition to the existing pump channels P01 and P02, which ensure the serial supply of the hydraulic consumers with a hydraulic fluid, two further pump channels arranged parallel to these and not passing through the spool valves P1 and P2 are provided for ensuring a parallel supply of the hydraulic consumers by means of the spool of the main control block of the construction machine. According to the invention, in addition to a first bridge channel, a second bridge channel is provided in each section of the main control block, which forms a ring bridge together with the first bridge channel. From the pump parallel channels P1 and P2, the ring bridge can be assigned an additional volume flow. The metering can be realized in a flexible manner by various valve functions, such as throttle, throttle check valve, Pressure balance etc.

Damit wird das vorhandene hydraulische Steuersystem dahingehend flexibel erweitert, dass nunmehr jeder Verbraucher mittels seines zugeordneten Steuerschiebers bedarfsgerecht hinsichtlich dem gewünschtem Volumenstrom versorgt wird, soweit es der installierte Maximalvolumenstrom der Maschine zulässt. Alle Verbraucher können simultan betrieben werden; im Fall des Einsatzes von Druckwaagen auch lastdruckkompensiert und unabhängig voneinander. Dies führt zu einem höheren Komfort und zu einer sichereren Betriebsführung. Unter Betriebsführung sind alle diejenigen Vorgänge zu verstehen, die der Bediener der Baumaschine unter Nutzung der hydraulischen Verbraucher, wie z.B. des Löffels, des Auslegers oder auch des Fahrens, vollzieht.Thus, the existing hydraulic control system is flexible expanded to the effect that now each consumer is supplied by means of its associated spool as needed in terms of the desired volume flow, as far as it allows the installed maximum flow rate of the machine. All consumers can be operated simultaneously; in the case of the use of pressure compensators also load pressure compensated and independently. This leads to a higher level of comfort and to a safer operation. Operational management means all those operations which the operator of the construction machine makes use of the hydraulic consumers, e.g. of the spoon, the jib or the driving, complete.

Bevorzugt erstrecken sich die zusätzlichen Pumpenkanäle P1 und P2 in Richtung der Längsachse des Hauptsteuerblocks parallel zu den vorhandenen Pumpenkanälen P01 und P02, wobei die Pumpenkanäle P1 und P01 durch eine erste Pumpe versorgt und die Pumpenkanäle P2 und P02 durch die zweite Pumpe versorgt werden. Damit versorgen die Pumpenkanäle P01 und P02 die hydraulischen Verbraucher in herkömmlicher Weise seriell und die Pumpenkanäle P1 und P2 die hydraulischen Verbraucher über die zugehörigen Steuerschieber zusätzlich parallel. Die erste Pumpe und die zweite Pumpe speisen damit jeweils einen Reihenkanal und einen Parallelkanal, nämlich die Pumpenkanäle P01 und P1 bzw. die Pumpenkanäle P02 und P2.Preferably, the additional pump passages P1 and P2 extend in the direction of the longitudinal axis of the main control block parallel to the existing pump passages P01 and P02, the pump passages P1 and P01 being supplied by a first pump and the pump passages P2 and P02 being supplied by the second pump. Thus, the pump channels P01 and P02 supply the hydraulic consumers in a conventional manner in series and the pump channels P1 and P2 additionally supply the hydraulic consumers in parallel via the associated control valves. The first pump and the second pump thus each feed a series channel and a parallel channel, namely the pump channels P01 and P1 and the pump channels P02 and P2.

Der weiteren Ausführung wird vorangestellt, dass der Hauptsteuerblock aus einem monolithischen Gussgebilde oder aus mehreren miteinander gefügten gleichartigen Gussteilen bestehen kann. Unabhängig von der Fertigung des Hauptsteuerblocks ist der Hauptsteuerblock in mehrere Sektionen unterteilt, in denen jeweils ein Steuerschieber für einen Verbraucher angeordnet ist.The further embodiment is preceded by the fact that the main control block can consist of a monolithic casting or a plurality of similar castings joined together. Independent of the production of the main control block, the main control block is divided into several sections, in each of which a control slide is arranged for a consumer.

Unmittelbar nach dem Eintritt der druckbeaufschlagten Pumpenleitungen PL1 und PL2 in den Hauptsteuerblock verzweigen diese sich in die Pumpenkanäle P01 und P1 bzw. P02 und P2. Alle Pumpenkanäle erstrecken sich in Richtung der Längsachse des Hauptsteuerblocks vom Eintritt in den Hauptsteuerblock bis zu einem Abschlusselement.Immediately after the entry of the pressurized pump lines PL1 and PL2 into the main control block, they branch into the pump channels P01 and P1 or P02 and P2. All pump passages extend in the direction of the longitudinal axis of the main control block from entry into the main control block to a closing element.

Die einzelnen zu einem Hauptsteuerblock aneinander gereihten und hydraulisch gekoppelten Sektionen mit 8/3-Wege-Steuerschiebern verfügen, wie in der Patentschrift DE 23 64 282 C3 offenbart, über jeweils einen ersten Brückenkanal, der die Pumpenkanälen P01 und P02 mit den verbraucherseitigen Steuerkanten A und B verbindet. Zusätzlich weisen die Steuerschieber-Sektionen erfindungsgemäß einen zweiten Brückenkanal auf, über die die 8/3-Wege-Steuerschieber und damit die verbraucherseitigen Steuerkanten A und B mittels der zusätzlichen Pumpenkanäle P1 und P2 mit dem Hydraulikfluid versorgt werden. Diese beiden Brückenkanäle sind derart ringförmig angeordnet und hydraulisch miteinander gekoppelt, dass sie eine gemeinsame Ringbrücke ausbilden, aus der Volumenstrom für die verbraucherseitigen Steuerkanten A und B entnommen werden kann.The individual to a main control block juxtaposed and hydraulically coupled sections with 8/3-way spools have, as disclosed in the patent DE 23 64 282 C3, each having a first bridge channel, the pump channels P01 and P02 with the consumer-side control edges A and B connects. In addition, the spool sections according to the invention on a second bridge channel, via which the 8/3-way spool and thus the consumer-side control edges A and B are supplied by means of the additional pump ports P1 and P2 with the hydraulic fluid. These two bridge channels are arranged in such a ring and hydraulically coupled together that they form a common ring bridge, from the volume flow for the consumer-side control edges A and B can be removed.

In Abhängigkeit von der Verwendung eines Steuerschiebers kann die Verbindung von den Pumpenkanälen P1 und P2 zur Ringbrücke optional ausgebildet sein durch Sperrventile und/oder Drosselrückschlagventile und/oder Druckwaagen und/oder Blindstopfen.Depending on the use of a control slide, the connection from the pump passages P1 and P2 to the ring bridge may optionally be formed by check valves and / or throttle check valves and / or pressure compensators and / or blind plugs.

Nach der Konzeption der Erfindung kann der Hauptsteuerblock durch anflanschbare Optionsblöcke dahingehend erweitert werden, dass zusätzliche hydraulische Verbraucher oder Anbaugeräte in das hydraulische System eingebunden werden können, ohne eine kostenintensive und unvorteilhafte Zusatzverschlauchung vornehmen zu müssen. Die Optionsblöcke weisen die gleiche Kanalstruktur wie der Hauptsteuerblock auf. Die Anordnung der Optionsblöcke erfolgt zwischen der Abschlussplatte und dem Hauptsteuerblock, der vorzugsweise die Grundfunktionen einer Baumaschine beinhaltet. Die Begrenzung des Volumenstroms des von einem Optionsblock versorgten hydraulischen Verbrauchers kann hierbei in besonders vorteilhafter Weise durch eine Hubbegrenzung der Steuerstange realisiert werden.According to the conception of the invention, the main control block be supplemented by attachable option blocks to the extent that additional hydraulic consumers or attachments can be integrated into the hydraulic system, without having to make a costly and unfavorable additional hoses. The option blocks have the same channel structure as the main control block. The arrangement of the option blocks takes place between the end plate and the main control block, which preferably includes the basic functions of a construction machine. The limitation of the volume flow of the powered by an option block hydraulic consumer can be realized in a particularly advantageous manner by a stroke limitation of the control rod.

Durch eine zweckmäßige Ausbildung der C-Steuerkanten der Steuerschieber im Hinblick auf den Querschnitt wird unmittelbar auf die Wirkung der zusätzlichen Pumpenkanäle auf das hydraulische Steuersystem Einfluss genommen.By appropriate design of the C-control edges of the spool with respect to the cross section is directly influenced on the effect of the additional pump channels on the hydraulic control system.

In einer bevorzugten Ausführungsform der Erfindung weist der Optionsblock eine herkömmliche Druckwaage auf. Mittels dieser Druckwaage kann ein gewünschter Volumenstrom für den an diesen Steuerschieber angeschlossen zusätzlichen Verbraucher lastdruckunabhängig bereitgestellt werden. Damit bleibt der vom Optionsblock versorgte Verbraucher von anderen hydraulischen Verbrauchern des Hauptsteuerblockes unbeeinflusst. Die Anordnung der Druckwaage kann wahlweise zwischen den Pumpenkanälen P1 und/oder P2 und dem ringförmigen Brückenkanal erfolgen.In a preferred embodiment of the invention, the option block has a conventional pressure compensator. By means of this pressure compensator, a desired volume flow for the additional consumers connected to this spool can be provided independent of the load pressure. Thus, the consumer powered by the option block remains unaffected by other hydraulic consumers of the main control block. The arrangement of the pressure compensator can be done either between the pump channels P1 and / or P2 and the annular bridge channel.

Spezifische Anbaugeräte, wie z.B. Hydraulikhämmer, erfordern zu ihrer funktionsgemäßen Aufgabenerfüllung eine nahezu drucklose Rücklaufleitung zum Tank. Diesem Erfordernis wird dadurch Rechnung getragen, indem erfindungsgemäß ein steuerbares Hammerventil im Hauptsteuerblock angeordnet ist. Mit dieser bevorzugten Ausführungsform der Erfindung kann auf herkömmliche, extern angeordnete Zusatzventile und deren Verschlauchung zur Hammersteuerung weitestgehend verzichtet werden. Das Hammerventil weist eine Hauptstufe und eine Pilotstufe zu deren Ansteuerung auf, wobei die bei der Hauptstufe verwendeten Ventileinsätze aus Kosten- und Standardisierungsgründen mit denen der später beschriebenen Sperrventile identisch sind.Specific implements, such as hydraulic hammers, require a nearly unpressurized return line to the tank for their functional task fulfillment. This requirement is thereby taken into account by the present invention, a controllable hammer valve in the main control block is arranged. With this preferred embodiment of the invention can be largely dispensed with conventional, externally arranged additional valves and their tubing for hammer control. The hammer valve has a main stage and a pilot stage for driving them, wherein the valve inserts used in the main stage for cost and standardization reasons are identical to those of the check valves described later.

In Abhängigkeit der Ausrüstungsvariante der Baumaschine kann dieses Hammerventil funktionell sowohl dem Steuerschieber der Sektion 6 als auch dem Steuerschieber eines Optionsblockes zugeordnet werden.Depending on the equipment variant of the construction machine, this hammer valve can be functionally assigned to both the spool of section 6 and the spool of an option block.

Zur Lösung der Aufgabenstellung ist des Weiteren ein Summierventil vorgesehen, welches in einem Abschlusselement des Hauptsteuerblocks angeordnet ist. Mit diesem Summierventil kann im Bedarfsfall eine Vereinigung von Volumenströmen des in den Pumpenkanälen P1 und P2 strömenden Hydraulikfluids mit dem Ziel, diesen vereinigten Volumenstrom einem einzelnen hydraulischen Verbraucher zuzuführen, realisiert werden. Insbesondere Anbaugeräte, die mehr Volumenstrom zu ihrer Funktionserfüllung benötigen als von einer einzelnen Hydraulikpumpe bereitgestellt werden kann, können damit erfindungsgemäß versorgt werden.To solve the task further a summing valve is provided, which is arranged in a closing element of the main control block. If necessary, this summing valve can be used to realize a combination of volume flows of the hydraulic fluid flowing in the pump passages P1 and P2 with the aim of supplying this combined volume flow to a single hydraulic consumer. In particular, implements that require more volume flow to fulfill their function than can be provided by a single hydraulic pump can thus be supplied according to the invention.

Mit einer weiteren vorteilhaften konstruktiven Lösungsvariante, nämlich durch den Einsatz eines Überströmventils, kann der mittels der zweiten Pumpe über den Pumpenkanal P2 bereitgestellte Volumenstrom des Hydraulikfluids, der nicht von einem optionalen Verbraucher benötigt wird, dem Pumpenkanal P02 zur Verfügung gestellt werden. Das eingesetzte und festeingestellte Druckventil mit einem spezifischen Ansprechdruck realisiert als Pilotstufe das notwendige Druckniveau im Parallelkanal P2, so dass die zusätzlichen Funktionen in den Optionsblöcken mit erhöhter Priorität versorgt werden, bevor der restliche Volumenstrom dem hydraulischen Gesamtsystem im Pumpenkanal P02 zur Verfügung gestellt wird.With a further advantageous constructive solution variant, namely by the use of an overflow valve, the provided by means of the second pump via the pump passage P2 volume flow of the hydraulic fluid, which is not required by an optional consumer, the pump channel P02 can be provided. The inserted and fixed pressure valve With a specific response pressure realized as a pilot stage, the necessary pressure level in the parallel channel P2, so that the additional functions in the option blocks are provided with increased priority, before the remaining volume flow is provided to the hydraulic system in the entire pump channel P02.

Das erfindungsgemäße hydraulische Steuersystem ist grundsätzlich als Zweidrucksystem ausgebildet, wobei die beiden parallel angeordneten Pumpen im Bedarfsfall derart hydraulisch zusammenwirken können, dass das hydraulische Steuersystem als Eindrucksystem mit einer Summierung der Volumenströme der ersten und zweiten Pumpe betrieben werden kann.The hydraulic control system according to the invention is basically designed as a two-pressure system, wherein the two pumps arranged in parallel can, if necessary, cooperate hydraulically such that the hydraulic control system can be operated as an impression system with a summation of the volume flows of the first and second pump.

Es ist für den Fachmann nachvollziehbar, dass das erfindungsgemäße hydraulische System durch eine Kombination von Merkmalen einer Bedarfssteuerung und von Merkmalen einer aus dem Stand der Technik vorbekannten Load-Sensing-Steuerung gekennzeichnet ist. Da jede Pumpe einen vorhandenen Pumpenkanal und einen erfindungsgemäßen zusätzlichen Pumpenkanal mit Hydraulikfluid versorgt, kann folglich eine Doppelbeaufschlagung jedes Steuerschiebers mit Hydraulikfluid realisiert werden, was zu einer gewünschten Redundanz in Bezug auf die hydraulische Versorgung führt.It will be understood by those skilled in the art that the inventive hydraulic system is characterized by a combination of demand control features and features of prior art load sensing control. Consequently, since each pump supplies hydraulic fluid to an existing pump channel and pump channel according to the present invention, double action of each spool with hydraulic fluid can be realized, resulting in a desired redundancy with respect to the hydraulic supply.

Die signifikanten Vorteile und Merkmale der Erfindung gegenüber dem Stand der Technik sind im Wesentlichen:

  • Parallelversorgung der hydraulischen Verbraucher mit einem Hydraulikfluid mittels zweier zusätzlicher Pumpenkanäle P1 und P2,
  • Anordnung eines zusätzlichen zweiten Brückenkanals, der zusammen mit dem ersten Brückenkanal eine Ringbrücke bildet und damit eine redundante Versorgung der hydraulischen Verbraucher mit einem Hydraulikfluid aus den Pumpenkanälen P01, P02, P1 und P2 sicherstellt,
  • Kombination aus Merkmalen der Bedarfssteuerung und Merkmalen der Load-Sensing-Steuerung und damit Erhöhung der Flexibilität des hydraulischen Systems durch Verwendung von Lasthalteventilen, Druckdifferenzventilen, Druckminderventilen und Druckwaagen,
  • Erweiterungsmöglichkeit des Hauptsteuerblocks durch Optionsblöcke, wobei durch eine Hubbegrenzung der Steuerstange der Volumenstrom für den durch diesen Optionsblock versorgten Verbraucher begrenzt werden kann,
  • Verwendung eines Überströmventils, um im Bedarfsfall den mittels der zweiten Pumpe über den Pumpenkanal P2 bereitgestellten Anteil an Volumenstrom des Hydraulikfluids, der nicht von einem optionalen Verbraucher benötigt wird, dem Gesamtsystem über den Pumpenkanal P02 zur Verfügung zu stellen,
  • Verwendung eines Summierventil, um im Bedarfsfall eine Vereinigung von Volumenströmen des in den Pumpenkanälen P1 und P2 strömenden Hydraulikfluids zu gewährleisten und
  • Verwendung eines steuerbaren Hammerventils zur drucklosen Rückführung des Hydraulikfluids, wobei das Hammerventil innerhalb des Hauptsteuerblockes angeordnet ist, um zusätzliche Ventile oder Verschlauchung einzusparen.
The significant advantages and features of the invention over the prior art are essentially:
  • Parallel supply of the hydraulic consumers with a hydraulic fluid by means of two additional pump channels P1 and P2,
  • Arrangement of an additional second bridge channel, which forms a ring bridge together with the first bridge channel and thus ensures a redundant supply of the hydraulic consumers with a hydraulic fluid from the pump channels P01, P02, P1 and P2,
  • Combination of demand control features and load-sensing control features to increase the flexibility of the hydraulic system by using load-holding valves, differential pressure valves, pressure reducing valves and pressure compensators,
  • Extension possibility of the main control block by option blocks, whereby by a stroke limitation of the control rod the volumetric flow for the consumer supplied by this option block can be limited,
  • Use of an overflow valve in order, if necessary, to make available to the entire system via the pump channel P02 the proportion of volume flow of the hydraulic fluid, which is not required by an optional consumer, provided by the second pump via the pump channel P2,
  • Use of a summing valve to ensure, if necessary, a combination of volume flows of the hydraulic fluid flowing in the pump channels P1 and P2 and
  • Use of a controllable hammer valve for pressure-free return of the hydraulic fluid, wherein the hammer valve is located within the main control block to save additional valves or tubing.

Verschiedene Lösungen und Vorteile der Erfindung erschließen sich dem Fachmann des Weiteren aus der folgenden detaillierten Beschreibung einer bevorzugten Ausführungsform mit Bezug auf die anliegenden Zeichnungen; in diesen zeigen:

Fig. 1
hydraulische Grundstruktur des Hauptsteuer blocks,
Fig. 2
Detaildarstellung der Sektion Steuerschieber-Löffel,
Fig. 3
Detaildarstellung der hydraulischen Grundstruktur des Hauptsteuerblocks mit der Sektion 6 und Druckwaage, mit Überströmventil, mit integriertem Hammerventil, Detaildarstellung eines Optionsblockes mit einer Druckwaage und Lastdruckbegrenzung sowie eine Detaildarstellung der Abschlussplatte mit einem Summierventil,
Fig. 4
Detaildarstellung eines Optionsblocks unter Verwendung einer Druckwaage,
Fig. 5
Detaildarstellung des Hauptsteuerblockes unter Verwendung eines Überströmventils,
Fig. 6
Detaildarstellung der Abschlussplatte unter Verwendung eines Summierventils und
Fig. 7
Detaildarstellung des Hauptsteuerblockes unter Verwendung eines integrierten Hammerventils.
Various solutions and advantages of the invention will become apparent to those skilled in the art from the following detailed description of a preferred embodiment with reference to the accompanying drawings; in these show:
Fig. 1
hydraulic basic structure of the main control block,
Fig. 2
Detailed view of the section Spool Spoon,
Fig. 3
Detailed view of the hydraulic basic structure of the main control block with the section 6 and pressure compensator, with overflow valve, with integrated hammer valve, detail display of an option block with a pressure balance and load pressure limitation as well as a detailed representation of the end plate with a summing valve,
Fig. 4
Detail of an option block using a pressure balance,
Fig. 5
Detail view of the main control block using an overflow valve,
Fig. 6
Detail of the end plate using a summing valve and
Fig. 7
Detail of the main control block using an integrated hammer valve.

Fig. 1 illustriert die hydraulische Grundstruktur des erfindungsgemäßen hydraulischen Steuersystems 1. Der allgemein mit dem Bezugszeichen 2 gekennzeichnete Hauptsteuerblock umfasst, wie beispielhaft dargestellt, sechs Sektionen 3, einen Optionsblock 11 sowie ein Abschlusselement 14, die hydraulisch und mechanisch miteinander zu einem massiven Block verbunden sind. Innerhalb der Sektionen 3 und des Optionsblockes 11 sind verschiebbare Steuerschieber 19 angeordnet, mit denen die einzelnen hydraulischen Verbraucher mit Hydraulikfluid versorgt werden. Orthogonal zu den Steuerschiebern 19 sind die vorhandenen Pumpenkanäle P01 17.1 und P02 17.2 ausgebildet, die sich in Richtung der Längsachse des Hauptsteuerblocks 2 erstrecken. In diesen Pumpenkanälen 17.1, 17.2 strömt das mittels der nicht dargestellten Pumpen 5 druckbeaufschlagte Hydraulikfluid zu den Steuerschiebern 19. Erfindungsgemäß erstrecken sich die zusätzlichen Pumpenkanäle P1 17.3 und P2 17.4 in Richtung der Längsachse des Hauptsteuerblocks 2 parallel zu den vorhandenen Pumpenkanälen P01 17.1 und P02 17.2 , wobei die Pumpenkanäle P1 17.3 und P01 17.1 durch eine erste Pumpe 5.1 versorgt und die Pumpenkanäle P2 17.4 und P02 17.2 durch eine zweite Pumpe 5.2 versorgt werden. Damit versorgen die Pumpenkanäle P01 17.1 und P02 17.2 die nicht dargestellten hydraulischen Verbraucher 18 in herkömmlicher Weise seriell und die Pumpenkanäle P1 17.3 und P2 17.4 die hydraulischen Verbraucher 18 über die zugehörigen Steuerschieber 19 zusätzlich parallel. Die erste Pumpe 5.1 und die zweite Pumpe 5.2 speisen damit jeweils einen Reihenkanal und einen Parallelkanal, nämlich die Pumpenkanäle P01 17.1 und P1 17.3 bzw. die Pumpenkanäle P02 17.2 und P2 17.4. Nach dem Eintritt der druckbeaufschlagten Pumpenleitungen PL1 20.1 und PL2 20.2 in den Hauptsteuerblock 2 verzweigen sich diese in die Pumpenkanäle P01 17.1 und P1 17.3 bzw. P02 17.2 und P2 17.4. Alle Pumpenkanäle 17 erstrecken sich in Richtung der Längsachse des Hauptsteuerblocks 2 vom Eintritt in den Hauptsteuerblock 2 über den Optionsblock 11 bis hin zu einem Abschlusselement 14. Die Kanalstruktur in jeder Sektion 3 ist nahezu identisch, d.h. alle Sektionen 3 weisen gleichartige Durchbrüche zur Ausbildung der Pumpenkanäle 17 auf. Die Versorgung jedes Steuerschiebers 19 mit Hydraulikfluid erfolgt, wie in Fig. 2 detaillierter dargestellt, über einen ersten Brückenkanal 6.1, der zwei Lasthalteventile 24 aufweist. Mittels des Steuerschiebers 19 wird, wie für jeden Fachmann nachvollziehbar, eine gewünschte Stellung der öffnenden Pfade des 8/3-Wege-Ventils erzielt. Für den Fall einer erhöhten Bedarfsabnahme durch die beiden äußeren Steuerschieber 19 steht gegebenenfalls nicht mehr ausreichend Hydraulikfluid für die Steuerschieber 19 der innenliegenden Sektionen 3 zur Verfügung. Erfindungsgemäß sind deshalb zwei zusätzliche Pumpenkanäle P1 17.3 und P2 17.4 vorgesehen, die sich parallel zu den vorhandenen Pumpenkanälen P01 17.1 und P02 17.2 in der Längsachse des Hauptsteuerblocks 2 erstrecken. Neben der Ausbildung dieser Pumpenkanäle P1 17.3 und P2 17.4 weist jede einzelne Sektion 3 einen Durchbruch für jeden Kanal 17.3, 17.4 auf, so dass eine Verbindung zum Brückenkanal 6.2 gegeben ist.Fig. 1 illustrates the basic hydraulic structure of the hydraulic control system 1 of the invention. The main control block, generally indicated by reference numeral 2, comprises, as exemplified, six sections 3, an option block 11 and a closure element 14 which are hydraulically and mechanically connected together to form a solid block , Within the sections 3 and the option block 11 displaceable spool 19 are arranged, with which the individual hydraulic consumers are supplied with hydraulic fluid. Orthogonal to the control valves 19, the existing pump channels P01 17.1 and P02 17.2 are formed, which extend in the direction of the longitudinal axis of the main control block 2. In this pump channels 17.1, 17.2, the hydraulic fluid pressurized by means of the pumps 5, not shown, flows to the spools 19. According to the invention, the additional pump passages P1, 17.3 and P2 17.4 extend in the direction of the longitudinal axis of the main control block 2 parallel to the existing pump passages P01, 17.1 and P02, 17.2. the pump channels P1 17.3 and P01 17.1 being supplied by a first pump 5.1 and the pump channels P2 17.4 and P02 17.2 being supplied by a second pump 5.2. Thus supply the pump channels P01 17.1 and P02 17.2 the hydraulic consumers 18, not shown in series in a conventional manner and the pump channels P1 17.3 and P2 17.4, the hydraulic consumers 18 via the associated spool 19 in addition to parallel. The first pump 5.1 and the second pump 5.2 thus each feed a series channel and a parallel channel, namely the pump channels P01 17.1 and P1 17.3 or the pump channels P02 17.2 and P2 17.4. After the entry of the pressurized pump lines PL1 20.1 and PL2 20.2 in the main control block 2, these branch into the pump channels P01 17.1 and P1 17.3 or P02 17.2 and P2 17.4. All pump channels 17 extend in the direction of the longitudinal axis of the main control block 2 from the entry into the main control block 2 via the option block 11 up to a closing element 14. The channel structure in each section 3 is almost identical, ie all sections 3 have similar breakthroughs for the formation of the pump channels 17 on. The supply of each spool 19 with hydraulic fluid, as shown in more detail in Fig. 2, via a first bridge channel 6.1, which has two load-holding valves 24. By means of the control slide 19, as is understandable for any expert, a desired position of the opening paths of the 8/3-way valve achieved. In the event of an increased demand decrease by the two outer spool 19 is possibly no longer sufficient hydraulic fluid for the spool 19 of the inner sections 3 available. According to the invention therefore two additional pump channels P1 17.3 and P2 17.4 are provided, which extend parallel to the existing pump channels P01 17.1 and P02 17.2 in the longitudinal axis of the main control block 2. In addition to the formation of these pump channels P1 17.3 and P2 17.4, each individual section 3 has an opening for each channel 17.3, 17.4, so that a connection to the bridge channel 6.2 is given.

Fig. 2 zeigt eine Detaildarstellung einer Sektion 3 des Hauptsteuerblocks 2, beispielhaft für den Steuerschieber 19 des nicht dargestellten hydraulischen Verbrauchers 18 Löffelzylinder. Die Sektion 3 umfasst mindestens einen Steuerschieber 19 mit seinen verbraucherseitigen Steuerkanten A und B 21, zwei Brückenkanäle 6.1, 6.2, zwei Lasthalteventile 24, ein Drosselrückschlagventil 7, einen Blindstopfen 8 und zwei Sekundärdruckbegrenzungs-ventile 10.Fig. 2 shows a detailed view of a section 3 of the main control block 2, as an example of the spool 19 of the hydraulic consumer 18, not shown, bucket cylinder. The section 3 comprises at least one spool 19 with its consumer-side control edges A and B 21, two bridge channels 6.1, 6.2, two load-holding valves 24, a throttle check valve 7, a blind plug 8 and two secondary pressure limiting valves 10th

Gemäß dieser Darstellung ist der vorhandene erste Brückenkanal 6.1 rechts vom Steuerschieber 19 und der erfindungsgemäße zweite Brückenkanal 6.2 links vom Steuerschieber 19 angeordnet. Beide Brückenkanäle 6.1, 6.2 sind derart zueinander angeordnet, dass sie gemeinsam eine Ringbrücke 6 ausbilden. Die vorhandenen Pumpenkanäle P01 17.1 und P02 17.2 sowie der Steuerschieber 19 mit seinen verbraucherseitigen Steuerkanten A und B 21 sind in einer ersten gedachten Ebene angeordnet, die in der dargestellten Figur vertikal ausgerichtet ist. Die beiden zusätzlichen Pumpenkanäle P1 17.3 und P2 17.4 sind in einer zweiten gedachten Ebene angeordnet, die parallel zu der ersten Ebene ausgerichtet ist. Die Pumpenkanäle P1 17.3 und P01 17.1 sind spiegelsymmetrisch zu den Pumpenkanälen P2 17.4 und P02 17.2 in Bezug auf eine Spiegelachse angeordnet, die orthogonal zu der ersten und zu der zweiten Ebene ausgerichtet ist.According to this illustration, the existing first bridge channel 6.1 is arranged to the right of the spool valve 19 and the second bridge channel 6.2 according to the invention to the left of the spool valve 19. Both bridge channels 6.1, 6.2 are arranged to each other such that they together form a ring bridge 6. The existing pump channels P01 17.1 and P02 17.2 and the spool 19 with its consumer-side control edges A and B 21 are arranged in a first imaginary plane, which is vertically aligned in the illustrated figure. The two additional pump channels P1 17.3 and P2 17.4 are arranged in a second imaginary plane, which is aligned parallel to the first plane. The pump channels P1 17.3 and P01 17.1 are arranged mirror-symmetrically to the pump channels P2 17.4 and P02 17.2 with respect to a mirror axis which is aligned orthogonal to the first and to the second plane.

Zur gattungsmäßigen Funktionserfüllung ist der erste Brückenkanal 6.1 mit den Pumpenkanälen P01 17.1 und P02 17.2 sowie mit den verbraucherseitigen Steuerkanten A und B 21 des Steuerschiebers 19 der Sektion 3 und der erfindungsgemäße zweite Brückenkanal 6.2 mit den Pumpenkanälen P1 17.3 und P2 17.4 sowie ebenfalls mit den verbraucherseitigen Steuerkanten A und B 21 des Steuerschiebers 19 der Sektion 3 hydraulisch gekoppelt. Folglich kann der Steuerschieber 19 zur Versorgung z.B. des Löffelzylinders durch die Pumpenkanäle P01 17.1, P02 17.2 und P1 17.3 mit Hydraulikfluid beaufschlagt werden. Der Blindstopfen 8 verschließt in der dargestellten Figur den Pumpenkanal P2 17.4.For generic functional performance is the first bridge channel 6.1 with the pump channels P01 17.1 and P02 17.2 and the consumer-side control edges A and B 21 of the spool 19 of section 3 and the invention second bridge channel 6.2 with the pump channels P1 17.3 and P2 17.4 and also with the consumer side Control edges A and B 21 of the spool 19 of the section 3 hydraulically coupled. Consequently, the spool 19 can be used to supply e.g. of the bucket cylinder are supplied with hydraulic fluid through the pump channels P01 17.1, P02 17.2 and P1 17.3. The blind plug 8 closes in the illustrated figure the pump channel P2 17.4.

Der erste Brückenkanal 6.1 weist zwei Lasthalteventile 24 auf, währenddessen im zweiten Brückenkanal 6.2 jeweils ein Drosselrückschlagventil 7 und ein Blindstopfen 8 angeordnet sind. Es ist für den Fachmann ersichtlich, dass die Sekundärdruckbegrenzungsventile 10 auf der Verbraucherseite des Steuerschiebers 19 platziert sind. Die Sperrventile 16 verschließen in dieser Anordnung die nicht näher gekennzeichneten Verbraucherkanäle A und B derart, dass keine weiteren extern angeordneten Sperrventilblöcke zur Funktionserfüllung notwendig sind.The first bridge channel 6.1 has two load-holding valves 24, while a throttle check valve 7 and a blind plug 8 are arranged in the second bridge channel 6.2 are. It will be apparent to those skilled in the art that the secondary pressure relief valves 10 are placed on the consumer side of the spool valve 19. The check valves 16 close in this arrangement, the unspecified labeled consumer channels A and B such that no further externally arranged check valve blocks to fulfill the function are necessary.

Anstelle des Blindstopfens 8 oder des Drosselrückschlagventils 7 kann auch eine Druckwaage 9 angeordnet sein, wodurch der Steuerschieber 19 der Sektion 3 und mithin das gesamte hydraulische Steuersystem 1 sehr flexibel für die Anforderungen der Nutzer konfigurierbar ist.Instead of the dummy plug 8 or the throttle check valve 7, a pressure compensator 9 may be arranged, whereby the spool 19 of the section 3 and thus the entire hydraulic control system 1 is very flexible configurable for the requirements of the user.

In einer weiteren Ausgestaltung der Erfindung weist die für den nicht dargestellten hydraulischen Verbraucher 18/Ausleger zugehörige Sektion 3 keine zweite Brücke 6.2 auf. Da die hydraulische Versorgung des Zylinders des Auslegers mit einer genügend hohen Priorität in Bezug auf eine Unterversorgung ausgestattet ist, kann diese Sektion 3 auch ohne die erfindungsgemäße zweite Brücke 6.2 ausgebildet werden. Der Zylinder des Auslegers wird zum Heben vorrangig aus den vorhandenen Pumpenkanälen P01 17.1 und P02 17.2 versorgt. Das Senken des Auslegers erfolgt unter Nutzung seines Eigengewichtes und durch einen speziell gestalteten Hohlsteuerschieber, wobei aus dem Kolbenraum der Zylinder ein Teilvolumenstrom über den Steuerschieber 19 zur Füllung des Ringraumes der Zylinder genutzt wird. Durch diese Regenerativfunktion ist keine Pumpe 5 für den Senkenvorgang notwendig.In a further embodiment of the invention, the section 3, which is not shown for the hydraulic consumer 18 / boom, has no second bridge 6.2. Since the hydraulic supply of the cylinder of the boom is provided with a sufficiently high priority with respect to an undersupply, this section 3 can also be formed without the second bridge 6.2 according to the invention. The cylinder of the boom is supplied for lifting primarily from the existing pump channels P01 17.1 and P02 17.2. The lowering of the boom takes place using its own weight and a specially designed hollow control slide, wherein from the piston chamber of the cylinder, a partial volume flow through the spool 19 is used to fill the annular space of the cylinder. Due to this regenerative function, no pump 5 is necessary for the sinking operation.

Eine ähnlich gestaltete Regenerativfunktion kann auch für die Steuerung des Stielzylinders verwendet werden. Die Verwendung von Sperrventilen 16 ist optional möglich, wenn z.B. ein ungewolltes Absenken des Auslegers bei längeren Standzeiten durch Leckageverluste des Hydraulikkreises vermieden werden soll. Alternativ können anstelle von Sperrventilen 16 auch Rohrbruchsicherungen verwendet werden, um die erforderlichen Sicherheitsbestimmungen in Bezug auf den Einsatz der Baumaschine als Hebezeug zu erfüllen.A similarly designed regenerative function can also be used for the control of the handle cylinder. The use of check valves 16 is optionally possible, for example, if an unwanted lowering of the boom at a longer Service life should be avoided by leakage losses of the hydraulic circuit. Alternatively, instead of check valves 16 and pipe rupture protection can be used to meet the required safety regulations in relation to the use of the construction machine as a hoist.

In einer bevorzugten Ausgestaltung der Sektion 6 für den nicht dargestellten hydraulischen Verbraucher 18/Nackenzylinder der Baumaschine weist die zweite Brücke 6.2 neben einer Druckwaage 9 einen zusätzlichen Blindstopfen 8 auf.In a preferred embodiment of the section 6 for the hydraulic consumer 18 / neck cylinder of the construction machine, not shown, the second bridge 6.2 in addition to a pressure compensator 9 an additional blanking plug 8.

Fig. 3 illustriert eine Detaildarstellung der Sektion 6 des Hauptsteuerblocks 2 in Verbindung mit einem Optionsblock 11 und einem Abschlusselement 14.FIG. 3 illustrates a detailed representation of the section 6 of the main control block 2 in conjunction with an option block 11 and a closure element 14.

Signifikante Merkmale der Sektion 6 des Hauptsteuerblocks 2 sind ein Überströmventil 13, ein Hammerventil 12, eine Druckwaage 9, ein Stromregler 27 zur Lastdruckentlastung, ein erster Teil der Wechselventilkette 26 und ein Steuerschieber 19.Significant features of the section 6 of the main control block 2 are a spill valve 13, a hammer valve 12, a pressure compensator 9, a current regulator 27 for load pressure relief, a first part of the shuttle valve chain 26 and a spool 19th

Der Optionsblock 11 ist stirnseitig mit dem Hauptsteuerblock 2 verbunden und umfasst einen weiteren Steuerschieber 19, eine Druckwaage 9, die Lastdruckbegrenzung 23 und einen zweiten Teil der Wechselventilkette 26. Das erfindungsgemäße Summierventil 15 ist innerhalb des Abschlusselements 14 angeordnet, welches sich stirnseitig an den Optionsblock 11 anschließt.The option block 11 is connected to the front side of the main control block 2 and includes a further spool 19, a pressure compensator 9, the load pressure limiting 23 and a second part of the shuttle valve chain 26. The summing valve 15 according to the invention is arranged within the end element 14, which is frontally to the option block 11th followed.

Die Verbindung zwischen Hauptsteuerblock 2, Optionsblock 11 und Abschlusselement 14 erfolgt durch jeweils eine Flanschverbindung, die zusätzlich durch druckdichte und temperaturbeständige Dichtungen gesichert sind.The connection between the main control block 2, option block 11 and end element 14 is carried out by a respective flange, which are additionally secured by pressure-tight and temperature-resistant seals.

Bei gleichzeitigem Einsatz mehrerer Druckwaagen 9, beispielsweise zur Steuerung eines Verbrauchers über einen Optionsblock 11 und eines Verbrauchers über die Sektion 6 des Hauptsteuerblockes 2, erfolgt der Lastdruckvergleich mittels einer Wechselventilkette 26.With simultaneous use of multiple pressure compensators 9, for example for controlling a consumer via an option block 11 and a consumer via the section 6 of the main control block 2, the load pressure comparison is carried out by means of a shuttle valve chain 26th

Wie bereits vorgetragen, können anflanschbare Optionsblöcke 11 an einer Stirnseite des Hauptsteuerblocks 2 angeordnet werden, um weitere nicht dargestellte hydraulische Verbraucher 18 ohne zusätzlichen Aufwand für die Verschlauchung in das hydraulische Steuersystem 1 zu integrieren. Wie in Fig. 4 illustriert, weist der Optionsblock 11 einen zweiten Brückenkanal 6.2 auf, der gemeinsam mit dem ersten Brückenkanal 6.1 zu einer Ringbrücke 6 ausgebildet ist. Damit weisen auch die Optionsblöcke 11 eine identische Kanalstruktur 17 wie der Hauptsteuerblock 2 auf. Im Strömungspfad des zweiten Brückenkanals 6.2 ist eine Druckwaage 9 angeordnet, die die Verbindung zwischen P2 17.4 und dem zweiten Brückenkanal 6.2 herstellt, um die gewünschte Lastunabhängigkeit des hydraulischen Verbrauchers 18 sicherzustellen. Jeweils auf der Verbraucherseite des Steuerschiebers 19 sind zwei Sekundärdruckbegrenzungsventile 10 angeordnet, die das hydraulische Steuersystem 1 vor unzulässigen äußeren Lastdrücken schützen.As already stated, flange-mounted option blocks 11 can be arranged on one end face of the main control block 2 in order to integrate further hydraulic consumers 18, not shown, into the hydraulic control system 1 without additional effort for the tubing. As illustrated in FIG. 4, the option block 11 has a second bridge channel 6.2, which is formed together with the first bridge channel 6.1 to form a ring bridge 6. Thus, the option blocks 11 have an identical channel structure 17 as the main control block 2. In the flow path of the second bridge channel 6.2 a pressure compensator 9 is arranged, which establishes the connection between P2 17.4 and the second bridge channel 6.2 to ensure the desired load independence of the hydraulic consumer 18. In each case on the consumer side of the spool 19, two secondary pressure limiting valves 10 are arranged, which protect the hydraulic control system 1 against inadmissible external load pressures.

In Fig. 5 ist eine Detaildarstellung eines Überströmventils 13 illustriert, das im Hauptsteuerblock 2 angeordnet ist. Das Überströmventil 13 verbindet den Pumpenkanal P2 17.4 und den Pumpenkanal P02 17.2 derart, dass der von nicht dargestellten hydraulischen Verbrauchern 18 in den Optionsblöcken 11 oder von dem hydraulischen Verbraucher der Sektion 6 nicht benötige Volumenstrom, der durch eine Pumpe 5.2 bereitgestellt wird, beim Erreichen eines definierten Drucks vom Pumpenkanal P2 17.4 zu dem Pumpenkanal P02 17.2 strömen kann. Das festeingestellte Druckbegrenzungsventil 13.1 als Pilotstufe des Überströmventils 13 realisiert das notwendige Druckniveau im Pumpenkanal P2 17.4, wodurch die prioritäre Versorgung der Anbaugeräte mit Hydraulikfluid gewährleistet wird. Das Pilotventil 13.1 wirkt dazu in vorteilhafter Weise auf die internen Vorsteuerdrücke des Überströmventils 13. Ferner ist ein mit einer zusätzlichen Düse beschalteter Stromregler 27 vorgesehen, der zur Entlastung des hydraulischen Meldekanals insofern beiträgt, dass keine unerwünschten hydraulischen Einspannungen auftreten.FIG. 5 illustrates a detailed illustration of an overflow valve 13 which is arranged in the main control block 2. The overflow valve 13 connects the pump channel P2 17.4 and the pump channel P02 17.2 such that the non-illustrated hydraulic consumers 18 in the option blocks 11 or by the hydraulic consumer section 6 unnecessary volume flow, which is provided by a pump 5.2, upon reaching a defined pressure from the pump channel P2 17.4 to the pump channel P02 17.2 can flow. The fixed pressure relief valve 13.1 as a pilot stage of the spill valve 13 realizes the necessary pressure level in the pump channel P2 17.4, whereby the priority supply of attachments is ensured with hydraulic fluid. The pilot valve 13.1 acts in an advantageous manner to the internal pilot pressures of the spill valve 13. Furthermore, a connected to an additional nozzle current regulator 27 is provided, which contributes to the discharge of the hydraulic signaling channel in that no undesirable hydraulic restraints occur.

Die Versorgung der hydraulischen Verbraucher 18 des Optionsblockes 11 oder des Verbrauchers in Sektion 6 des Hauptsteuerblockes 2 wird durch den Pumpenkanal P2 17.4 realisiert, währenddessen über den Pumpenkanal P02 17.2 der von diesen Verbrauchern nicht benötigte Hydraulikvolumenstrom an das Gesamtsystem übergeben wird. Damit steht energetisch auch der von den optionalen Verbrauchern nicht genutzte Restvolumenstrom der Pumpe 5.2 dem Gesamtsysstem zur Verfügung.The supply of the hydraulic consumers 18 of the option block 11 or of the consumer in section 6 of the main control block 2 is realized by the pump channel P2 17.4, while the pump channel P02 17.2 transfers the hydraulic volume flow not required by these consumers to the overall system. Thus, energetically, the residual volume flow of the pump 5.2, which is not used by the optional consumers, is also available to the overall system.

Im Gegensatz dazu kann dann ein steuerbares erfindungsgemäßes Summierventil 15 vorgesehen werden, wenn ein hydraulischer Verbraucher 18 mehr Volumenstrom benötigt als von der Pumpe 5.2 bereitgestellt werden kann. Dabei handelt es sich üblicherweise um Anbaugeräte, die mittels der Steuerschieber 19 vorrangig in den Optionsblöcken 11 durch die Pumpe 5.2 über den Pumpenkanal P2 17.4 mit Hydraulikfluid versorgt werden. Dieses Summierventil 15 ist in dem Abschlusselement 14 des Hauptsteuerblocks 2 angeordnet, wie der Fig. 6 zu entnehmen ist. Hierbei werden die Volumenströme der Pumpenkanäle P1 17.3 und P2 17.4 im Bedarfsfall vereinigt und einem hydraulischen Verbraucher 18 zugeführt. Konstruktiv ist das Summierventil 15 derart ausgebildet, dass der Hydraulikfluidvolumenstrom aus dem Pumpenkanal P1 17.3 in den Pumpenkanal P2 17.4 strömt. Der Pumpenkanal P1 17.3 weist im Bereich des Abschlusselements 14 dazu ein Rückschlagventil 22 auf, um ein Rückströmen des Hydraulikfluids zu verhindern.In contrast, a controllable inventive summing valve 15 can then be provided if a hydraulic consumer 18 requires more volumetric flow than can be provided by the pump 5.2. These are usually attachments, which are supplied by means of the spool 19 primarily in the option blocks 11 by the pump 5.2 via the pump port P2 17.4 with hydraulic fluid. This summing valve 15 is arranged in the closing element 14 of the main control block 2, as shown in FIG. 6 can be seen. If necessary, the volume flows of the pump channels P1 17.3 and P2 17.4 are combined and fed to a hydraulic consumer 18. Structurally, the summing valve 15 is such designed such that the hydraulic fluid volume flow from the pump passage P1 17.3 flows into the pump passage P2 17.4. The pump channel P1 17.3 has in the region of the end element 14 to a check valve 22 to prevent backflow of the hydraulic fluid.

Mit der Anordnung eines steuerbaren Hammerventils 12 im Hauptsteuerblock 2 gemäß Fig. 7 kann auf externe Zusatzventile verzichtet werden, da das im Hammerrücklauf strömende Hydraulikfluid unmittelbar dem Tank und nicht mittelbar über die den Steuerschiebern 19 nachgeschaltete gemeinsame Rücklaufleitung des Hauptsteuerblocks 2 zugeführt wird. Das Hammerventil 12 weist eine Hauptstufe und eine Pilotstufe 12.1 auf, wobei aus Kosten- und Standardisierungsgründen der Ventileinsatz dieser Hauptstufe dem Ventileinsatz der Sperrventile 16 identisch ist. Die Druckabgriffsblende 12.2 ermöglicht einen systeminternen Steuerdruckabgriff für die Pilotstufe 12.1, der zur Steuerdruckentlastung bzw. zur Steuerdruckbeaufschlagung, respektive zum Öffnen bzw. Schließen, der Hauptstufe verwendet wird.With the arrangement of a controllable hammer valve 12 in the main control block 2 of FIG. 7 can be dispensed with external auxiliary valves, since the hydraulic fluid flowing in the hammer return directly to the tank and not indirectly via the control slide 19 downstream common return line of the main control block 2 is supplied. The hammer valve 12 has a main stage and a pilot stage 12.1, wherein for cost and standardization reasons, the valve core of this main stage is the valve insert of the check valves 16 identical. The Druckabgriffsblende 12.2 allows an intrinsic control pressure tap for the pilot stage 12.1, which is used for control pressure relief or for Steuerdruckbeaufschlagung, respectively for opening or closing, the main stage.

Der Weg des Erfindungsgedankens wird auch dann nicht verlassen, wenn andere als die bei den Sperrventilen 16 eingesetzten Ventileinsätze zur Anwendung kommen.The way of the inventive concept is not left even if other than the valve inserts used in the check valves 16 are used.

Die Betätigung der Steuerschieber 19 aller Sektionen 3 sowie der Steuerschieber 19 der Optionsblöcke 11 erfolgen vorzugsweise durch eine elektro-hydraulische Vorsteuerung, wobei auch eine herkömmliche hydraulische Vorsteuerung möglich ist.The actuation of the spool 19 of all sections 3 and the spool 19 of the option blocks 11 are preferably carried out by an electro-hydraulic pilot control, whereby a conventional hydraulic pilot control is possible.

Mit dem erfindungsgemäßen Hydrauliksystem 1 kann nunmehr eine bedarfsgerechte und flexible Versorgung aller hydraulischen Verbraucher mit dem Hydraulikfluid realisiert werden, wobei zusätzlich durch die Anordnung der Pumpenkanäle P1 17.3 und P2 17.4 und des mit ihnen verbundenen zweiten Brückenkanals 6.2, durch Verwendung eines Summierventils 15, eines Überströmventils 13 und eines steuerbaren Hammerventils 12 eine energetisch vorteilhafte Betriebsführung ermöglicht wird.With the hydraulic system 1 according to the invention, a need-based and flexible supply of all hydraulic consumers to the hydraulic fluid can now be realized are, in addition by the arrangement of the pump channels P1 17.3 and P2 17.4 and connected to them second bridge channel 6.2, by using a summing valve 15, a spill valve 13 and a controllable hammer valve 12, an energetically advantageous operation management is possible.

LISTE DER BEZUGSZEICHENLIST OF REFERENCE SIGNS

11
hydraulisches Steuersystemhydraulic control system
22
HauptsteuerblockMain control block
33
Sektionensections
3.13.1
Pumpenseite des SteuerschiebersPump side of the spool valve
3.23.2
Verbraucherseite des SteuerschiebersConsumer side of the spool
44
Hydrauliktankhydraulic tank
55
Pumpenpump
5.15.1
erste Pumpefirst pump
5.25.2
zweite Pumpesecond pump
66
Ringbrückering bridge
6.16.1
erster Brückenkanalfirst bridge canal
6.26.2
zweiter Brückenkanalsecond bridge channel
77
DrosselrückschlagventilSpeed Controller
88th
Blindstopfenblind plug
99
Druckwaagepressure compensator
1010
SekundärdruckbegrenzungsventileSecondary pressure relief valves
1111
Optionsblockoption block
1212
Hammerventilhammer valve
12.112.1
DruckabgriffsblendeDruckabgriffsblende
12.212.2
Pilotstufe des HammerventilsPilot stage of the hammer valve
1313
Überströmventiloverflow
13.113.1
Druckbegrenzungsventil als PilotstufePressure relief valve as a pilot stage
1414
Abschlusselementtermination element
1515
Summierventilsumming
1616
Sperrventilecheck valves
1717
Pumpenkanälepump channels
17.117.1
Pumpenkanal P01Pump channel P01
17.217.2
Pumpenkanal P02Pump channel P02
17.317.3
Pumpenkanal P1Pump channel P1
17.417.4
Pumpenkanal P2Pump channel P2
1818
hydraulischer Verbraucherhydraulic consumer
1919
Steuerschieberspool
2020
Pumpenleitungenpump lines
20.120.1
erste Pumpenleitung PL1first pump line PL1
20.220.2
zweite Pumpenleitung PL3second pump line PL3
2121
verbraucherseitige A-B-Steuerkantenconsumer A-B control edges
2222
Rückschlagventilcheck valve
2323
LastdruckentlastungLoad pressure relief
2424
LasthalteventilLoad-holding valve
2525
Spiegelachsemirror axis
2626
WechselventilketteShuttle valve chain
2727
Stromreglercurrent regulator

Claims (11)

  1. A hydraulic control system (1) for building machines, in particular for controlling hydraulic consumers (18) of an excavator, at least having a main control unit (2) forming a plurality of sections (3) with control spools (19) arranged therein, a hydraulic tank (4) and two pump passages P01 (17.1) and P02 (17.2) which are adapted to be acted upon with pressure by means of a first pump (5.1) and a second pump (5.2) for the serial supply of the hydraulic consumers (18) with hydraulic fluid by way of the control spools (19),
    characterised in that
    there are provided two further pump passages P1 (17.3) and P2 (17.4) which do not pass through the control spools (19), which extend parallel to the pump passages P01 (17.1) and P02 (17.2) and which are so designed in order additionally to ensure a parallel supply for the hydraulic consumers (18) by means of the control spools (19).
  2. A hydraulic control system (1) for building machines according to claim 1 characterised in that the pump passages P01 (17.1) and P1 (17.3) are adapted to be acted upon with pressure by the first pump (5.1) and the pump passages P02 (17.2) and P2 (17.4) are adapted to be acted upon with pressure by the second pump (5.2).
  3. A hydraulic control system (1) for building machines according to claim 1 or claim 2 characterised in that each section (3) has a first bridge passage (6.1) and a second bridge passage (6.2), wherein the first bridge passage (6.1) connects the pump passages P01 (17.1) and P02 (17.2) to the respective control spool (19) and the second bridge passage (6.2) connects the additional pump passages P1 (17.3) and P2 (17.4) to the respective control spool (19).
  4. A hydraulic control system (1) for building machines according to claim 3 characterised in that the first bridge passage (6.1) and the second bridge passage (6.2) are hydraulically coupled together and form a ring bridge (6).
  5. A hydraulic control system (1) for building machines according to one of claims 1 to 4 characterised in that the main control unit (2) is adapted to be expandable in the direction of its longitudinal extent by means of optional units (11) for functional expansion of the hydraulic control system (1), wherein said optional units (11) are adapted to be hydraulically coupled to the existing pump passages P01 (17.1) and P02 (17.2) and to the additional pump passages P1 (17.3) and P2 (17.4) and that the optional units (11) are of the same passage structure as the main control unit (2).
  6. A hydraulic control system (1) for building machines according to one of claims 1 to 5 characterised in that provided in the main control unit (2) and/or in the respective optional block (11) is an automatic overflow valve (13) which connects the pump passage P2 (17.4) to the pump passage P02 (17.2) so that the volume flow of the hydraulic fluid which is afforded by the second pump (5.2) by way of the pump passage P2 (17.4) and which is not needed by a hydraulic consumer (18) passes into the pump passage P02 (17.2).
  7. A hydraulic control system (1) for building machines according to one of claims 1 to 6 characterised in that the main control unit (2) has at at least one end a closure element (14) in which the pump passage P02 (17.2) and the pump passage P2 (17.4) are hydraulically coupled together.
  8. A hydraulic control system (1) for building machines according to claim 7 characterised in that the closure element (14) has a controllable summing valve (15) which is connected to the pump passages P1 (17.3) and P2 (17.4) and which when necessary feeds the volume flows of the hydraulic fluid flowing in the pump passages P1 (17.3) and P2 (17.4) to a single hydraulic consumer (18).
  9. A hydraulic control system (1) for building machines according to one of claims 1 to 8 characterised in that the main control unit (2) has a controllable hammer valve (12) with a main stage and a pilot stage (12.2) as well as a control pressure tapping aperture (12.1), wherein control pressure tapping internal to the system is possible for the pilot stage (12.2) by means of the control pressure tapping aperture (12.1), wherein the main stage is opened or closed by means of the control pressure.
  10. A hydraulic control system (1) for building machines according to one of claims 1 to 9 characterised in that the section (3) in the region of the second bridge passage (6.2) has a throttle check valve (7) and a blind plug (8), wherein the throttle check valve (7) supplies the control spool (19) with hydraulic fluid by means of the volume flow provided by the pump passage P1 (17.3) and the blind plug (8) hydraulically closes a communication between the pump passage P2 (17.4) and the control spool (19).
  11. A hydraulic control system (1) according to one of claims 1 to 10 characterised in that the optional block (11) has a controllable pressure governor (9) which connects the pump passage P2 (17.4) and the second bridge (5.2) together, wherein the pressure governor (9) supplies an additional hydraulic consumer (18) with a desired pressure and a desired volume flow of the hydraulic fluid independently of load pressure.
EP04762373A 2003-08-08 2004-07-13 Hydraulic control system for building machinery, particularly excavators Expired - Lifetime EP1651870B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10336334A DE10336334B3 (en) 2003-08-08 2003-08-08 Hydraulic control system for construction machinery, in particular for excavators
PCT/DE2004/001513 WO2005015030A1 (en) 2003-08-08 2004-07-13 Hydraulic control system for building machinery, particularly excavators

Publications (2)

Publication Number Publication Date
EP1651870A1 EP1651870A1 (en) 2006-05-03
EP1651870B1 true EP1651870B1 (en) 2007-05-02

Family

ID=34129509

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04762373A Expired - Lifetime EP1651870B1 (en) 2003-08-08 2004-07-13 Hydraulic control system for building machinery, particularly excavators

Country Status (7)

Country Link
US (1) US7475502B2 (en)
EP (1) EP1651870B1 (en)
JP (1) JP4691492B2 (en)
AT (1) ATE361430T1 (en)
DE (2) DE10336334B3 (en)
ES (1) ES2282884T3 (en)
WO (1) WO2005015030A1 (en)

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CN102878137B (en) * 2012-09-28 2015-04-15 江苏南华地下空间研究所有限公司 Valve block assembly of hydraulic system of comprehensive experiment platform
CN102966630A (en) * 2012-11-16 2013-03-13 无锡汇虹机械制造有限公司 Detection method for constant-flow oil return channel
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Publication number Publication date
US20070056437A1 (en) 2007-03-15
JP4691492B2 (en) 2011-06-01
ES2282884T3 (en) 2007-10-16
DE10336334B3 (en) 2005-08-04
EP1651870A1 (en) 2006-05-03
DE502004003704D1 (en) 2007-06-14
WO2005015030A1 (en) 2005-02-17
US7475502B2 (en) 2009-01-13
JP2007501914A (en) 2007-02-01
ATE361430T1 (en) 2007-05-15

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