EP1651870B1 - Systeme de commande hydraulique pour engins de construction, en particulier pour excavateurs - Google Patents

Systeme de commande hydraulique pour engins de construction, en particulier pour excavateurs 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)
English (en)
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EP1651870A1 (fr
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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    • 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.

Landscapes

  • 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)

Claims (11)

  1. Système de commande hydraulique (1) pour des engins de construction, en particulier pour commander les appareils consommateurs hydrauliques (18) d'un excavateur, comprenant au moins un bloc de commande principal (2) qui forme plusieurs sections (3) avec des tiroirs de commande (19) agencés dans ledit bloc, un réservoir hydraulique (4) et deux canaux de pompe P01 (17.1) et P02 (17.2) réalisés pour être alimentés en pression au moyen d'une première pompe (5.1) et d'une seconde pompe (5.2), pour l'alimentation en série des appareils consommateurs hydrauliques (18) avec un fluide hydraulique via les tiroirs de commande (19),
    caractérisé en ce que
    il est prévu deux autres canaux de pompe P1 (17.3) et P2 (17.4), qui ne traversent pas les tiroirs de commande (19), qui s'étendent parallèlement aux canaux de pompe P01 (17.1) et P02 (17.2), et qui sont conçus de manière à assurer en supplément une alimentation parallèle des appareils consommateurs hydrauliques (18) au moyen des tiroirs de commande (19).
  2. Système de commande hydraulique (1) pour des engins de construction selon la revendication 1,
    caractérisé en ce que les canaux de pompe P01 (17.1) et P1 (17.3) sont réalisés de manière à pouvoir être alimentés en pression par la première pompe (5.1), et les canaux de pompe P02 (17.2) et P2 (17.4) sont réalisés de manière à pouvoir être alimentés en pression par la seconde pompe (5.2).
  3. Système de commande hydraulique (1) pour des engins de construction selon la revendication 1 ou 2,
    caractérisé en ce que chaque section (3) comprend un premier canal de pontage (6.1) et un second canal de pontage (6. 2), dans lequel le premier canal de pontage (6. 1) relie les canaux de pompe P01 (17.1) et P02 (17.2) au tiroir de commande respectif (19), et le second canal de pontage (6. 2) relie les canaux de pompe additionnels P1 (17.3) et P2 (17.4) au tiroir de commande respectif (19).
  4. Système de commande hydraulique (1) pour des engins de construction selon la revendication 3,
    caractérisé en ce que le premier canal de pontage (6.1) et le second canal de pontage (6.2) sont couplés l'un à l'autre sur le plan hydraulique et forment un pontage annulaire.
  5. Système de commande hydraulique (1) pour des engins de construction selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que le bloc de commande principal (2) est réalisé de façon à pouvoir être complété, en direction de son extension longitudinale, au moyen de blocs à option (11), lesdits blocs à option (11) étant réalisés couplés hydrauliquement avec les canaux de pompe existants P01 (17.1) et P02 (17.2) ainsi qu'avec les canaux de pompe additionnels P1 (13.3) et P2 (17.4), et en ce que les blocs à option (11) présentent la même structure de canaux que le bloc de commande principal (2).
  6. Système de commande hydraulique (1) pour des engins de construction selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce que, dans le bloc de commande principal (2) et/ou dans le bloc à option respectif (11), et prévue une valve de déversement automatique (13) qui relie le canal de pompe P2 (17.4) au canal de pompe P02 (17.2), de sorte que l'écoulement volumétrique fourni par la seconde pompe (5.2) via le canal de pompe P2 (17.4), du fluide hydraulique qui n'est pas nécessité par un appareil consommateur hydraulique (18), parvient dans le canal de pompe P02 (17.2).
  7. Système de commande hydraulique (1) pour des engins de construction selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que le bloc de commande principal (2) comprend sur au moins un côté frontal un élément de terminaison (14) dans lequel le canal de pompe P02 (17.2) et le canal de pompe P2 (17.4) sont couplés hydrauliquement l'un à l'autre.
  8. Système de commande hydraulique (1) pour des engins de construction selon la revendication 7,
    caractérisé en ce que l'élément de terminaison (14) comprend une valve de sommation (15) susceptible d'être commandée, laquelle est reliée aux canaux de pompe P1 (17.3) et P2 (17.4), et amènent en cas de besoin les courants volumétriques du fluide hydraulique s'écoulant dans les canaux de pompe P1 (17.3) et P2 (17.4) à un appareil consommateur hydraulique (18) unique.
  9. Système de commande hydraulique (1) pour des engins de construction selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que le bloc de commande principal (2) comprend une soupape marteau (12) commandée avec un étage principal et un étage pilote (12. 2) ainsi qu'un diaphragme de prélèvement de pression de commande (12.1), le diaphragme de prélèvement de pression de commande (12. 1) permettant à l'intérieur du système un prélèvement de la pression de commande pour l'étage pilote (12.2), l'étage principal étant ouvert ou fermé au moyen de la pression de commande.
  10. Système de commande hydraulique (1) pour des engins de construction selon l'une quelconque des revendications 1 à 9,
    caractérisé en ce que la section (3) comprend, dans la région du second canal de pontage (6.2), un clapet antiretour à étranglement (7) et un bouchon borgne (8), le clapet antiretour à étranglement (7) alimentant le tiroir de commande (19) avec du fluide hydraulique au moyen du courant volumétrique fourni par le canal de pompe P1 (17.3), et le bouchon borgne (8) obturant une liaison entre le canal de pompe P2 (17.4) et le tiroir de commande (19).
  11. Système de commande hydraulique (1) selon l'une quelconque des revendications 1 à 10,
    caractérisé en ce que le bloc à option (11) comprend une balance de pression (9) susceptible d'être commandée, qui relie l'un à l'autre le canal de pompe P2 (17.4) et le second canal de pontage (5.2), ladite balance de pression (9) alimentant un appareil consommateur hydraulique (18) additionnel avec une pression désirée et un courant volumétrique désiré du fluide hydraulique, de façon indépendante vis-à-vis de la pression de charge.
EP04762373A 2003-08-08 2004-07-13 Systeme de commande hydraulique pour engins de construction, en particulier pour excavateurs Expired - Lifetime EP1651870B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10336334A DE10336334B3 (de) 2003-08-08 2003-08-08 Hydraulisches Steuersystem für Baumaschinenen, insbesondere für Bagger
PCT/DE2004/001513 WO2005015030A1 (fr) 2003-08-08 2004-07-13 Systeme de commande hydraulique pour engins de construction, en particulier pour excavateurs

Publications (2)

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

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EP04762373A Expired - Lifetime EP1651870B1 (fr) 2003-08-08 2004-07-13 Systeme de commande hydraulique pour engins de construction, en particulier pour excavateurs

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

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EP2433650A3 (fr) * 2006-06-06 2012-12-19 Tolerrx Inc. Administration d'anticorps anti-CD3 dans le traitement de maladies auto-immunes
CN102062127B (zh) * 2011-02-02 2012-11-28 卢宇 一种比例控制多路阀
US8966890B2 (en) 2011-07-29 2015-03-03 Caterpillar Inc. Method and arrangement for active make-up in an overrunning actuator
JP6200634B2 (ja) * 2012-06-28 2017-09-20 ナブテスコ株式会社 油圧制御弁
CN102878137B (zh) * 2012-09-28 2015-04-15 江苏南华地下空间研究所有限公司 综合实验平台液压系统的阀块总成
CN102966630A (zh) * 2012-11-16 2013-03-13 无锡汇虹机械制造有限公司 一种恒流量回油通道检测方法
DE102014005410A1 (de) 2014-03-01 2015-09-03 Hydac Filtertechnik Gmbh Ventilvorrichtung
JP6522320B2 (ja) * 2014-11-11 2019-05-29 ナブテスコ株式会社 方向切換弁
JP6552829B2 (ja) * 2015-01-28 2019-07-31 ナブテスコ株式会社 方向切換弁
JP6773421B2 (ja) * 2016-02-08 2020-10-21 ナブテスコ株式会社 方向切換弁及び油圧システム
JP6717541B2 (ja) 2016-07-28 2020-07-01 キャタピラー エス エー アール エル 弁装置およびこれを備えた流体圧システム
CN106382266B (zh) * 2016-12-05 2018-06-08 中国第一汽车股份有限公司 一种多功能专用车液压系统
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Also Published As

Publication number Publication date
US20070056437A1 (en) 2007-03-15
JP4691492B2 (ja) 2011-06-01
ES2282884T3 (es) 2007-10-16
DE10336334B3 (de) 2005-08-04
EP1651870A1 (fr) 2006-05-03
DE502004003704D1 (de) 2007-06-14
WO2005015030A1 (fr) 2005-02-17
US7475502B2 (en) 2009-01-13
JP2007501914A (ja) 2007-02-01
ATE361430T1 (de) 2007-05-15

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