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EP3058236B1 - Dispositif de commande - Google Patents

Dispositif de commande Download PDF

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Publication number
EP3058236B1
EP3058236B1 EP14780756.4A EP14780756A EP3058236B1 EP 3058236 B1 EP3058236 B1 EP 3058236B1 EP 14780756 A EP14780756 A EP 14780756A EP 3058236 B1 EP3058236 B1 EP 3058236B1
Authority
EP
European Patent Office
Prior art keywords
control
valve
pressure
function block
block
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.)
Active
Application number
EP14780756.4A
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German (de)
English (en)
Other versions
EP3058236A1 (fr
Inventor
Sascha Alexander Biwersi
Marcus Hettiger
Marcus Simon Specks
Christoph Stönner
Marcus Karl Pfeiffer
Erik LAUTER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydac Filtertechnik GmbH
Original Assignee
Hydac Filtertechnik GmbH
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Filing date
Publication date
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Publication of EP3058236A1 publication Critical patent/EP3058236A1/fr
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Publication of EP3058236B1 publication Critical patent/EP3058236B1/fr
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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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0427—Heating
    • 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
    • F15B13/026—Pressure compensating 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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated 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
    • 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
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/008—Valve failure
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/003—Systems with different interchangeable components, e.g. using preassembled kits
    • 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
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds
    • 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
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control 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
    • F15B2211/60—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
    • 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
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit 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
    • F15B2211/60—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing 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
    • F15B2211/67—Methods for controlling pilot 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8636—Circuit failure, e.g. valve or hose failure
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust

Definitions

  • the invention relates to a device with a control device in the manner of a valve block, in particular for the hydraulic control of components of mobile work machines.
  • a control device for hydraulic motors is known, with at least one directional spool valve, which can be connected via an inlet line to a pump as a pressure supply device, via an outlet line to a tank or return connection and via at least one working line to one of the hydraulic motors, with an inlet regulator arranged in the inlet line , with a load pressure control point in the directional spool that can be connected to the work line via a load pressure sensing point that can be activated in a direction-dependent manner, and with at least one relief line leading from the control line via the directional spool to the drain line, in which at least one safety valve is arranged that, when a predetermined load pressure is reached - Or movement limit can be switched to a passage position, the relief line in the directional spool can be switched to passage depending on the direction and synchronously with the respectively activated load pressure sensing point.
  • the safety valve in one is arranged between the passage in the directional spool and the discharge line lying section of the relief line, the section of the relief line containing the safety valve remains depressurized until the safety valve is used for monitoring the direction of movement of the hydraulic motor assigned to it. This ensures with the known solution that different safety valves can be defined independently for each direction of movement.
  • the WO 02 / 090778A2 describes a control device in the manner of a valve block, consisting of at least one pressure supply and a tank or return connection as well as two useful connections and control and / or regulating valves connected between the individual connections as well as with two control lines, which at least one of the control and / or Can control valves.
  • the WO 2004/099657 A1 discloses another control device. Proceeding from this prior art, the object of the invention is to further improve the known control device while maintaining the advantages described above in such a way that its range of functions is increased in order to be able to achieve increased functional reliability in this way. A relevant object is achieved by a device having the features of claim 1 in its entirety.
  • control lines is connected to a function block with a modular structure, depending on the design of the function block, further control and regulating tasks can be solved and the functional reliability of the overall control device can be increased. It is surprising for an average specialist in the field of hydraulic control devices that, given a suitable design of the module-like function block, he can conceptually revise existing control devices in the form of a large number of further designs, and in this way can also regularly increase the functional reliability.
  • the function block used in each case for example as a pressure relief valve and to control it with the control pressure of a load sensing line LP, whereas in another further preferred configuration the function block has an electromagnetically switchable directional valve which on its input side has the pressure from another load sensing - Line LS receives.
  • Further function blocks that can be used advantageously are in Fig. 1a shown.
  • connection points, lines or valves are specified in the hydraulic circuit diagrams, these are no longer explained in detail, but are the subject of the usual nomenclature in this area.
  • the representation after the Fig. 1 relates to a control device, in particular for the electro-hydraulic control of components of mobile machines, which are not shown here, however.
  • the control device shown has a pressure supply connection P and a tank or return connection T and also has two useful connections A, B to which a hydraulic consumer, for example in the form of a working cylinder (not shown in more detail) or in the form of a hydraulic motor, can be connected.
  • two control lines C and Z are shown, as well as load sensing lines LS, LX and LP along with the associated load sensing connections.
  • a so-called individual pressure compensator 10 is used as control and regulating valves of the control device, which is connected upstream of the control slide 12 of a directional control valve 14, which can be designed, for example, as a proportional pressure regulating valve. Furthermore, two changeover or priority valves 16 are used, as well as two electro-proportional pressure control valves 18, which on the output side control the control slide 12 of the directional control valve 14 in its displacement position on opposite sides in each case.
  • the control device is designed in the manner of a valve block 20 and has, at least on one of its sides, a flange pattern 22 for connecting various module-like function blocks 24, 26.
  • the load signal in combination with the individual pressure compensator 10 connected upstream of the control slide 12 has a decisive influence on their functional properties in the case of quantity-controlled mobile valves. If, for example, the load signal is limited to a set value with the aid of a pressure relief valve, when this value is reached, the individual pressure compensator 10 ensures that the amount of consumer continuously decreases due to its closing movement. If the load signal is not limited to a set pressure, but is completely relieved in the direction of the tank connection T, the individual pressure compensator 10 remains in its closed position. When the control slide 12 is deflected, no quantity can then flow via the individual pressure compensator 10 and thus via the slide 12 in the direction of the consumers connected to the consumer connections A, B.
  • the function is therefore blocked by the pressure supply device P, for example in the form of a hydraulic pump in the direction of the consumer, connected to the useful connections A, B.
  • the manipulation of the load signal can be of great importance in the context of mechanical safety considerations.
  • the individual overpressure limitation of the load signal for the consumer or utility connections A and B, which is integrated in the individual slide sections, is standard from today's perspective.
  • electrically operated shut-off valves are also state of the art and, for example, in DE 42 30 183 C2 shown.
  • the known pressure limiting and switch-off functions for the load signal only consider the section-relevant load pressures A and B of the working or useful connections in this section.
  • the signal from the previous sections at this section and the signal reported to the next section (upstream and downstream of the section change valve) is routed to the outside according to the solution according to the invention and can be manipulated there.
  • Fig. 1 shown external LP load sensing connection and associated line, it is possible to limit all previous sections with only one pressure relief valve (mechanical, electrically connectable or electro-proportional) 28 instead of up to two per section. It is a prerequisite that all consumer connections of the previous sections are limited to the same lower system pressure. Furthermore, it is possible to switch off all previous sections with only one 2/2-way valve 30.
  • the same manipulative range of functions as in the context of the load sensing line LP can be implemented via the load sensing line LS in addition to the associated LS connection, except that the load signal of the section located at this connection is also taken into account.
  • the load sensing lines LP and / or LS can be part of a flange diagram 22 of the valve block 20 for the control device or can be implemented in the context of conventional threaded connections.
  • the function block 24 the pressure relief valve 28 to be connected and the other function block 26 the directional control valve 30.
  • the connection lines LS, Z and LP shown for the function blocks 24, 26 are in fluid connection with the corresponding connections LS, Z and LP in the flange diagram 22 for a functionally reliable use To connect.
  • the control line Z is optional and, as in the illustration according to FIG Fig.
  • FIG. 1 shown, be designed as an internal leakage oil line Z or open into the tank line T.
  • the connections LA, LB and LR ( Fig. 1b ) are also brought out.
  • a correspondingly modified drawing is in the Fig. 1b shown, the otherwise the embodiment of the Fig. 1 corresponds, the function blocks 24, 26 not being shown further here for the sake of simplicity.
  • FIG. 1a shows, other function blocks (framed in dashed lines) with their valve installation components, as they correspond to the usual hydraulic circuit diagrams, can be connected to overall control devices, as exemplified in the Fig. 1 and 1b are shown, as set out above, in order to achieve modified functions for the control device and to increase the modularity of the overall concept accordingly.
  • individual modules are shown as functional components and on the opposite right side combinations of these modules consisting of several valve function elements in a function block to be connected. Additional logics with or without other modules can also be implemented for the load sensing lines LA, LB and LR (cf. Fig. 1b ).
  • both the pressure reducing valve 32 can fail and also the individual electro-proportional control valves 18 for the individual control spool sides. If, for example, the pressure reducing valve 32 is stuck, the high pressure side is connected to the low pressure side. The potential risk is very high. If, on the other hand, a control valve 18 is stuck in the control position, then a pilot slide side would be permanently subjected to a pilot pressure. The result would be an uncontrollable machine function. In this case, if you are unable to interrupt the low-pressure supply, emergency operation using the hand lever is also no longer ensured.
  • Today's primary measures in the prior art include certain design principles for the individual components.
  • protective screens or filter devices 34 are shown, arranged in the fluid guide direction upstream of the pressure reducing valve 32 and optionally upstream of the control valves 18 also to the other primary protective mechanisms. Additional pressure relief valves (not shown) can be used as secondary measures.
  • valve block 20 In order to create a cost-effective alternative to the respective pressure relief valve as a secondary measure, a further function block 36 was designed for the design of the control device shown as valve block 20 created.
  • a fundamental disadvantage of pressure relief valves is that the function is not necessarily recognizable to the machine operator. That is, in order to really be able to detect the response of the pressure limiting valve and thus the faulty function of the pressure reducing valve, a pressure switch or pressure sensor would also be required in addition to a pressure limiting valve. This causes not inconsiderable additional costs.
  • a safety device against overpressure is used within the function block 36, which in the present exemplary embodiment according to FIG Fig. 2 is designed as a rupture disc 38 of conventional design. If the permissible pressure upstream of the control valves 18 is exceeded, the rupture disk 38 is destroyed and the pressure upstream of the control valves 18, in particular via the control line C, is completely reduced using an inlet nozzle 40 in front of the pressure reducing valve 32. A control of the valve spool 12 of the directional control valve 14 and thus an actuation of the consumers via the control valves 18 is then no longer possible. The machine connected to the control device can then still be operated via a conventional hand lever actuation (not shown) and possibly brought out of a danger area.
  • the rupture disk 38 can be integrated in the context of a functional block 36 both in the flange or connection plate 22 and also directly in an end plate of the valve block 20 of the control device.
  • connection or flange plate 22 of the valve block 20 defines a predefinable flange pattern C ', C and Z, on which the pressure between the pressure reducing valve 32 and the two pressure control valves 18 can be tapped. Furthermore, there is a hydraulic connection C ′, C, at which the pressure, viewed in the direction of fluid flow, is present behind the pressure reducing valve 32.
  • a manually operable shut-off unit 54 can be connected via the flange pattern 22 in the context of a connectable function block 46.
  • a further possibility is to connect an electrically actuable 2/2-way valve 56 with a relief nozzle 58 and optional pressure monitoring 60 on the secondary side in the function block 48.
  • a further comparable possibility exists through the use of an electrically actuable 3/2-way valve 62, which in turn can optionally be monitored for the switching position and also has an optional pressure monitor 60 on the secondary side.
  • the relevant unit can be connected to the flange pattern 22 via the function block 50, as already shown.
  • function block 64 to monitor the pressure immediately after the pressure reducing valve 32. Furthermore, it remains to be stated that there is basically the possibility of using all of the above-mentioned functional blocks with their exchangeable contents together in a control device or to make a combinatorial selection with regard to the respective security functionality presented.
  • Fig. 4a , 4b in turn relate to a hydraulic LS control block in the manner of a control device with which individual hydraulic consumers can be controlled via integrated valve arrangements 10, 14, 16 and 18 as a control and regulating valve assembly, which in turn can be connected to the useful connections A and B.
  • the hydraulic energy is in turn made available via a pressure supply device P, for which purpose both variable and constant pumps can be used.
  • control device can cool down to ambient temperature, while the pressure medium in the overall hydraulic circuit can have a significantly higher temperature due to the actuation of delimited subsystems. If a control slide 12 of one of the directional control valves 14 is now actuated, the warm oil flows into the control slide 12. Since the control slide 12 and the valve housing surrounding it can expand differently due to the material, shape and flow around them under the influence of temperature, the respective control or valve slide 12 may jam in the associated housing of the directional control valve 14, particularly in winter.
  • variable pump maintains a previously defined and set differential pressure, for example 25 bar, in neutral circulation, i.e. when no hydraulic consumers are actuated.
  • control block connection in the form of the pressure supply connection P, which is dependent on the volume flow and corresponds to the differential pressure of the neutral circulation circuit (usually> 5 bar). That is, in both cases, a low pressure can be used to allow a defined volume flow to flow through the control or valve block 20 with the aid of a simple orifice 66 for the purpose of tempering.
  • both connections P and T are in a valve module in the form of the valve block 20, this is achieved through an additional channel 68.
  • This channel 68 is not earmarked and can basically be used for various tasks in the entire modular valve system. In the present case, it guides the volume flow from the connection plate or flange plate 22 through all sections into the end plate, where the volume flow mentioned specifically ends in the T-channel.
  • the T-channels have the basic advantage of being very large in terms of cross-section, so that they can also give off a lot of heat due to the large area they create.
  • a volume flow defined via the orifice 66 and the open closing element 70 of a so-called cartridge valve 72 is now fed into the additional channel 68, passed through all sections into the end plate and there specifically into the T channels and thus back to the connection plate 22 and to the tank or return port T.
  • the relevant transition point 74 is in the direction of viewing Fig. 4 seen on the right.
  • the load reporting line LS chain
  • the logic arrangement consisting of the diaphragm 66 and the closing element 70 of the valve 72 can, due to the additional channel 68, both in the connection or flange plate 22 ( Fig. 4a ) as well as in the end plate ( Fig. 5 ) are arranged in the valve block 20.
  • the additional channel 68 is used for the volume flow guidance to the end plate in the form of the valve block 20; in the second case, the highest load signal of the LS chain is sent back to the end plate on the locking element via this channel 68 70 of the valve 72 reported.
  • this arrangement in the end plate has the advantage that both the large T channels and the large pressure supply channel P can be used for the temperature control function, the T and P connections then both in the connection or flange plate 22 are arranged. In the case of a P-channel switch-off, a priority switch or a switch, this arrangement would no longer work.
  • the orifice 66 and the closing element 70 of the valve 72 in turn form a common unit in the form of a function block 76 which can be connected in a modular manner.
  • the relevant function block 76 can in turn be integrated directly in the control or valve block 20, as well as according to the illustration in FIG Fig. 4a can be adapted to the control or valve block 20 with the aid of a suitable flange pattern via the connection or flange plate 22.
  • the function block 76 can also be located together with the pressure reducing valve 32 together with the filter device 34 on the opposite side, that is to say in the direction of view of the Fig. 4b seen on the right, can be connected to the valve block 20 by means of a suitable flange or connection plate 22.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (4)

  1. Dispositif constitué d'un dispositif de commande à la manière d'un bloc (20) de vanne, notamment pour la commande hydraulique d'éléments de machines fournissant du travail, et d'un bloc (24, 26) de fonction, le dispositif de commande étant constitué d'au moins un raccord (P) d'alimentation en pression et d'un raccord (T) de réservoir ou de retour, ainsi que de deux raccords (A, B) utiles et de vannes (10, 14, 16, 18) de commande et/ou de réglage montées entre les divers raccords (P, T, A, B), ainsi que de deux lignes (C, Z) de commande, qui peuvent commander au moins l'une des vannes de commande et/ou de réglage, le bloc (24, 26) de fonction constitué modulairement étant raccordé à au moins l'une des lignes (C, Z) de commande, et dans lequel
    - le bloc respectif de fonction est raccordé, en tant que pièce modulaire normalisée, à une plaque (22) de bride normée du bloc (20) de vanne et a, suivant l'utilisation, des éléments de vanne de conformation différente,
    - des lignes (LS, LP et Z) de raccordement du bloc respectif de fonction sont en communication fluidique avec des raccords (LS, LP et Z) correspondants de la plaque (22) de bride,
    - deux des lignes (LS, LP) de raccord sont des lignes Loadsensing, dont l'une est raccordée à l'élément de vanne respectif et l'autre est fermée ou est raccordée à un autre élément de vanne du bloc de fonction, et
    - l'autre ligne (Z) de raccordement du bloc de fonction est raccordée à l'une des deux lignes (Z) de commande du bloc (20) de vanne, qui sert de ligne d'huile de fuite.
  2. Dispositif suivant la revendication 1, caractérisé en ce que les éléments de vanne sont constitués sous la forme d'une vanne (28) de limitation de la pression ou d'une vanne à plusieurs voies commutables, de préférence électromagnétiquement, de préférence une vanne (30) à 2/2 voies, ou un diaphragme.
  3. Dispositif suivant la revendication 1 ou 2, caractérisé en ce que l'une des vannes de commande et/ou de réglage est une balance manométrique, notamment une balance (10) manométrique individuelle.
  4. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que l'une des vannes de commande et/ou de réglage est une vanne (14) à tiroir à plusieurs voies, à laquelle sont raccordés, du côté de la sortie, fluidiquement les raccords (A, B) utiles.
EP14780756.4A 2013-10-15 2014-09-24 Dispositif de commande Active EP3058236B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310017093 DE102013017093A1 (de) 2013-10-15 2013-10-15 Steuervorrichtung
PCT/EP2014/002583 WO2015055276A1 (fr) 2013-10-15 2014-09-24 Dispositif de commande

Publications (2)

Publication Number Publication Date
EP3058236A1 EP3058236A1 (fr) 2016-08-24
EP3058236B1 true EP3058236B1 (fr) 2020-06-03

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EP14780756.4A Active EP3058236B1 (fr) 2013-10-15 2014-09-24 Dispositif de commande

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US (1) US10119558B2 (fr)
EP (1) EP3058236B1 (fr)
CN (1) CN205663670U (fr)
DE (1) DE102013017093A1 (fr)
WO (1) WO2015055276A1 (fr)

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EP3225583B1 (fr) * 2016-03-31 2019-02-13 Cargotec Research & Development Ireland Limited Soupape hydraulique en sections et chariot élévateur à fourche monté sur camion incorporant une telle soupape
ITUA20162611A1 (it) 2016-04-14 2017-10-14 Cnh Ind Italia Spa Circuito idraulico di controllo e potenza e veicolo da costruzione comprendente tale circuito
CN108374808A (zh) * 2018-04-11 2018-08-07 安徽省万豪水坝节能技术有限公司 一种闸门油电控制器及控制系统
US10858806B2 (en) * 2019-03-12 2020-12-08 Caterpillar Inc. Modular manifold having at least two control modules for controlling operation of at least two hydraulic actuators of an earthmoving machine
CN113931892B (zh) * 2021-09-28 2022-06-14 中联重科股份有限公司 负载口独立控制的负载敏感多路阀及液压系统
DE102022002192A1 (de) 2022-06-17 2023-12-28 Hydac Fluidtechnik Gmbh Volumenstromversorgung

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DE9111569U1 (de) 1991-09-17 1991-11-14 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Steuervorrichtung für wenigstens einen Hydromotor
DE19647994A1 (de) * 1996-11-20 1998-05-28 Rexroth Mannesmann Gmbh Lastfühlende hydraulische Steuerung zur Betätigung eines hydraulischen Verbrauchers mit unterschiedlichen Geschwindigkeiten
DE19948232A1 (de) * 1999-07-10 2001-01-11 Mannesmann Rexroth Ag Wegeventilscheibe, insbesondere für ein mobiles Arbeitsgerät
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DE10121924A1 (de) * 2001-05-05 2002-11-07 Bosch Rexroth Ag Hydraulische Steueranordnung zur Steuerung eines einfachwirkenden hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit und Wegeventil dafür
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Also Published As

Publication number Publication date
US10119558B2 (en) 2018-11-06
EP3058236A1 (fr) 2016-08-24
CN205663670U (zh) 2016-10-26
US20160258450A1 (en) 2016-09-08
WO2015055276A1 (fr) 2015-04-23
DE102013017093A1 (de) 2015-04-16

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