EP3312436B1 - Anti-rohrbruch apparatus - Google Patents

Anti-rohrbruch apparatus Download PDF

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Publication number
EP3312436B1
EP3312436B1 EP17197491.8A EP17197491A EP3312436B1 EP 3312436 B1 EP3312436 B1 EP 3312436B1 EP 17197491 A EP17197491 A EP 17197491A EP 3312436 B1 EP3312436 B1 EP 3312436B1
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EP
European Patent Office
Prior art keywords
line
valve
pressure
hydraulic
tube
Prior art date
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Application number
EP17197491.8A
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English (en)
French (fr)
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EP3312436A1 (de
Inventor
Christian Storci
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Atlantic Fluid Tech SRL
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Atlantic Fluid Tech SRL
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Publication date
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Publication of EP3312436A1 publication Critical patent/EP3312436A1/de
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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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/005—Leakage; Spillage; Hose burst
    • 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
    • F15B13/023—Excess flow valves, e.g. for locking cylinders in case of hose burst
    • 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
    • F15B13/0422—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with manually-operated pilot valves, e.g. joysticks
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • 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

Definitions

  • the invention relates to a tube rupture protection device, in particular a hydraulic protection device that ensures safe conditions in the case of rupture of a (flexible) tube connected to a hydraulic actuator.
  • the invention can be applied to the control system of a working machine (for example an excavating and/or load handling machine), in which the drive can be provided by a linear (cylindrical) hydraulic actuator, to ensure the safe descent control in the event of rupture of the flexible tube connected to the bottom of the linear actuator.
  • a working machine for example an excavating and/or load handling machine
  • the drive can be provided by a linear (cylindrical) hydraulic actuator, to ensure the safe descent control in the event of rupture of the flexible tube connected to the bottom of the linear actuator.
  • the prior art comprises various types of tube rupture valves that protect against the rupture of the flexible tube that in an excavator, connects the bottom of the hydraulic cylinder to the distributor.
  • the tube rupture valves are installed directly on the cylinder without the interposition of the flexible tube.
  • Standard ISO 8643 requires, in the event of rupture of the flexible tube during lowering of the lifting arm, the arm not to be able to exceed twice the speed at the moment of rupture, with the control lever (joystick) maintained in the same position.
  • the prior art tube rupture valves are piloted by a first pressure on the stem side of the hydraulic cylinder and by a second pressure on the bottom side.
  • the tube rupture protection device in question does not belong to these types of valves, which are particularly complex.
  • the tube rupture protection device in question belongs to a second type of tube rupture valve - simpler than the preceding types - which normally stay closed and are piloted in opening by a pilot pressure taken from the same pilot line that pilots the distributor of the operating fluid of the cylinder, at the command of the same control lever (joystick) that is manoeuvred by the operator and also pilots the shuttle of the distributor.
  • the tube rupture valves In the event of rupture of the tube, the tube rupture valves have to be configured in such a manner as to generate an appropriate pressure drop.
  • the tube rupture valves of known type can generate pressure drops that are relatively high, with a consequent risk of slowing the machine also during normal operation, together with a possible increase in energy consumption and/or operating temperature.
  • the prior art rupture valves normally require a specific setting for each machine and/or for each modification of the configuration of the machine. Consider, for example, adding a device (for example a lifting fork) that modifies the features of the machine during the descent of the arm, so that the valve might not ensure the requested requirements.
  • JP 4 890147 B2 shows a tube rupture protection device as in the preamble of claim 1.
  • One object of the invention is to make a tube rupture protection device that is able to overcome the aforesaid limits and drawbacks of the prior art.
  • One object of the invention is to provide a tube rupture protection device for the safe descent control in the event of rupture of the flexible tube.
  • One advantage is to ensure that, in the case of a tube rupture, the descent speed of the working arm of a machine (excavator) does not exceed a set value (for example twice the speed preceding the rupture).
  • One advantage is to provide a tube rupture protection device that, during normal operations, generates a relatively reduced pressure drop.
  • One advantage is to make available a tube rupture protection device with great versatility, that is for example able to adapt to different types of machine and/or to various configurations of a machine, without the need to carry out a specific setting as the machine and/or the configuration thereof changes.
  • One advantage is to give rise to a tube rupture protection device that is constructionally simple and cheap.
  • One advantage is excellent controllability of the movable arm of a working machine ensuring great stability during movement of the arm.
  • One advantage is to ensure good manoeuvrability and optimum comfort for the operator during the various material handling operations.
  • One advantage is to reduce energy consumption, obtaining high energy efficiency during the step of controlling the movable arm.
  • One advantage is to provide a device with a mechanical seal with virtually no leaking in the joining zone between the movable element (piston) and the seat thereof, which is able to offset the leak that is normally present in the distributor (typically consisting of a shuttle distributor).
  • a hydraulic tube rupture protection device which is in particular suitable for controlling (limiting) the descent speed in the case of rupture of a tube connected to a hydraulic actuator of a movable arm of a working machine, comprises a control valve (of the pressure and/or of the flow) arranged on a hydraulic line connected to the tube; the control valve is controlled by a pilot line connected to a control member (joystick) that is manoeuvrable by an operator and also controls the valve (distributor) that adjusts the flow of operating fluid with respect to the hydraulic actuator;
  • the tube rupture protection device comprises at least one hydraulic element (for example a logic element, a pressure limiting valve, a check valve, etc) arranged on a connection line that connects the pilot line to the hydraulic line connected to the tube, whereby, in the event of rupture of the tube and even without moving the control member, the hydraulic element will open at least partially the connection line, causing the at least partial closure of the control valve, thus limiting the descent speed of the movable arm.
  • a tube rupture protection device has been indicated that is suitable for use, in particular, on a working machine (for example an excavating and/or load handling machine).
  • the tube rupture protection device 1 is used, in particular, to limit the descent speed of a movable arm in the event of rupture of the (flexible) tube that, normally, connects the directional control valve (distributor) to the hydraulic actuator that controls movement of the arm of the working machine.
  • the tube rupture protection device 1 may comprise, in particular, a valve unit made as a single block (schematized with a dashed line in Figures 1-6 and 9 ).
  • the tube rupture protection device 1 comprises a hydraulic line 2 in turn comprising a first port P1 intended for the connection with a (linear) hydraulic actuator C and a second port P2 intended for the connection with a (flexible) tube T at risk of rupture.
  • the tube T may be, in turn, connected to a directional control valve D of the operating fluid of the actuator C.
  • the directional control valve D may be, in particular, of proportional type.
  • the tube rupture protection device 1 comprises at least one control valve V operating in the hydraulic line 2.
  • the control valve V may comprise, in particular, a control valve (of the pressure and/or of the flow) of known type that can normally be used in a tube rupture protection device.
  • the control valve V may comprise, for example, a control valve (of the pressure and/or of the flow) with a control of proportional type.
  • the control valve V may comprise, in particular, a valve of mechanical seal type, i.e. a valve configured for ensuring a mechanical seal with virtually no leaking, for example by using specific mechanical components (that are in themselves known), such as a movable element (piston) and a seat for the movable element with no leaking.
  • a valve of mechanical seal type i.e. a valve configured for ensuring a mechanical seal with virtually no leaking, for example by using specific mechanical components (that are in themselves known), such as a movable element (piston) and a seat for the movable element with no leaking.
  • the control valve V comprises at least one first (ascent) position in which it permits a flow towards the first port P1 and prevents a flow towards the second port P2.
  • the control valve V comprises at least one second (descent) position in which it permits a flow to the second port P2, for example with a localized load loss (of a preset amount).
  • control valve V may comprise other types of valve (also of known type).
  • the tube rupture protection device 1 comprises a pilot line 3 arranged for piloting the control valve V to the aforesaid first position.
  • the pilot line 3 comprises a third port P3 intended for the connection with a control device J manoeuvrable by an operator.
  • the control device J (for example a joystick of known type) may be configured, as in these embodiments, so as to control simultaneously both the directional control valve D and the control valve V.
  • the tube rupture protection device 1 comprises a connection line 4 arranged for connecting the pilot line 3 to a portion of the hydraulic line 2 comprised between the second port P2 and the control valve V.
  • the tube rupture protection device 1 comprises at least one circuit element 5, or hydraulic element, arranged in the connection line 4.
  • the circuit element 5 is configured so as to be closed in the normal operating steps and to be opened automatically (at least partially) in the case of a tube rupture (because of a pressure drop that will occur in the aforesaid portion of the hydraulic line 2 comprised between the second port P2 and the control valve V).
  • This circuit element 5 may be, in particular, sensitive to a pressure present in the aforesaid portion of the hydraulic line 2 such as to close the connection line 4 when in the aforesaid portion of the hydraulic line 2 there is a first pressure in the case of an intact tube T, i.e. in a normal operating situation.
  • This circuit element 5 is sensitive to a pressure present in the aforesaid portion of the hydraulic line 2 so as to open (at least partially) the connection line 4 when in the aforesaid portion of the hydraulic line 2 there is a second pressure lower than the aforesaid first pressure.
  • the second pressure may be due, in particular, to rupture of the tube T, i.e. in an emergency situation that requires an automatic and immediate intervention to maintain the system in a safe condition, even if the operator does not promptly return the control device J to the safety position.
  • This circuit element 5 may comprise, for example, at least one of the circuit elements illustrated in Figure 7 and indicated from A to F.
  • Figures 7A to 7F with I the side of the circuit element 5 to the control device J has been indicated, with II the side towards the tube T, with III the side (if present) towards the drain R.
  • the circuit element 5 may comprise, as in the embodiments in Figure 1 and Figure 6 , a pressure control valve, for example the valve in Figure 7A .
  • the circuit element 5 may comprise, in other embodiments which are not illustrated, a pressure control valve as in Figure 7B or as in Figure 7D .
  • the circuit element 5 could comprise, in particular, a proportional control valve, as in the embodiments in Figures 7A and 7D .
  • the circuit element 5 could comprise other embodiments of maximum pressure valves (of known type).
  • the circuit element 5 may comprise, in other embodiments which are not illustrated, the check valve in Figure 7C arranged so as to permit a flow from the pilot line 3 to the hydraulic line 2 (connected to the flexible tube T).
  • the circuit element 5 may comprise, as in the embodiments in Figures 2 , 3 , 4 and 5 , a logic element, for example like that of Figure 7E or 7F , which can be arranged in such a manner as to be piloted in closure by the pressure in the aforesaid portion of the hydraulic line 2.
  • the logic element may be piloted in closure by elastic means.
  • the logic element may be piloted in opening by the pressure coming from the control device J (with the possible interposition of first choking means C1 and/or second choking means C2).
  • the logic element may be configured, in particular as in Figure 7E , in such a manner as to have a differential area dimensioned for maintaining the element in balance when the pressure on the side of the hydraulic line 2 (tube side) is (significantly) lower than the pressure on the opposite side (joystick side), for example with a ratio greater than 1:3, or 1:4, or 1:5, and less than 1:12, or 1:10, or 1:8 (for example 1:6, in particular 1 bar on one side and 6 bar on the opposite side).
  • the logic element may be configured, in particular as in Figure 7F , in such a manner as to have a differential area dimensioned for maintaining the element in balance when the pressure on the side of the hydraulic line 2 (tube side) is (significantly) greater than the pressure on the opposite side (joystick side), for example with a ratio greater than 3:1, or 4:1, or 5:1, and less than 12:1, or 10:1, or 8:1 (for example 6:1, in particular 6 bar on one side and 1 bar on the opposite side).
  • the circuit element 5 facilitates closing of the control valve V during the emergency due to the rupture of the tube T, causing a desired reduction in descent speed, in a controlled manner, further limiting dispersal of the operating fluid that exits through the rupture of the tube T. It is possible, in particular, to reach complete closure of the control valve V, gradually, i.e. without the risk of generating instability in the movement of the movable arm controlled by the hydraulic actuator C.
  • connection line 4 and of the circuit element 5 sensitive to the pressure enables the valve V to generate a relatively low load loss during normal operation, to then generate automatically (gradually) a greater load loss immediately after the rupture of the tube, so that the valve V is able to close, also only partially, because of the rupture of the tube, without the need to intervene on the control device J.
  • the protection device 1 comprises, as in the embodiments in Figures 3 , 4 , 5 and 9 , a locking valve 7 arranged for blocking a signal (for example present on the connection line 4 and coming from the hydraulic line 2) directed to the control valve V.
  • the locking valve 7 may be piloted, in particular, by a pressure coming from the pilot line 3.
  • the locking valve 7 is positioned on the connection line 4.
  • the locking valve 7 may be positioned between the control device J and the circuit element 5.
  • the locking valve 7 may be positioned between the circuit element 5 and the hydraulic line 2.
  • the locking valve 7 comprises a valve with at least two positions, in the specific embodiments of Figure 3 , 5 and 9 with three positions, with at least one central open position and at least two lateral, or external, or end closing positions, opposite one another with respect to the central open position.
  • a first lateral closing position could be piloted, for example, by elastic means.
  • a second first lateral closing position could be piloted, for example, by a pressure taken by a pilot line 9 and coming from the pilot line 3.
  • the locking valve 7 could comprise a two position valve with an open position (piloted by a pressure taken by a pilot line 9) and a closed position (piloted by elastic means).
  • the locking valve 7 may be configured, in particular, so as to remain closed (for example in the first lateral closing position) for a pressure lower than a first value (where the first value may be, in particular, the same as the opening operating pressure of the circuit element 5, for example equal to 5 bar).
  • the locking valve 7 may be configured, in particular, in such a manner as to be open (for example in the first central open position) when the pressure is comprised between the aforesaid first value and a second value (where the second value may be, in particular, the pressure beyond which it is no longer necessary to activate the tube rupture protection device 1, for example a 12 bar value).
  • the locking valve 7 may be configured, in particular, in such a manner as to be closed (for example in the second first lateral closing position) for a pressure greater than the aforesaid second value, i.e. when the tube rupture protection device 1 can be deactivated.
  • the locking valve 7 comprises a two position valve ( Figure 4 ) with an open position and a closed position it is possible for the locking valve 7 to be configured, in particular, so as to remain closed for a pressure lower than the first value and in such a manner as to be open when the pressure is greater than the first value.
  • Figure 8 shows (partially) a tube rupture protection device 1, the hydraulic diagram of which corresponds to that of Figure 5 , in which the (three-position) locking valve 7 is integrated into a movable element (piston) of the valve V.
  • the tube rupture protection device 1 may comprise, in particular, first choking means C1 (for example at least one adjustable grubscrew) arranged in the pilot line 3.
  • the first choking means C1 may be arranged, in particular, between the third port P3 and the connection line 4.
  • the first choking means C1 may comprise, in particular, a calibrated orifice with a determined diameter.
  • the tube rupture protection device 1 may comprise, in particular, second choking means C2 (for example at least one adjustable grubscrew) arranged in the connection line 4.
  • the second choking means C2 may be arranged, in particular, between the circuit element 5 and the pilot line 3.
  • the second choking means C2 may comprise, in particular, a calibrated orifice with a determined diameter.
  • the first choking means C1 and the second choking means C2 may be calibrated in such a manner as to obtain a desired limitation of the descent speed of the movable arm connected to the hydraulic actuator C in the case of a tube rupture.
  • the first choking means C1 and the second choking means C2 may comprise two calibrated orifices with the same diameter (for example 1 mm).
  • the first choking means C1 will have a passage section that is greater than the second choking means C2.
  • the first choking means C1 will have a passage section that is less than the second choking means C2.
  • the tube rupture protection device 1 may comprise, in particular, an auxiliary drainage line 8 arranged for draining the above circuit element 5.
  • the tube rupture protection device 1 may comprise, in particular, a fourth port P4 connected to the aforesaid auxiliary drainage line 8.
  • the fourth port P4 may be intended, as in this embodiment, for connection with a drain R.
  • the control circuit of the hydraulic actuator C may comprise, in particular, the aforesaid directional control valve D arranged for distributing in a controlled manner the operating fluid of the actuator C.
  • the control circuit may comprise, in particular, the flexible tube T at risk of rupture arranged for connecting the directional control valve D with the hydraulic actuator C.
  • the control circuit may comprise, in particular, the tube rupture protection device 1 arranged between the flexible tube T and the hydraulic actuator C.
  • the control circuit may comprise, in particular, the control device J manoeuvrable by an operator.
  • the control device J may be configured and arranged so as to control simultaneously both the directional control valve D and the control valve V.
  • the cursor S may comprise, in particular, the piloting piston of the valve V.
  • the piloting pressure is present, whereas on the left there is the main movable shutter means of the valve V (for example of known type).
  • the cursor S is a movable element that gives rise, in cooperation with one or more recesses on the valve body B, to the (three-position) locking valve 7. With S1, S2, S3 and S4 some significant strokes have been indicated that the cursor S can execute with reference to the position of the connection recess 11.
  • the stroke S1 comprises, substantially, a dead stroke that is used to eliminate possible clearance of at least one movable element (piston unit) of the valve V that operates on the cursor S.
  • the locking valve 7 may be closed.
  • the recess 11 may still be in a covering position with respect to the hole communicating with the connection line 4.
  • the control valve V may be in a pre-opening step whilst the locking valve 7 may still be closed.
  • drainage (of some drops of the) operating fluid may occur so as to generate depressurization in the actuator C.
  • draining may be achieved, in particular, from the control valve V, of (some drops of the) operating fluid that is suitable for generating depressurization in the actuator C.
  • the piloting pressure may act, in particular, both on the control valve V and on the directional control valve D, causing a first flow indication thereof, but with a movement of the actuator C that can still be imperceptible.
  • an opening pressure of the control valve V that may be, for example, about 5 bar; in this step also the locking valve 7 may start to open, so the connection recess 11 no longer has a cover of the hole that communicates with the connection line 4 and the fluid can start to transit.
  • the control valve V may have a pre-opening, whereas the locking valve 7 may remain closed and in the opening stroke S3 both the valves V and 7 may have a true opening.
  • end stroke S4 a (possible) end stroke has been indicated in which the locking valve 7 is reclosed again.
  • the end stroke S4 may be provided, depending on the needs and the requests of the user of the tube rupture protection device, in particular if it is desirable to limit the descent speed whatever the speed or only for a given descent speed range.
  • the tube rupture protection device 1 may comprise, as in the embodiments in Figures 5 , 6 and 9 , anti-collision means that may comprise, in particular, a maximum pressure valve 13 arranged on a drainage line 14 that connects the actuator C with the piloting of the valve V.
  • the drainage line 14 may be connected, for example, to the pilot line 3, in particular by a selector valve 6 that selects, between the two aforesaid lines, the line with greater pressure, automatically excluding the other.
  • the drainage line 14 may be connected to the drain R, for example by a drainage line 15 that branches off from the drainage line 14 to reach the drainage line 8.
  • third choking means C3 (a calibrated orifice).
  • the fluid discharged from the maximum pressure valve 13, through the third choking means C3, may generate, in particular, an increase in pressure that spreads in the pilot line 3 and thus on the piloting piston, thus opening the control valve V and releasing the fluid from the actuator C to reduce the pressure thereof.
  • the anti-collision means may be arranged, in particular, to protect the hydraulic system from pressure peaks or overloads.
  • FIG 9 another embodiment of the tube rupture protection device is shown that comprises the hydraulic line 2, the first port P1, the second port P2, the control valve V, the pilot line 3, the third port P3, the connection line 4, the circuit element 5, the (three-position) locking valve 7, the first choking means C1, the second choking means C2, the auxiliary drainage line 8 (arranged in particular for draining the control valve V), the fourth port P4 to be connected to a drain, the anti-collision means comprising the maximum pressure valve 13, the drainage line 14, the selector valve 6, the drainage line 15, the third choking means C3.
  • the (three-position) locking valve 7 is integrated into the movable element of the control valve V.
  • the second choking means C2 may be, in particular (as in this embodiment), integrated into the movable element of the control valve V.
  • the second choking means C2 may be arranged, according to other embodiments which are not illustrated, between the locking valve 7 (in this case with three positions) and the circuit element 5.
  • the second choking means C2 may be arranged, according to other embodiments which are not illustrated, between the circuit element 5 and the hydraulic line 2.
  • the auxiliary drainage line 8 may be, in particular (as in this embodiment), arranged for draining the control valve V.
  • the tube rupture protection device may comprise, in particular (as in this embodiment in Figure 9 ), a bypass valve 16 arranged on a bypass line 17 to bypass the control valve V along the hydraulic line 2 in a direction of the flow that goes from the second port P2 to the first port P1.
  • the bypass system (valve 16 and line 17) is used, in particular, in the ascent step to bypass the descent control valve V that does not work during the ascent.
  • the tube rupture protection device may comprise, in particular (as in this embodiment of Figure 9 ), an equalizing line 18 that connects the first port P1 to an equalizing port E.
  • the equalizing system (line 18 and port E) is used, in particular, if the working machine comprises two or more parallel cylinders (excavator type) and is thus provided with two or more tube rupture protection devices, one for each cylinder. In this situation, it is possible to connect together the equalization ports of the various safety devices (for example by a tube), in order to balance the pressures inside the various cylinders, so that such pressures are similar, to prevent one cylinder bearing the load and another cylinder not bearing the load.
  • the circuit element 5, or hydraulic element will open at least partially the connection line 4, causing the at least partial closure of the control valve V, limiting the descent speed of the actuator C.

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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)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)

Claims (14)

  1. Vorrichtung (1) zur hydraulischen Schlauchbruchsicherung, welche aufweist:
    - eine Hydraulikleitung (2), die einen ersten Anschluss (P1), der mit einem hydraulischen Stellglied (C) verbunden werden kann, und einen zweiten Anschluss (P2) aufweist, der mit einem bruchgefährdeten Schlauch (T) verbunden werden kann;
    - mindestens ein Steuerventil (V), das in der Hydraulikleitung (2) arbeitet, wobei das Steuerventil (V) mindestens eine erste Stellung, in der es einen Durchfluss zu dem ersten Anschluss (P1) ermöglicht und einen Durchfluss zu dem zweiten Anschluss (P2) verhindert, und mindestens eine zweite Stellung aufweist, in der es eine Strömung in Richtung auf den zweiten Anschluss (P2) ermöglicht;
    - eine Steuerleitung (3), die ausgestaltet ist, um das Steuerventil (V) in Richtung auf die erste Stellung zu steuern, wobei die Steuerleitung (3) einen dritten Anschluss (P3) aufweist, der mit einer Steuervorrichtung (J) verbunden werden kann, die von einem Bediener bedient werden kann;
    - eine Verbindungsleitung (4), die ausgestaltet ist, um die Steuerleitung (3) mit einem Abschnitt der Hydraulikleitung (2) zwischen dem zweiten Anschluss (P2) und dem mindestens einen Steuerventil (V) zu verbinden;
    - mindestens ein Schaltungselement (5), das in der Verbindungsleitung (4) angeordnet ist und das auf einen in dem Abschnitt der Hydraulikleitung (2) vorhandenen Druck reagieren kann, um die Verbindungsleitung (4) zu schließen, wenn in dem Abschnitt der Hydraulikleitung (2) bei einem intakten Schlauch (T) ein erster Druck herrscht, und um die Verbindungsleitung (4) zumindest teilweise zu öffnen, wenn in dem Abschnitt der Hydraulikleitung (2) ein zweiter Druck herrscht, der niedriger als der erste Druck bei einem Schlauchbruch (T) ist;
    - mindestens ein an der Verbindungsleitung (4) angeordnetes Sperrventil (7);
    dadurch gekennzeichnet, dass das mindestens eine Sperrventil (7) ein Ventil mit mindestens zwei Stellungen aufweist, das in ein bewegliches Element des Steuerventils (V) eingebaut ist.
  2. Vorrichtung nach Anspruch 1, bei der das mindestens eine Sperrventil (7) durch einen Druck gesteuert wird, der von der Steuerleitung (3) kommt.
  3. Vorrichtung nach Anspruch 2, wobei das mindestens eine Sperrventil (7) so ausgestaltet ist, dass es eine geschlossene Stellung für einen Druck unter einem ersten Wert und eine offene Stellung für einen Druck über dem ersten Wert einnimmt.
  4. Vorrichtung nach einem der vorhergehenden Ansprüche, welche ein erstes Drosselmittel (C1) aufweist, das in der Steuerleitung (3) zwischen dem Anschluss (P3) und der Verbindungsleitung (4) angeordnet ist.
  5. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei das mindestens eine Sperrventil (7) ein Zweistellungsventil aufweist, wobei mindestens eine geschlossene Stellung durch ein elastisches Mittel gesteuert wird und mindestens eine offene Stellung durch einen von der Steuerleitung (3) kommenden Druck gesteuert wird.
  6. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei das mindestens eine Sperrventil (7) ein Dreistellungsventil mit mindestens einer ersten geschlossenen Stellung für einen Druck kleiner als ein erster Wert, mit mindestens einer offenen Stellung für einen Druck zwischen den einen ersten Wert und einen zweiten Wert, der größer als der erste Wert ist, und mit mindestens einer zweiten geschlossenen Stellung für einen Druck, der größer als der zweite Wert ist, aufweist.
  7. Vorrichtung nach Anspruch 6, wobei die mindestens eine offene Stellung eine mittlere Stellung ist, wobei die mindestens eine erste geschlossene Stellung eine äußere Stellung ist, die durch ein elastisches Mittel gesteuert wird, wobei die mindestens eine zweite geschlossene Stellung eine äußere Stellung ist, die durch einen von der Steuerleitung (3) kommenden Druck gesteuert wird.
  8. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei das mindestens eine Schaltungselement (5) ein Druckregelventil, zum Beispiel ein Maximaldruckventil, und/oder ein Flussregelventil, zum Beispiel ein Rückschlagventil, aufweist.
  9. Vorrichtung nach einem der vorhergehenden Ansprüche, wobei das mindestens eine Schaltungselement (5) ein Logikelement aufweist.
  10. Vorrichtung nach Anspruch 9, wobei das Logikelement durch einen Druck in dem Abschnitt der Hydraulikleitung (2) und/oder durch ein elastisches Mittel zum Schließen gesteuert wird und/oder wobei das Logikelement mittels einer Hilfsabflussleitung (8) entleert wird, die mit einem Abfluss (R) verbunden werden kann.
  11. Vorrichtung nach einem der vorhergehenden Ansprüche, welche eine Hilfsabflussleitung (8), die so ausgestaltet ist, dass sie das Schaltungselement (5) ablässt, und einen vierten Anschluss (P4) aufweist, der mit der Hilfsabflussleitung (8) verbunden ist und mit einem Abfluss (R) verbunden werden kann.
  12. Vorrichtung nach einem der vorhergehenden Ansprüche, welche ein zweites Drosselmittel (C2) aufweist, das in der Verbindungsleitung (4) zwischen dem Schaltungselement (5) und der Steuerleitung (3) angeordnet ist.
  13. Hydraulischer Steuerkreis für ein hydraulisches Stellglied (C), wobei der hydraulische Steuerkreis ein Wegeventil (D) für eine Betriebsflüssigkeit des Stellglieds, einen bruchgefährdeten Schlauch (T) zum Verbinden des Wegeventils (D) an den hydraulischen Stellglieds (C), eine zwischen dem Schlauch (T) und dem hydraulischen Stellglied (C) anordenbare Schlauchbruchsicherung und eine von einer Bedienperson betätigbare Steuereinrichtung (J) aufweist, die gleichzeitig das Wegeventil (D) und das Steuerventil (V) steuert; wobei die Vorrichtung (1) zur Schlauchbruchsicherung nach einem der vorhergehenden Ansprüche hergestellt worden ist.
  14. Verwendung eines hydraulischen Steuerkreises zur sicheren Absenksteuerung bei einem Schlauchbruch eines Arms einer Arbeitsmaschine, insbesondere einer Bagger- und/oder Lastaufnahmemaschine, wobei der hydraulische Steuerkreis nach Anspruch 13 ausgebildet worden ist.
EP17197491.8A 2016-10-21 2017-10-20 Anti-rohrbruch apparatus Active EP3312436B1 (de)

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IT201800007591A1 (it) * 2018-07-27 2020-01-27 Atlantic Fluid Tech Srl Dispositivo per Controllare un Attuatore
CN108980208B (zh) * 2018-10-09 2020-01-17 杭州励贝电液科技有限公司 一种超高精度压力控制装置
CN109296527B (zh) * 2018-12-01 2020-03-17 潍坊亚油机械有限公司 一种往复泵用控制阀
IT201900016823A1 (it) 2019-09-20 2021-03-20 Atlantic Fluid Tech S R L Dispositivo di Controllo di un Attuatore Idraulico
CN111623001B (zh) * 2020-06-23 2024-08-30 柳工常州机械有限公司 整机液压系统的安全启动和应急控制装置以及方法

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JP3915622B2 (ja) * 2002-07-30 2007-05-16 コベルコ建機株式会社 油圧アクチュエータ回路の負荷保持装置
JP4890147B2 (ja) * 2006-08-04 2012-03-07 日立建機株式会社 油圧アクチュエータ回路の負荷保持装置
JP2014206245A (ja) * 2013-04-15 2014-10-30 コベルコ建機株式会社 油圧アクチュエータ回路の負荷保持装置
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