EP0942103B1 - Ventileinrichtung für einen hydraulischen Motor zum Antreiben einer Masse grossens Trägheitsvermögens - Google Patents

Ventileinrichtung für einen hydraulischen Motor zum Antreiben einer Masse grossens Trägheitsvermögens Download PDF

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Publication number
EP0942103B1
EP0942103B1 EP99400564A EP99400564A EP0942103B1 EP 0942103 B1 EP0942103 B1 EP 0942103B1 EP 99400564 A EP99400564 A EP 99400564A EP 99400564 A EP99400564 A EP 99400564A EP 0942103 B1 EP0942103 B1 EP 0942103B1
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EP
European Patent Office
Prior art keywords
principal
conduits
fluid
communication
slide element
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
EP99400564A
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English (en)
French (fr)
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EP0942103A1 (de
Inventor
Alain Mangano
Jean-Pierre Lebrun
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Poclain Hydraulics Industrie
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Poclain Hydraulics Industrie
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Filing date
Publication date
Priority claimed from FR9802967A external-priority patent/FR2776032B1/fr
Priority claimed from FR9809354A external-priority patent/FR2781532B1/fr
Application filed by Poclain Hydraulics Industrie filed Critical Poclain Hydraulics Industrie
Publication of EP0942103A1 publication Critical patent/EP0942103A1/de
Application granted granted Critical
Publication of EP0942103B1 publication Critical patent/EP0942103B1/de
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Classifications

    • 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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
    • 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
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/123—Drives or control devices specially adapted therefor
    • 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
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/128—Braking systems
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • 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
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • 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
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow 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
    • F15B2211/505—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
    • F15B2211/50527—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 using cross-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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/5154—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an 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
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control
    • 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
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F15B2211/715—Output members, e.g. hydraulic motors or cylinders or control therefor having braking means
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2617—Bypass or relief valve biased open
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7793—With opening bias [e.g., pressure regulator]

Definitions

  • the present invention relates to a valve device for less a hydraulic motor capable of driving a mass of inertia important, the engine having two main lines, respectively fluid supply and exhaust, which are likely to be closed for stopping the engine.
  • driven mass the mass that the motor serves to train will be called "driven mass”.
  • the motor to which this valve device applies is used for example to ensure the rotation of a turret of a machine such as a hydraulic shovel, or to ensure the translation of tracked or tire-bearing vehicles having a mass important.
  • It can be a hydraulic motor of the so-called “fast motor” type. (1000 to 2000 rpm) driving a reducer or a motor called “motor slow "(whose speed of rotation is for example of the order of 100 rpm, for example of the radial piston type.
  • a circulation of fluid is maintained in the engine and one of the main lines is pressurized to play the role of supply line, while the other of these lines is in relative vacuum and is connected to a fluid outlet for play the role of exhaust pipe.
  • the engine is stopped by performing a deceleration phase, then closing the supply lines and exhaust.
  • the pressure in the supply line becomes low pressure while pressure in the exhaust pipe becomes high pressure.
  • the fluid located in the pipe exhaust is at a higher pressure than the fluid located in the supply line.
  • the hydraulic fluid is slightly compressible.
  • the mass of inertia continues its movement until the pressure in the exhaust pipe reaches a maximum value corresponding to the compression of the fluid present in this conduct.
  • the mass return movement will have increases the pressure in the supply line to bring the fluid present in this line to a pressure of compression substantially equal to the maximum pressure prevailing in the exhaust pipe just before this phase of return.
  • the driven mass is driven by an oscillating movement whose frequency, for turrets of machines such as shovels hydraulic, is of the order of 1 Hz.
  • this oscillating movement has a small relative amplitude and that it is finally naturally braked from the makes friction phenomena, it is obviously extremely annoying, especially when it comes to placing the mass driven by the engine in a very precise position by stopping the engine without braking mechanical.
  • Another system is to allow permanent leaks between the engine supply and exhaust lines.
  • the invention aims to remedy the aforementioned drawbacks by proposing a simple and reliable device, which makes it possible to brake and cancel very system oscillations quickly after the engine has been isolated, whatever the mass training conditions, in particular that they are driven on a slope or slope, or on level ground.
  • the device comprises two main conduits respectively intended to be connected to the two main lines of the engine, which it includes means for said main conduits in communication situation when the fluid pressures in these conduits are substantially equal and for put said main conduits in a situation of isolation in which these conduits are isolated from each other when the pressures of fluid in these conduits are different and that it further comprises delay means capable of limiting the speed of passage between the communication situation and isolation situation.
  • the fluid pressure in the exhaust pipe is higher than the fluid pressure in the supply line. Therefore, during the deceleration phase and until the engine stops, the ducts of the valve device according to the invention remain in the situation isolation. Due to its high inertia, the driven mass continues its initial movement until the pressure in the line of delivery reaches a maximum value (compression). From this situation, the entrained mass initiates a movement back during from which the difference between the pressures in the pipes exhaust and supply decreases until it becomes appreciably nothing. At this time, the two main conduits of the device are put in communication situation, situation in which the volume of fluid in excess in the engine exhaust line may spill into the supply line.
  • the timing means we make sure that as soon as the mass has described about half of the return movement oscillations it has just started, that is to say as soon as the pressures in the supply line in the exhaust line become substantially equal, the main conduits of the device according to the invention are placed in a communication situation and tend to stay in this communication situation long enough to allow at least a large part of the volume of fluid in excess in the exhaust pipe to spill into the pipe Power.
  • the mass linked to the engine is braked as soon as it has describes half of a return movement and hardly moves not beyond.
  • the timing means of the invention limit the speed of passage between the situation of communication and the situation of isolation, that is, they make sure that once the situation of communication is obtained, this situation persists for at least one some time (on the order of a few tenths of a second to a second), necessary for the transfer of excess fluid in the pipe exhaust to the supply line.
  • the means of delay serve to hinder the passage from the situation of communication to the situation of isolation.
  • the means to put the main conduits in a situation of communication include means forming a calibrated restriction, the cross section of the fluid likely to flow through this restriction when the main conduits are in a situation of communication being much lower than the current section of the conduits main (1% to 5% of this current section).
  • This calibrated restriction is particularly useful when starting the engine from a situation where the pressures in the supply and exhaust lines are equal. Indeed, to start the engine, feed the supply line in fluid and, for the engine to work, this fluid must pass through the pistons cylinders before being evacuated by the pipe exhaust. In other words, you have to make sure that a loss of load is quickly installed between the supply lines and exhaust. Thanks to the presence of the calibrated restriction, the fluid supplying the first main conduit of the device will preferably go in the main engine supply line, only a small amount of fluid which can then "short-circuit" the engine and be evacuated by the second main conduit of the device via the restriction calibrated. Thus, a significant pressure difference will settle quickly between the supply and exhaust lines, this pressure difference obviously having the effect of putting the conduits of the device in isolation, so that the engine works normally.
  • the device comprises a movable member likely to be requested between three positions under the effect of the difference between the fluid pressures prevailing in the two main conduits, these three positions comprising a first and a second position extremes in which the two main conduits are in situation isolation from each other and an intermediate position in which said main conduits are in communication situation with each other, the movable member being placed in its first position extreme when the pressure in the first main duct is higher than the pressure in the second main duct while it is placed in its second extreme position when the pressure in the second main duct is higher than the pressure in the first main duct and placed in its intermediate position when the pressures in the two main conduits are substantially equal.
  • This movable member is preferably formed by a mounted drawer sliding in a bore, a portion of which extends between the two main ducts, this drawer being equipped with means forming a duct of communication which connects the main conduits in the position drawer and which is closed by the bore wall in the two extreme drawer positions.
  • the device comprises means for provide a first and a second control chamber, respectively located at a first and a second end of the drawer, the first chamber communicating with the first duct main through a first communication pass, while the second bedroom communicates with the second main duct by a second communication passage, the first control being capable of being supplied with fluid to repel the drawer to its first extreme position when the fluid pressure in the first main conduit becomes greater than the fluid pressure in the second main duct and empty to allow the moving the drawer to its second extreme position when the fluid pressure in the second main conduit becomes greater than the fluid pressure in the first main conduit, and the second control chamber being capable of being supplied with fluid for push the drawer back to its second extreme position when the pressure of fluid in the second main duct becomes greater than the fluid pressure in the first main duct and to empty for allow the drawer to move to its first extreme position when the fluid pressure in the first main duct becomes higher than the fluid pressure in the second main conduit.
  • the bottom of the control constitutes a movable stop for the ends corresponding to the drawer, this movable stop being recalled in permanence by return means in the direction of a reduction in the volume of control chambers.
  • the device shown in Figures 1 to 3 comprises a body 10 in which two main conduits 12 and 14 are drilled, respectively intended to be connected to the supply lines and hydraulic motor exhaust.
  • a bore 16 is made in the body 10, this bore having a middle portion which extends between the two main conduits 12 and 14, on either side of which extend two extreme portions located beyond the conduits 12 and 14.
  • a drawer 18 is slidably mounted in this bore, in which it can occupy three particular positions.
  • the first, visible in Figure 1, is a first extreme position in which the fluid pressure in the first main duct 12 is greater than the pressure in the second main duct 14 and in which the drawer isolates these two main conduits.
  • the drawer 18 can also occupy a second extreme position, shown in Figure 3, which corresponds to the situation reverse in which the fluid pressure in the second conduit main is greater than the pressure in the first main duct and in which the drawer isolates these two conduits.
  • the drawer can still occupy a third position which is an intermediate position illustrated by FIG. 2, in which the pressures in the conduits 12 and 14 are substantially equal and in which these conduits are placed communication.
  • the drawer 18 includes a communication conduit which, in the example shown, has a central bore 20, which opens on the wall of the drawer by first holes 22 and second holes 24 which are spaced from each other in the sliding direction of the drawer, so that, in the first extreme position, the orifices 22 are closed by the cylindrical wall of the bore 16, while in the intermediate position, the orifices 22 and 24 open respectively in the first and second main conduits 12 and 14 and that in the second extreme position shown in FIG. 3, the orifices 24 are closed by the wall of the bore 16.
  • orifices 22 and 24 are located in grooves, 23 and 25 respectively, made on the outer periphery of the drawer, this which allows the main conduits 12 and 14 to remain in communication via conduit 20 even when the drawer 18 is slightly shifted to one of its extreme positions from the intermediate position.
  • the conduit 20 comprises a section with a small passage section forming a calibrated restriction 21. As indicated previously, this restriction is used to generate a pressure drop when starting the motor, that is to say when one of the conduits 12 and 14 is supplied with fluid with the engine supply line to which it is connected.
  • Figures 1 to 3 show an exemplary embodiment of the communication conduit which comprises the conduit 20, the orifices 22 and 24 as well as restriction 21.
  • the conduit for communication in another way, especially by providing grooves, possibly stepped to form restriction 21, on the outer periphery of the drawer.
  • the device includes means for providing a first and a second control chambers 28 and 30, respectively located at a first and at a second end, 18A and 18B, of the drawer.
  • the first bedroom 28 is supplied with fluid via the first main duct 12, with which it communicates by a first pass communication 32.
  • the second control chamber 30 communicates with the second main conduit 14 via a second communication passage 34.
  • the first control chamber is supplied with fluid to push the drawer back into its first position shown in the figure 1.
  • the fluid pressure in the second conduit main 14 is greater than the pressure in the first main duct 12, it is the second control chamber 30 which is supplied with fluid, as seen in Figure 3.
  • control chambers 28 and 30 have first and second bottom walls respectively mobile, respectively designated by the references 38 and 40. These bottom walls constitute stops with which the first and second ends of the drawer to limit movement of this last.
  • the bottom walls 38 and 40 are movable in the direction of translation of the drawer and the device comprises a first return means, comprising for example a first mechanical spring 39, capable of permanently recall the bottom wall 38 towards the end 18A of the drawer, that is to say towards a position in which it tends to decrease the volume of the first control chamber 28.
  • the device comprises a second reminder means, comprising for example a mechanical spring 41, capable of permanently recalling the second wall bottom 40 in the direction going closer to the second end 18B of the drawer.
  • bottom walls 38 and 40 constitute the faces active pistons in bores 42 and 44, respectively practiced in parts 10A and 10B which are attached to the body 10 so that the bores 42 and 44 are in the extension of the bore 16 in which the slide 18 slides.
  • the fixing parts 10A and 10B on the body 10 is sealed using seals.
  • the return means 39 and 41 can in themselves contribute to the delay since, in order to be able to move towards one from its extreme positions from its intermediate position, the drawer 18 must first push one of the bottom walls 38 and 40 against the stress exerted on this wall by the return means 39 or 41.
  • the springs 39 and 41 rather constitute simple means of recall tending to replace the bottom walls 38 and 40 in their "advanced" positions once they have been pushed back by the drawer, and the delay means in themselves are made hydraulically.
  • the device shown in Figures 1 to 3 includes a first and second damping chambers respectively designated by the references 46 and 48.
  • the first bedroom damping communicates with the first main conduit 12 by a first communication and amortization pass which, for reasons which will be detailed below, advantageously includes two branches 50 and 52.
  • the second bedroom damping communicates with the second main conduit 14 by a second communication and damping pass which comprises two branches 54 and 56.
  • branch 52 of the first communication pass and depreciation includes a calibrated restriction 53 which limits the passage of the fluid in this region.
  • branch 56 of the second communication and depreciation pass includes a calibrated restriction 57.
  • the two damping chambers 46 and 48 are filled with fluid. From this situation, to allow passage of the drawer in its first extreme position shown in Figure 1, it will not only that the fluid supplying the first conduit 12 and entering the first control chamber 28 tends to move the drawer towards the right, but also that this movement is allowed by emptying at less partial damping chamber 48. Restriction 57 allows to impede the flow of fluid through passage 56 when the room 48 is emptied.
  • restriction 57 allows “slow down” the emptying of chamber 48, which prevents the drawer from passing too quickly from its intermediate position to its first position extreme.
  • restriction 53 "slows down” the emptying of the chamber 46 when, the pressure in the main duct 14 becomes greater than the pressure in the conduit 12, the drawer tends to move from its position intermediate towards its second extreme position shown in the figure 3.
  • main conduits 12 and 14 a diameter of approximately 9 mm
  • restriction 21 a diameter of approximately 1mm
  • restrictions 53 and 57 a diameter of approximately 0.3mm
  • stiffness of the springs 39 and 40 will be of the order of 1 N / mm.
  • damping chambers 46 and 48 are able to fill with fluid as quickly as possible so that the pistons carrying the bottom walls 38 and 40 can resume very quickly their advanced positions after being pushed back by the drawer. It's here reason for the existence of branches 50 and 54 of the passages of communication and depreciation, these branches actually constituting respectively a first and a second feeding passage equipped each of a non-return valve 51, 55, so as to allow circulation fluid from a main conduit 12 or 14 considered, that in the direction of filling of the corresponding chamber 46 or 48.
  • orifices 22 and 24 of the conduit of communication in drawer 18 are arranged so that the orifices 22 communicate with the main conduit 12 when the drawer occupies its second extreme position shown in Figure 3, while that the orifices 24 communicate with the second main conduit 14 when the drawer occupies its first extreme position shown on the figure 1.
  • Restrictions 53 and 57 can be directly practiced in the pistons which carry the bottom walls 38 and 40 if the passage between the damping chambers and main ducts is done at this place.
  • FIGS. 1 to 3 we now describe a circuit hydraulics incorporating the device of FIGS. 1 to 3 shown so schematic.
  • This circuit is of the so-called "open circuit" type insofar as the hydraulic pump 100 which is used to supply the motor M is a single direction pump, the fluid exhaust being connected to a tank R at atmospheric pressure.
  • the engine M includes main lines 112 and 114 which, depending on the direction of operation conditioned by one or other of the extreme positions a distribution valve 120, used for feeding or engine exhaust.
  • the circuit comprises also a booster pump 110 and pressure limiters 102 and 103.
  • Figure 4 illustrates the engine isolation situation, in which the valve 120 occupies an intermediate position which closes the pipes 112 and 114, the fluid delivered by the pump 100 going directly to the reservoir A.
  • the booster pump 110 is used to ensure a given minimum pressure in lines 112 and 114. In a manner known per se, it is connected to these pipes by non-return valves 104 and 105, associated with pressure relief valves 106 and 107
  • the device of the invention is located in block B1 in FIG. 4.
  • FIG. 4 We recognize the standardized representation of the drawer 18 mobile between three positions.
  • Figure 4 it is shown in its position intermediate in which the lines 12 and 14 of the device respectively connected to the main pipes 112 and 114 of the motor M, are put in communication via the passage of communication including the calibrated restriction 21.
  • Displacement of the drawer is controlled by the connected control chambers respectively to conduits 12 and 14 by the communication passages 32 and 34.
  • the passage of the drawer 18 from its intermediate position to one of its extreme positions is hampered by the damping chambers respectively connected to conduits 12 and 14 by the passages of communication and depreciation each comprising their two branches 50, 52 and, respectively, 54, 56.
  • the entire block B1 can be part of a hydraulic block intended to be fixed on the motor housing hydraulic M.
  • This block B1 can, with the block B2 which includes the valves check valves 104 and 105, as well as pressure limiters 106 and 107 constitute the same fixed hydraulic block ("flanged") on the casing of the engine.
  • the engine can be a single displacement engine or multiple operating displacements, in which case the hydraulic block comprising block B1 can also include the means for selecting the engine displacement.
  • the device according to the invention associated with a single engine M. In particular for training in translation of an extremely heavy mass, one can plan to use a group of several motors arranged in series or in parallel. In this case, this device can be associated with all of the motors of this group, its first and second main conduits 12 and 14 being respectively connected to the supply and exhaust lines of the engines of the group.
  • FIGS. 5 to 7 show another embodiment of the device according to the invention.
  • the elements common to the two embodiments are assigned in FIGS. 5 to 7 with the same references as in FIGS. 1 to 3 increased by 200.
  • the main conduits 212 and 214 are formed in the body 210 of the device, the slide 218 being axially movable in a bore 216 formed in the body 210 and extending partly between the conduits 212 and 214.
  • the drawer is capable of occupying two extreme positions ( Figures 5 and 7) and one position intermediate ( Figure 6).
  • the drawer 218 sets communication conduits 212 and 214 by a communication conduit which includes a first section of blind bore 220A which opens onto the external axial periphery of the drawer by orifices 222, a first 221A calibrated restriction which communicates the blind bore portion 220A with a communication chamber 219 and a second 221B calibrated restriction similar to the first, which communicates the communication chamber 219 with a second section of bore blind 220B, which opens on the periphery of the drawer by holes 224.
  • Restrictions 221A and 221B play a role similar to that of restriction 21 of Figures 1 to 3.
  • the communication conduit is closed by the wall of the bore 216 in the two extreme positions of the drawer 218.
  • first main conduit 212 can continue to stay in communication with room 219 in the first extreme position (figure 5) of the drawer, while the second conduit 214 can continue to stay in communication with this room in the second extreme position of the drawer (Figure 7).
  • conduits 220A and 220B are blind, that is to say that they do not meet inside the drawer. However, they open respectively on the ends 218A and 218B of the drawer 218.
  • sections 220A and 220B also play the role of first and second communication passages, allowing respectively to communicate the first and second conduits main 212 and 214 with, respectively, a first chamber of control 228 and a second control chamber 230.
  • first control chamber 228 When the pressure in conduit 212 is greater than pressure in conduit 214, the first control chamber 228 is filled with fluid for push the drawer back into its first extreme position, while in the reverse situation, it is the second control chamber 230 which is filled with fluid.
  • the volume of the chambers 228 and 230 is substantially equal to the half the maximum volume of each of these chambers. Indeed, in the balanced situation in which pressures in conduits 212 and 214 are equal, pressures are equal in chambers 228, 219 and 230 which communicate with each other via the conduits 220A and 220B with restrictions 221A and 221B.
  • At least one of the first and second communication passages (formed in the example shown, by sections 220A and 220B respectively) is equipped of a calibrated restriction to impede the flow of fluid through these passages.
  • the open end of the blind section 220A is fitted with a first restriction calibrated 253, while the open end of the blind pipe section 220B is fitted with a second 257 calibrated restriction. that, from the position shown in Figure 6, the passage of the drawer in either of its two intermediate positions is not possible only if one of the chambers 228 and 230 is emptied while, concomitantly, the other of these chambers is filled with fluid.
  • restriction 253 is used to limit the cross-section of the fluid, which amounts to to hinder the filling of the chamber 228 for the passage from the position intermediate to the first extreme position of the drawer, or to hinder emptying of this chamber 228 for the passage from the intermediate position to the second extreme position of this drawer.
  • Restriction 257 has the same effect with regard to room 230. Insofar as the emptying of a room is always concomitant with the filling of the other room, only one of the two restrictions 253 and 257 could be provided.
  • Restrictions 221A and 221B allow loss of load between conduits 212 and 214 when, when restarting the engine, the pressure in the supply line increases rapidly.
  • the diameter of these restrictions could for example be of the order of 1mm at 1.5mm, while that of restrictions 253 and 257 will be more or less 0.1 to 0.3 mm for motors operating up to pressures of 300 bars.
  • the chambers 228 and 230 act both as control chambers and as chambers depreciation, due to 253 and / or 257 restriction (s).
  • the device which has just been described in relation to FIGS. 5 to 7 can be placed, in place of that of FIGS. 1 to 3, in block B1 of the circuit of Figure 4, to operate in the same manner.
  • the circuit can be opened as shown in the Figure 4 or of the "closed" type in which the pump used is a two operating directions to which the lines are connected supply and exhaust.
  • the drawer 18 or 218 In the stabilized situation at the stop of the mass driven by the motor, the drawer 18 or 218 normally occupies its intermediate position (the pressures are the same in the two main conduits 12, 14 or 112, 114). This is in fact generally the case on flat ground in which, at the stop, no particular constraint that must be exerted on the mass driven to keep it in position.
  • Main conduits 312 and 314 are connected to bore 316 formed in the body 310.
  • the drawer 318 is movable in this bore between a first extreme position ( Figure 8) in which the pressure in the conduit 312 is greater than the pressure in conduit 314 and a second extreme position (figure 10) corresponding to the situation reverse.
  • FIG. 9 shows the intermediate position of the drawer 318, in which allows the communication of conduits 312 and 314.
  • the bore is closed at both ends by plugs, respectively 319A and 319B.
  • conduits 312 and 314 are isolated by the cooperation of the wall of the middle portion bore 316 which extends between conduits 312 and 314 with, respectively, zone 318A and zone 318B of the cylindrical face drawer exterior.
  • the communication of main ducts 312 and 314 goes through a calibrated restriction 321 constituted, in the example shown in Figures 8 to 10, by a calibrated flat formed on an area 318C of the drawer which is between the zones 318A and 318B.
  • a calibrated flat formed on an area 318C of the drawer which is between the zones 318A and 318B.
  • the 321 calibrated flat determines the pressure drop between the conduits key.
  • the communication conduit is therefore defined between this flat and the wall of the middle portion of the bore 316.
  • Figure 11 shows, also in the intermediate position of the drawer, a variant of the third embodiment of the invention, which distinguishes from that presented in FIGS. 8 to 10 only by the conformation of the calibrated restriction.
  • this restriction is produced by a calibrated bore 421 which constitutes a nozzle.
  • zone 318C of the drawer is dimensioned so as to establish contact with the wall of bore 316 by its external surface. Jet 421 is drilled obliquely in this area, so as to put in communication the two spaces delimited on either side of zone 318C of the drawer.
  • the communication conduit is then defined by the calibrated hole 421 in the middle portion of bore 316.
  • control means comprise a first and a second control chamber 328 and 330 which are both formed in the drawer 318.
  • the first chamber 328 is connected in permanence at the first main duct 312 while it is isolated from the second main duct 314.
  • the situation is the opposite for the second room 330, which is permanently connected to conduit 314 while being isolated of conduit 312.
  • chambers 328 and 330 are made in blind holes 327 and 329 which open respectively on the first and second axial ends 318D and 318E of the drawer. As will be seen below, these rooms are however closed from side of these axial ends.
  • Radial holes 332 and 334 extend respectively between the bores 327 and 329 and the axial periphery of the drawer and establish the permanent communication between, respectively, room 328 and the main duct 312, and chamber 330 and duct 314. These holes are possibly provided in gorges.
  • the walls of the chambers 328 and 330 which are on the side of the ends 318D and 318E of the drawer are fixed, so that the increase in pressure in one of these chambers, which causes a displacement of the drawer, also results in an increase in volume of the chamber considered.
  • the delay means which serve to limit the speed of passage of the drawer between one and the other of its extreme positions include a first damping chamber 346, located between the first end 318D of the drawer and the first end of bore 316 closed by plug 319A, as well as a second chamber damping 348, located between the second end 318E of the drawer and the second end of the bore 316 closed by the plug 319B.
  • Rooms 346 and 348 are in permanent communication with a "buffer" fluid enclosure via at least one restriction.
  • this enclosure is constituted by an axial bore 360 communicating with the chambers 346 and 348 by transverse holes, respectively 366 and 368.
  • the buffer enclosure is closed by plugs 361.
  • the volume of the enclosure is constant and therefore contains a volume of buffer fluid predetermined and is permanently isolated from the main conduits, under reserve for possible leaks due to functional play.
  • Restriction means comprising at least one restriction calibrated, are arranged in the buffer enclosure to hinder this fluid displacement.
  • two restrictions respectively 367 and 369, respectively arranged in holes 366 and 368.
  • the first and second control chambers 328 and 330 each have a useful surface on which the fluid pressure acts to cause the drawer to move to its first, respectively towards its second position.
  • the damping chambers 346 and 348 each have a useful surface on which the pressure acts of fluid to hinder the decrease in the volume of this chamber.
  • the ratio between the useful surface of the control chamber and the useful area of the damping chamber constitutes a parameter for controlling the speed of movement of the drawer in the direction of emptying the damping chamber in question.
  • the passage sections of the restriction means 367 and 369, as well as these relationships between the useful surfaces of the associated order and depreciation, may be determined at using simulations to get, in either direction of drawer movement, the desired delay time. Most of the time, we will choose equal time durations for both direction of movement.
  • first control chamber 328 is separated from the first damping chamber 346 by a first cylindrical rod 376 of small cross section which is arranged in the bore blind 327, as well as the second control chamber 330 is separated from the second damping chamber 348 by a second cylindrical rod 378 of small section disposed in bore 329.
  • Rods 376 and 378 are arranged in shirts, respectively 377 and 379, in bores 327 and 329. A contact of slip (made substantially watertight by minimal functional play) is established between these rods and these shirts, so that the rods 376 and 378 remain generally fixed when the drawer is moved.
  • the useful surface of the first control chamber 328 is determined by the area of the free end of the rod 376 which is in this chamber, likewise that the usable area of the second control chamber 330 is determined by the area of the free end of the rod 378 which is in this room.
  • the useful surface of the damping chamber 346 is a function of the section of the first end of the drawer 318D, possible deduction of the section of the rod 376, as well as the useful area of the second damping chamber 348 is a function of the section of the end 318E of the drawer, deduction possibly made of the section of the rod 378.
  • the depreciation volume of chamber 346 is the volume of fluid which, from the position intermediate of figure 9, must be evacuated from this room during the displacement of fluid in the buffer enclosure to allow movement of the drawer 318 over a stroke sufficient to close the communication between conduits 312 and 314.
  • cylindrical rods 376 and 378 are respectively mounted free in holes 327 and 329 (more specifically, in folders 377 and 379). This facilitates the mounting of these rods by avoiding the problems of concentricity between the rods and the bores.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
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Claims (15)

  1. Ventilvorrichtung (10, 210, 310) für mindestens einen Hydraulikmotor (M) zum Antreiben einer großen Schwungmasse, wobei der Motor zwei Hauptleitungen (112, 114) zur Flüssigkeitszuführung und zur Flüssigkeitsableitung aufweist, die durch das Anhalten des Motors verschließbar sind,
    dadurch gekennzeichnet, dass sie zwei Hauptkanäle (12, 14; 212, 214; 312, 314) umfasst, die jeweils dazu bestimmt sind, an die beiden Hauptleitungen des Motors angeschlossen zu werden, dass sie Mittel (18, 20, 22, 24, 28, 30; 218, 220A, 220B, 228, 230; 318, 321; 318, 421) umfasst, um die Hauptkanäle in eine Verbindüngssituation zu versetzen, wenn die Flüssigkeitsdrücke in diesen Kanälen im wesentlichen gleich sind, und um die Hauptkanäle in eine Isoliersituation zu versetzen, in der diese Kanäle voneinander isoliert sind, wenn die Flüssigkeitsdrücke in diesen Kanälen unterschiedlich sind, und dass sie zudem Verzögerungsmittel (39, 41; 46, 53, 48, 57; 228, 253, 230, 257; 346, 348, 367, 369, 378) umfasst, die geeignet sind, um die Geschwindigkeit des Übergangs von der Verbindungssituation in die Isoliersituation zu begrenzen.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Mittel, um die Hauptkanäle in die Verbindungssituation zu versetzen, Mittel umfassen, die eine kalibrierte Verengung (21; 221A, 221B; 321, 421) bilden, wobei der Durchtrittsquerschnitt für die Flüssigkeit, die durch diese Verengung fließt, wenn die Hauptkanäle sich in der Verbindungssituation befinden, viel kleiner ist, als der gewöhnliche Querschnitt der Hauptkanäle (12, 14; 212, 214; 312, 314).
  3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass sie ein bewegliches Organ (18; 218; 318) umfasst, das unter der Einwirkung des Unterschieds zwischen den Flüssigkeitsdrücken, die in den beiden Hauptkanälen (12, 14; 212, 214; 312, 314) herrschen, zwischen drei Stellungen beansprucht werden kann, wobei diese drei Stellungen eine erste und eine zweite Endstellung, in denen die beiden Hauptkanäle sich im Verhältnis zueinander in einer Isolierposition befinden, und eine Zwischenstellung, in der die Hauptkanäle sich im Verhältnis zueinander in einer Verbindungsposition befinden, umfassen, wobei das bewegliche Organ (18; 218; 318) in seine erste Endstellung gebracht wird, wenn der Druck im ersten Hauptkanal (12; 212; 312) größer ist, als der Druck im zweiten Hauptkanal (14; 214; 314), während es in seine zweite Endstellung gebracht wird, wenn der Druck im zweiten Hauptkanal größer ist, als der Druck im ersten Hauptkanal, und es in seine Zwischenstellung gebracht wird, wenn die Drücke in den beiden Hauptkanälen im wesentlichen gleich sind.
  4. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass das bewegliche Organ aus einem Schieber (18; 218; 318) besteht, der gleitend in einer Bohrung (16; 216; 316) angeordnet ist, deren einer Teil sich zwischen den beiden Hauptkanälen (12, 14; 212, 214; 312, 314) erstreckt, wobei dieser Schieber mit Mitteln ausgestattet ist, die einen Verbindungskanal (20, 22, 24; 220A, 221A, 221B, 220B, 222, 224; 321, 421) bilden, welcher die Hauptkanäle (12, 14; 212, 214; 312, 314) in der Zwischenstellung des Schiebers (18; 218; 318) verbindet und welcher in den beiden Endstellungen des Schiebers durch die Wand der Bohrung (16; 216; 316) abgeschlossen ist.
  5. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass sie Mittel umfasst, um eine erste und eine zweite Steuerkammer (28, 30; 228, 230; 328, 330) einzurichten, die sich jeweils an einem ersten und einem zweiten Ende (18A, 18B; 218A, 218B; 318D, 318E) des Schiebers befinden, wobei die erste Kammer (28; 228; 328) mit dem ersten Hauptkanal (12, 212; 312) über einen ersten Verbindungsdurchgang (32; 220A; 332) in Verbindung steht, während die zweite Kammer (30; 230; 330) mit dem zweiten Hauptkanal (14; 214; 314) über einen zweiten Verbindungsdurchgang (34; 220B; 334) in Verbindung steht, wobei die erste Steuerkammer (28; 228; 328) mit Flüssigkeit versorgt werden kann, um den Schieber in seine erste Endstellung zurückzuschieben, wenn der Flüssigkeitsdruck im ersten Hauptkanal (12; 212; 312) größer wird, als der Flüssigkeitsdruck im zweiten Hauptkanal (14; 214; 314), und sich entleeren kann, um die Verschiebung des Schiebers in seine zweite Endstellung zu ermöglichen, wenn der Flüssigkeitsdruck im zweiten Hauptkanal größer wird, als der Flüssigkeitsdruck im ersten Hauptkanal, und wobei die zweite Steuerkammer (30; 230; 330) mit Flüssigkeit versorgt werden kann, um den Schieber in seine zweite Endstellung zurückzuschieben, wenn der Flüssigkeitsdruck im zweiten Hauptkanal (14; 214; 314) größer wird, als der Flüssigkeitsdruck im ersten Hauptkanal (12; 212;312), und sich entleeren kann, um die Verschiebung des Schiebers in seine erste Endstellung zu ermöglichen, wenn der Flüssigkeitsdruck im ersten Hauptkanal größer wird, als der Flüssigkeitsdruck im zweiten Hauptkanal.
  6. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass mindestens einer der ersten und zweiten Verbindungsdurchgänge (220A, 220B) mit einer kalibrierten Verengung (253, 257) ausgestattet ist, um den Flüssigkeitsstrom durch die Durchgänge zu beschränken.
  7. Vorrichtung nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass die erste und die zweite Steuerkammer (28, 30) jeweils eine erste und eine zweite Rückwand (38. 40) umfassen, mit denen das erste und das zweite Ende (18A, 18B) des Schiebers (18) jeweils in Anschlag miteinander zusammenwirken können, dass die Rückwände in der Gleitrichtung des Schiebers beweglich sind, und dass die Vorrichtung erste Rückstellmittel (39) bzw. zweite Rückstellmittel (41) umfasst, das jeweils die erste Rückwand (38) bzw. die zweite Rückwand (40) in der Richtung, die sie dem ersten Ende (18A) des Schiebers (18) bzw. dem zweiten Ende (18B) des Schiebers näher bringt, ständig zurückstellen können.
  8. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass sie eine erste Dämpfungskammer (46), die mit dem ersten Hauptkanal (12) über einen ersten Verbindungs- und Dämpfungsdurchgang (50, 52) in Verbindung steht, sowie eine zweite Dämpfungskammer (48), die mit dem zweiten Hauptkanal (14) über einen zweiten Verbindungs- und Dämpfungsdurchgang (54, 56) in Verbindung steht, umfasst, und dass der erste und der zweite Verbindungs- und Dämpfungsdurchgang jeweils eine kalibrierte Verengung (53, 57) umfassen, um den Flüssigkeitsstrom durch die Durchgänge mindestens in der Entleerungsrichtung der Dämpfungskammern (46, 48) zu beschränken.
  9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass die erste und die zweite Dämpfungskammer (46, 48) jeweils mit den ersten und zweiten Hauptkanälen (12, 14), die jeweils mit einem Rückschlagventil (51, 55) ausgestattet sind, jeweils über einen ersten und einen zweiten Aufladungsdurchgang (50, 54) in Verbindung stehen.
  10. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass die erste und die zweite Steuerkammer (328, 330) in dem Schieber (318) eingerichtet sind, jeweils in der Nähe eines der beiden Enden (318D, 318E) dieses Schiebers.
  11. Vorrichtung nach Anspruch 10, dadurch gekennzeichnet, dass die Dämpfungskammern an den Enden des Schiebers angeordnet sind.
  12. Vorrichtung nach Anspruch 11, dadurch gekennzeichnet, dass sie eine erste Dämpfungskammer (346), die sich zwischen einem ersten Ende (318D) des Schiebers (318) und einem ersten Ende (319A) der Bohrung (316) befindet, in der der Schieber angeordnet ist, sowie eine zweite Dämpfungskammer (348), die sich zwischen einem zweiten Ende (318E) des Schiebers und dem zweiten Ende (319B) der Bohrung befindet, umfasst, wobei diese Dämpfungskammern sich ständig in Verbindung mit einer geschlossenen Einfassung (360, 366, 368) befinden, die ein Pufferflüssigkeitsvolumen enthält, das zwischen diesen beiden Dämpfungskammern (346, 348) hin und her zu verschieben ist, um die Verschiebung des Schiebers (318) zu ermöglichen, die mittels der Steuerkammern (328, 330) gesteuert wird.
  13. Vorrichtung nach Anspruch 12, dadurch gekennzeichnet, dass Mittel zur kalibrierten Verengung (367, 369) in der geschlossenen Einfassung (360, 366, 368) angeordnet sind.
  14. Vorrichtung nach einem der Ansprüche 12 und 13, dadurch gekennzeichnet, dass die erste Steuerkammer (328) in einer ersten Sackbohrung (327) ausgeführt ist, die am ersten Ende (318D) des Schiebers (318) mündet und von der ersten Dämpfungskammer (346) durch einen ersten zylindrischen Stift (376) getrennt ist, der in dieser Bohrung (327) angeordnet ist, und dass die zweite Steuerkammer (330) in einer zweiten Sackbohrung (329) ausgeführt ist, die am zweiten Ende (318E) des Schiebers (318) mündet und von der zweiten Dämpfungskammer (348) durch einen zweiten zylindrischen Stift (378) getrennt ist, der in dieser zweiten Bohrung (329) angeordnet ist.
  15. Vorrichtung nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, dass sie zu einem Hydraulikblock gehört, der dazu bestimmt ist, auf dem Gehäuse des Hydraulikmotors befestigt zu werden.
EP99400564A 1998-03-11 1999-03-09 Ventileinrichtung für einen hydraulischen Motor zum Antreiben einer Masse grossens Trägheitsvermögens Expired - Lifetime EP0942103B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR9802967A FR2776032B1 (fr) 1998-03-11 1998-03-11 Dispositif de valve pour un moteur hydraulique apte a entrainer une masse d'inertie importante
FR9809354 1998-07-22
FR9802967 1998-07-22
FR9809354A FR2781532B1 (fr) 1998-07-22 1998-07-22 Dispositif de valve pour un moteur hydraulique apte a entrainer une masse d'inertie importante

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EP0942103A1 EP0942103A1 (de) 1999-09-15
EP0942103B1 true EP0942103B1 (de) 2003-10-01

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EP3835599A1 (de) * 2019-12-12 2021-06-16 XCMG European Research Center GmbH Dämpfungssystem für hydraulische systeme
FR3121482B1 (fr) * 2021-03-30 2023-03-31 Poclain Hydraulics Ind Système d’entrainement amélioré pour un organe de véhicule ou d’engin
US11725478B2 (en) 2021-10-20 2023-08-15 Baker Hughes Oilfield Operations Llc Flow control device, method, and system

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Also Published As

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EP0942103A1 (de) 1999-09-15
DE69911674T2 (de) 2004-07-01
US6295811B1 (en) 2001-10-02
JP2000002202A (ja) 2000-01-07
JP4479976B2 (ja) 2010-06-09
DE69911674D1 (de) 2003-11-06

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