EP2256350B1 - Dispositif d'amortissement hydraulique et système de réglage - Google Patents

Dispositif d'amortissement hydraulique et système de réglage Download PDF

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Publication number
EP2256350B1
EP2256350B1 EP09007166A EP09007166A EP2256350B1 EP 2256350 B1 EP2256350 B1 EP 2256350B1 EP 09007166 A EP09007166 A EP 09007166A EP 09007166 A EP09007166 A EP 09007166A EP 2256350 B1 EP2256350 B1 EP 2256350B1
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EP
European Patent Office
Prior art keywords
bore
cross
section
variable
throttle
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Active
Application number
EP09007166A
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German (de)
English (en)
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EP2256350A1 (fr
Inventor
Georg Jemüller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hawe Hydraulik SE
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Hawe Hydraulik SE
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Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to ES09007166T priority Critical patent/ES2367544T3/es
Priority to AT09007166T priority patent/ATE516443T1/de
Priority to EP09007166A priority patent/EP2256350B1/fr
Priority to US12/783,204 priority patent/US8511081B2/en
Publication of EP2256350A1 publication Critical patent/EP2256350A1/fr
Application granted granted Critical
Publication of EP2256350B1 publication Critical patent/EP2256350B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve

Definitions

  • the invention relates to a hydraulic damping device according to the preamble of patent claim 1 and to a control system according to the preamble of patent claim 12.
  • an adjusting throttle are arranged in a discharge path from the adjusting piston of the variable-displacement pump to the low-pressure side and an adjusting throttle in a discharge path from a 3/2 directional spool valve to the low-pressure side.
  • the 3/2-way slide valve regulates from the supply pressure, for example, load pressure-dependent, the loading of the actuating piston and the discharge of the actuating piston to the low pressure side.
  • the damping is due to internal leaks on the variable throttle.
  • Each variable throttle has an adjusting element in order to adjust the throttle cross section as required.
  • An optimal damping of pressure oscillations in the control system of the variable displacement pump requires, for example, to take into account the system-related relationship between the internal leakage at the downstream side of the actuating piston and the internal leakage at the downstream side of the 3/2-way spool valve, ie, when reducing the one throttle cross-section the other Enlarge throttle area. If adjustments are to be made to the two adjusting elements of both adjusting throttles, it is difficult to perform the adjustments relatively accurately according to the system-related law in the control system. Such adjustments require a great deal of skill and skill, are time consuming because the effect of an adjustment made can only be determined during operation, and actually only lead to a compromise between the final throttle cross-sections of the adjustment throttle. Because the manufacturer of the control system, which knows the system-related law, has no influence on user-executed settings. In addition, the structural complexity for two variable throttle with its own adjustment is high.
  • a control system of a variable displacement pump wherein for pressure control of a multi-way valve for two actuating cylinders of the variable displacement a 4/3-way valve feedback control valve is provided, which is actuated depending on the pressure of one of the actuating cylinder.
  • a zero position is adjustable, in which the two pilot pressure sides for the multi-way valve are relieved jointly via two fixed throttle to the tank. If the feedback directional control valve is moved from the zero position, the fixed throttles are blocked by the valve element of the feedback directional control valve.
  • variable displacement multi-way valve provided either manually via a lever or druckvorquaint operable pressure compensator, in which a piston with two coils mutually blind-like cooperates with outlets to a Connect pressure port to either the tank or a secondary control channel.
  • a hydraulic control device for a work machine which is fed by a variable displacement pump.
  • a main circulation valve is provided, which is actuated by a solenoid valve to discharge the pressure medium either directly to the tank or to supply a group of multi-way valves for different consumers.
  • Each multi-way valve of the group contains a passage to the tank, which is open in the neutral position of the multi-way valve directly to the tank and quickly shut off when adjusting the multi-way valve from the neutral position.
  • GB 1 095 347 A relates to a fluid pressure servomechanism with a valve in which a rotatable valve element simultaneously adjusts two adjusting throttles in its rotational movement.
  • Out DE 32 27 452 A is a control and regulating device for an adjustable hydrostatic unit is known in which a hydrostatic motor is provided as the drive source of a pressure network line for constant pressure as possible, which drives via an output shaft serving as a speed signal generator auxiliary control pump.
  • a control pressure delivery line The control auxiliary pump designed as a fixed displacement pump is connected to the tank via an adjusting throttle.
  • An output line of the hydraulic auxiliary motor driving the auxiliary hydraulic motor is also connected to the tank for actuating an adjusting cylinder of the hydraulic motor via a multi-way control valve and a further adjusting throttle.
  • the two adjusting throttles can be connected to one another in opposite directions. However, the variable throttles do not serve to dampen pressure oscillations, but to specify the target speed of the hydraulic motor in both directions of rotation.
  • the invention has for its object to provide a hydraulic damping device and a control system in which in a structurally simple manner, quickly and without special expertise each optimal damping is adjustable.
  • the two variable restrictors, the outflow paths and the connection to the low pressure side and the adjusting element are housed in a housing.
  • the two outflow paths are merged at a Abströmweg node from which, preferably, a single connection leads to the low pressure side.
  • the two variable restrictors are arranged communicating with each other at the outflow path node, and use the same connection to the low pressure side.
  • An outflow path to the low pressure side is a straight through hole in the housing.
  • the other outflow path intersects the through-bore at the outflow-node with a transverse, preferably perpendicular, extending bore, which opens into the through hole.
  • the adjusting element is arranged in the bore or an extension of this bore and adjustable in the direction of the bore axis. It can be quickly achieved optimal damping, since a change of a throttle cross section to the larger at the same time forces the change of the other nozzle cross section to the smaller, and the processes of the changes systemic legality.
  • An adjustment is comfortable and quickly carried out, since it is only to manipulate on an adjustment, and the adjustment at least within a portion of the entire Verstellhubes reduced a throttle cross-section and increases the other throttle cross-section according to the system-related law, or vice versa.
  • the mechanical combination of the two variable throttles for opposing simultaneous change in the throttle cross sections results in a considerable structural simplification. The user can easily find an optimal setting because he only needs to change one throttle area, and then automatically the other throttle area has the right size.
  • the control system is characterized by the fact that the dynamic behavior of the variable displacement pump for adjustments, eg. B. load pressure-dependent adjustments, is favorably damped.
  • the damping device By means of the damping device, an overshoot can be minimized or avoided as well as oscillating reactions during the adjustment of the variable displacement pump.
  • the throttle cross-sections are reversible linearly in opposite directions.
  • the respective positive or negative gradients in the linear change may be equal or unequal, z. B. in each case in adaptation to the system-related law between the two internal leaks in the control system.
  • the throttle cross-sections may occur simultaneously and in opposite directions, but along non-linear equal or unequal curves with equal or unequal positive and negative gradients, respectively. In this way, the system-related law between the two control parameters may be even better taken into account.
  • At least the throttle cross-section of an adjusting nozzle in a start and / or end portion of the Verstellhubes to a minimum or maximum size substantially constant, so that there is at least one plateau in the curve of the change of the throttle cross section on the Verstellhub.
  • a plateau can be set constructively for one or both variable throttles, and either only at the beginning or only at the end or at the beginning and at the end of the adjustment stroke. Such a plateau may even, if appropriate to the systemic law, within the Verstellhubes, z. B. in a central region, be predetermined for one or the other or for both variable throttles.
  • the throttle cross-section of a variable throttle is defined at least by the outer periphery of a dipping from the bore into the through hole head and the inner wall of the through hole, wherein the head may be attached to the adjusting or part thereof.
  • the head acts as a throttle body, which depending on the position of the adjusting within the Verstellhubes increasingly throttles or releases the through hole.
  • the throttle cross-section of the other variable throttle is defined in part in an opening into the through-hole outlet channel in the head and its other part by a cross-channel passing through the head and the inner wall of the through hole.
  • the adjustment at least one mouth of the transverse channel in the head like an aperture cooperates with the inner wall of the through hole or the intersection edge between the bore and the through hole. The blind-like cooperation allows a sensitive change of this throttle cross-section.
  • a fixed throttle may be arranged in the head between the mouth of the outlet channel and a communication connection with the transverse channel, whose cross-section is smaller than the cross section of the transverse channel.
  • This fixed throttle and the adjustable throttle cross section of the other variable throttle act parallel to each other.
  • the mouth of the transverse channel is covered by the inner wall of the bore, only the fixed throttle, so that irrespective of a further change in the throttle cross section of a variable throttle the fixed throttle a largely constant throttle cross section aufrecht conception.
  • the z. B. is smaller than the cross section of the transverse channel.
  • This remaining free throttle cross section remains in the maximum end position of the adjustment open. Part of this remaining free throttle cross-section may also be the then acting for the one variable throttle cross-channel of the other variable throttle.
  • the throttle cross-section of the other variable throttle is defined by the inner wall of a provided between the outflow opening into the hole and the through hole and at least two, preferably three, connected in series throttle points at the head of the actuating element, preferably by at least one longitudinal groove, preferably a plurality of circumferentially distributed longitudinal grooves, in the head, and two separated by a constriction, interrupted by the longitudinal groove, formed on the head coils whose outer diameter corresponds approximately to the inner diameter of the bore.
  • This embodiment is favorable in terms of production because both the bore and the collars and the constriction as well as the at least one longitudinal groove can be manufactured with simple tools and high precision, expedient for a design of the damping device made of steel components.
  • the series throttling points produce a combinatorial throttling effect until the front collar in the direction of adjustment has entered the through hole and only the rear throttling point acts. It can be achieved in this way a structurally predetermined non-linear course of the change of the throttle cross-section of the other variable throttle. If desired, the throttle cross-section can remain substantially constant until the front collar emerges from the bore into the through-bore, despite the adjusting movement of the actuating element, in order to achieve a plateau effect.
  • the adjusting element is mechanically, for. B. manually adjusted by means of a tool or a knob.
  • this can also be an actuator can be used, which twists the set screw.
  • the adjustment can be remotely adjusted hydraulically or electrically or electromagnetically and directly linear within the Verstellhubes.
  • a piston, a proportional solenoid, or a stepper motor can be used.
  • Fig. 1 illustrates as one of various possible applications for a hydraulic damping device D according to the invention, a control system S of a hydraulic variable displacement pump P.
  • the variable displacement pump P pumps into a pressure line 1 and via a node 2, for example, a valve assembly 3 for controlling at least one hydraulic consumer, not shown whose load pressure is tapped via a control line 6.
  • From node 2 branches off a line 4 to a 3/2-way spool valve 7, with which via a line 9, a control piston 10 can be acted upon, the variable displacement pump P (counterclockwise) to a minimum flow rate and (clockwise) to a maximum Displacement adjusted, supported by an opposite working another spring piston 10 '.
  • the 3/2-way spool valve 7 is acted upon from a branching off from the line 4 control line 5 with a pilot pressure in the direction of a control position in which the line 4 is connected to the line 9 and the actuator piston 10 is fully applied.
  • the 3/2-way spool valve 7 is acted upon via the control line 6 and a preferably adjustable spring 8 in the direction of a control position, in which the line 9 with a Abströmweg 13 to a low pressure side 17 (a reservoir R) is connected to reduce the pressurization of the actuating piston 10.
  • a discharge path 12 also to the low pressure side 17 from.
  • the outflow paths 12, 13 lead via the hydraulic damping device D, in which an adjusting throttle D1 in Abströmweg 13 and an adjusting throttle D2 are arranged in Abströmweg 13, to a reservoir R.
  • the throttle cross-sections of the two adjusting throttles D1, D2 adjustable, by means of a generally indicated, common adjustment element 14.
  • the two variable throttle D1, D2 are mechanically coupled, such that (see directions of arrows 15, 16) is reduced throttle cross-section and at the same time the other Throttle cross-section is increased, and vice versa, and at least within a portion of the Verstellhubs the adjustment 14.
  • About the hydraulic damping device D occur internal leaks that cause damping of pressure oscillations in the control system S, and thus overshoot or a swinging response of adjustments Minimize or exclude the variable displacement pump P.
  • the internal leaks via the two variable throttles D1, D2 are two control parameters of the control system S, between which there is a system-related law, which is taken into account constructively in the hydraulic damping device D.
  • Fig. 2 illustrates in a longitudinal section a concrete embodiment of the hydraulic damping device D, which, for example, in the control system S of Fig. 1 is usable, and used in part reference numerals that are already in Fig. 1 appear.
  • the two adjusting throttles D1, D2 are structurally housed in a housing 18 which passes through a through hole 19.
  • a housing 18 which passes through a through hole 19.
  • the line 17 or the low pressure side defines.
  • a bore 40 is provided in the housing 18 transversely to the through hole 19, preferably perpendicular to it, which intersects the passage hole 19 at a Abströmweg node K and opens into it.
  • the common adjusting element 14 both adjusting throttles D1, D2, for example in the form of a screw 21, housed.
  • the adjusting screw 21 can be screwed with a threaded portion 24 in the bore 40 in the direction of the bore axis, for example by means of a hexagon socket 22 or a rotary knob, not shown.
  • an actuator 23 may be provided which acts on the adjusting screw 21, z.
  • an electric motor or stepper motor, a proportional solenoid, or a hydraulic cylinder to adjust the hydraulic damping device D remotely operable.
  • the screw 21 could act directly a linear actuator or operate the linearly movable actuator 14.
  • the adjusting screw 21 then has on the threaded portion 24 a constriction 25, in the region in the housing 18, a further bore 20 opens, to which the outflow 12 is connected. Subsequent to the constriction 25, the adjusting screw 21 has a head 26 which, for example, has a spherical or rounded outer contour 27, and which dips into the through-bore 19 in the area of the outflow-way node K.
  • the outer contour 27 of the head 26 defines with an inner wall 28 of the through hole 19, the throttle cross section of a variable throttle D2. The further the adjusting screw 21 in Fig. 2 is screwed, the smaller is the throttle cross-section of the variable throttle D2.
  • transverse channels 30 From the constriction 25 lead branch channels 29, for example, two mutually 90 ° crossing transverse channels 30 in the head 26. At least one mouth of a transverse channel 30 can blind with the intersection edge on the inner wall 28 of the through hole 19 together, depending on the depth of the screw 21. Von Here, as an option, the transverse channels 30 extend an approximately axial outlet channel 32 to the free front end of the head 26.
  • a fixed throttle 31 is provided between the transverse channels 30 and the mouth of the outlet channel 32 in the end face of the head 26 whose throttle cross section is smaller than the cross section of the transverse channels 30.
  • the axial distance of the transverse channels 30 from the front end of the head 26 is chosen so that when further screwed up screw 21 than in Fig. 2 shown, the mouths of the transverse channels 30 are closed by the wall of the bore 40, and only a flow path through the fixed throttle 31 is open in the through hole 19.
  • the adjusting screw 21 is adjusted within a range in which the mouths of the transverse channels 30 are closed, although the throttle cross section of a variable throttle D2 varies, but the throttle cross section of the fixed throttle 31 remains unchanged (plateau effect) or alone effective as explained later. Furthermore, within the Verstellhubes the screw 21 through the blind-like cooperation between at least one mouth of the transverse channels 30 and the inner wall 28 of the through hole 28 of the throttle cross section of the other variable throttle D1 changed, z. B. be increased.
  • the throttle cross-section of the one adjusting throttle D2 can be reduced in size or at least kept substantially constant that with a reduction or enlargement of the throttle cross section between the outer periphery 27 of the head 26 and the inner wall 28 of the through hole 19 simultaneously a reduction or enlargement of the aperture cross section between the transverse channels 30 and the inner wall 28 of the through hole 19 takes place, that is, that then an adjusting throttle D2 also shares the provided for the other adjusting throttle D2 transverse channels 30.
  • Fig. 3 shows a longitudinal section of another embodiment of the damping device D.
  • the bore 40 to the through hole 19 contains the screw as verstellschraube with a lock nut common adjustment element 14 both Verstelldrosseln D1, D2 and is connected via a smaller diameter bore 39 with the through hole 19.
  • the Abströmweg 12 opens into the bore 40 between the sealed shaft 25 and the bore 39.
  • a transverse bore 40 intersecting screw 44 forms a stop for the actuator 14.
  • the through hole 19 in the block 18, for example, the block of 3/2 -Way gate valve 7 of Fig. 1 is formed as a blind bore, which emanates directly from the slide bore.
  • the head 26 with its rounded outer contour 27 defines with the inner wall 28 of the through hole 19 the adjusting throttle D2 in Abströmweg 13.
  • the shaft 25 tapers to the head 26 and includes at least one longitudinal groove 38, preferably a plurality, for example three, circumferentially distributed longitudinal grooves one certain depth and width.
  • a narrower collar 41 is formed in the direction of insertion of the adjusting element 14 into the through-bore 19 and is separated by a constriction 42 from a wider collar 43 located behind it. Both bundles 41, 43 are interrupted by the at least one longitudinal groove 38.
  • the outer diameter of the collars 41, 43 are only slightly smaller than the inner diameter of the bore 39. In this way, in the embodiment shown, two series-connected throttle points are formed, which in the in Fig. 3 shown position of the adjusting element 14 combinatorial act.
  • the pressure medium entering from the discharge path 12 is first throttled in the first throttle point of the longitudinal groove 38 between the collar 43 and the inner wall of the bore 39, can then expand in the region of the constriction 42, and is then in the second throttle point in the longitudinal groove 38 between the Bund 41 and the inner wall of the bore 39 throttled before it enters the through hole 19.
  • This is a position of the adjusting element 14 with maximum throttling in the one adjusting throttle D1.
  • the other variable throttle D2 has a maximum throttle cross-section.
  • adjusting element 14 If the adjusting element 14 continues as in Fig. 3 shown screwed, then enters the head 26 with the collar 41 further into the through hole 19 a. It then acts only the throttle in the longitudinal groove 38 between the collar 43 and the inner wall of the bore 39, and possibly also the throttle point in the constriction 42.
  • the usable throttle cross-section of a variable throttle D1 is thus increased, while the effective throttle cross-section of other variable throttle D2 is reduced.
  • Fig. 4 The throttle cross-sections A are simultaneously changed in opposite directions, ie, with a reduction of the throttle cross-section of a variable throttle D2 is an increase in the throttle cross-section of the other Adjusting throttle D1 accompanied, and vice versa.
  • the changes in the throttle cross-sections of the two variable throttles D1, D2 are in Fig. 4 are shown as straight lines 33, 35, wherein their positive and negative gradients may be the same or different.
  • the position of the intersection of the straight lines 35, 33 within the Verstellhubes h is structurally predetermined.
  • the throttle cross-sections A both Verstelldrosseln D1, D2 or only the throttle cross-section A of the variable throttles D1 or D2 (indicated by dashed lines) according to design curves 35 ', 33' of the same or different shapes and the same or unequal positive or negative gradient can be changed.
  • Fig. 4 indicated that at least one of the lines 35, 33 or the curves 33 ', 35' has a plateau 36 or 37, here at an end portion.
  • This plateau means that the respective throttle cross section A at an adjustment does not change anymore.
  • the plateau 37 results from the fixed throttle 31 in Fig. 2 when the transverse channels 30 are closed.
  • a plateau in the straight line or the curve 33, 33 'of the variable throttle D1 for example, by the interaction between the reduction of the cross section between the outer periphery 27 of the head 26 and the inner wall 28 of the through hole 19 and the simultaneous reduction or enlargement of the aperture between at least one Mouth of a transverse channel 30 and the inner wall 28 of the through hole 19 are generated.
  • a plateau may also be structurally predetermined in an intermediate region of the adjustment stroke h in one or the other or in both adjusting throttles D1, D2.
  • Fig. 5 illustrates the hydraulic damping device D in symbolic representation. It is actually a kind of 3/2-way valve between the discharge paths 12, 13 and the low pressure side 17. This valve is actuated by the common adjusting element 14 (the adjusting screw 21) between three positions.
  • the outflow 12 is in Fig. 2 with stronger throttling effect with the low pressure side 17 via the cross section between the outer periphery 27 of the head 26 and the inner wall 28 of the through hole 19 and the aperture between at least one mouth of a transverse channel 30 and the inner wall 28 of the passage 19.
  • the Abströmweg 13 is connected to the low pressure side 17 via which the throttle cross section between the mouth of at least one transverse channel 30 and the inner wall 28 of the through hole 19.
  • the parallel-connected fixed throttle 31, if present, plays no role as long as the aperture cross section is greater than the cross section of the fixed throttle 31st
  • the Abströmweg 12 is connected with even less throttling over the cross section between the outer periphery 27 of the head 26 and the inner wall of the through hole 19 with the low pressure side 17, while the Abströmweg 13 is connected only via the fixed throttle 31 with the low pressure side 17 ( Plateau).
  • the middle position is a control range in which the throttle cross-sections are changed in opposite directions.
  • the discharge path 13 with minimum throttling or without significant throttling or the outflow 12 can be effective with minimal or no throttling.
  • transverse channels 30 could in an alternative embodiment in a circumferential circumferential groove (not shown) of the head 26 open to irrespective of the relative rotational position of the head 26 and the screw 21 a well-defined blind-like cooperation with the inner wall 28 of the through hole 19 and To achieve Verschneidungskante between the bore 40 and the through hole 19, which depends strictly on the depth of the screw 21.
  • the head 26 could be coupled to the adjusting screw 21 via a rotatable connection, and linearly displaceably guided, for example, by a pin engaging in an axial guide groove and prevented from turning, so that only one, for example, coaxial with the through hole 19 transverse channel 30 with its mouth only depending on the depth of engagement of the screw 21 defines exactly cooperates with the inner wall 28 of the through hole 19 and the intersection edge between the bore 40 and the through hole 19 like an aperture.
  • the fixed throttle 31, a replaceable screwed Einschraubdrossel could be replaced, which can be exchanged for another screw with other throttle cross-section.
  • the mouths of the transverse channels 30 and / or the outer periphery 27 of the head 26 could be formed with a special geometric shape to change the respective throttle cross-section when screwing the screw 21 according to predetermined criteria, for example, the in Fig. 4 To achieve gradients and / or the plateaus shown.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (12)

  1. Dispositif d'amortissement hydraulique (D) pour des paramètres de réglage d'un système de réglage (S), en particulier pour un système de réglage (S) de pompes à cylindrée variable, comprenant deux étranglements (D1, D2) disposés dans des parcours d'échappement séparés (12, 13) en direction d'un côté basse pression, la section transversale d'étranglement active (A) d'au moins un étranglement étant modifiable à l'intérieur d'une course de réglage (h), caractérisé en ce que les deux étranglements réglables (D1, D2), les deux parcours d'échappement (12, 13), le côté basse pression et un élément de réglage (14), commun aux deux étranglements réglables (D1, D2) et ajustable sur la course de réglage (h), sont logés dans un carter (18) dans lequel les deux parcours d'échappement (12, 13) sont réunis sur un noeud (K) de parcours d'échappement, à partir duquel un parcours d'échappement unique (17) s'étend en direction du côté basse pression, que les deux étranglements réglables (D1, D2) communiquent entre eux dans le noeud (K) de parcours d'échappement, l'un des parcours d'échappement (13, 17) étant un alésage de passage (19) dans le carter (18) et l'autre parcours d'échappement (12) débouchant sur le noeud (K) par un alésage (40), qui coupe transversalement l'alésage de passage (19), que l'élément de réglage (14), qui couple mécaniquement les deux étranglements réglables (D1, D2), a une disposition ajustable dans l'alésage (40) ou dans un prolongement d'alésage en direction de l'axe de l'alésage, et modifie simultanément en sens contraire, au moins à l'intérieur d'une section de la course de réglage (h), les sections transversales (A) des deux étranglements réglables (D1, D2).
  2. Dispositif d'amortissement hydraulique suivant la revendication 1, caractérisé en ce que les sections transversales d'étranglement (A) sont modifiables linéairement en sens contraire, de préférence avec des gradients égaux ou inégaux positivement et négativement.
  3. Dispositif d'amortissement hydraulique suivant la revendication 1, caractérisé en ce que les sections transversales d'étranglement (A) sont modifiables en sens contraire le long de courbes (33', 35') non linéaires égales ou inégales.
  4. Dispositif d'amortissement hydraulique suivant l'une au moins des revendications précédentes, caractérisé en ce que, lors d'un déplacement de l'élément de réglage (14), au moins la section transversale d'étranglement (A) d'un étranglement réglable (D1, D2) peut être maintenue de façon essentiellement constante à une grandeur minimale ou maximale dans une section initiale et/ou finale de la course de réglage (h), au moins essentiellement le long d'un plateau (36, 37).
  5. Dispositif d'amortissement hydraulique suivant la revendication 1, caractérisé en ce que la section transversale (A) d'un étranglement réglable (D2) des deux étranglements réglables (D1, D2) est définie au moins par le pourtour extérieur d'une tête (26), qui plonge de l'alésage (40) dans l'alésage de passage (19), et de la paroi intérieure (28) de l'alésage de passage (19), la tête (26) étant montée sur l'élément de réglage (14) ou faisant partie de ce dernier, et que la section transversale d'étranglement (A) d'un autre étranglement (D1) des deux étranglements réglables (D1, D2) est définie en partie par un canal d'échappement (32), qui débouche dans l'alésage de passage (19), et en une autre partie par au moins un canal transversal (30), qui traverse la tête (26), et la paroi intérieure (28) de l'alésage de passage (19), au moins un débouché du canal transversal (30), qui communique avec le canal d'échappement (32), coopérant à la manière d'un obturateur avec la paroi intérieure (28) de l'alésage de passage (19).
  6. Dispositif d'amortissement hydraulique suivant la revendication 5, caractérisé en ce qu'un étranglement fixe (31), dont la section transversale est plus petite que celle du canal transversal (30), est disposé dans la tête (26) entre le débouché du canal d'échappement (32) et une liaison de communication avec le canal transversal (30).
  7. Dispositif d'amortissement hydraulique suivant la revendication 5, caractérisé en ce qu'une section transversale d'étranglement libre, de préférence plus petite que la section transversale du canal transversal (30), peut être formée entre le pourtour extérieur (27) de la tête (26) et la paroi intérieure (28) de l'alésage de passage (19), en position de plongée maximale de la tête (26) dans l'alésage de passage (19).
  8. Dispositif d'amortissement hydraulique suivant la revendication 5, caractérisé en ce que, à l'intérieur d'au moins une section partielle de la course de réglage (h), la section transversale d'obturation ouverte entre le canal transversal (30) et la paroi intérieure (28) de l'alésage de passage (19) fait partie simultanée des sections transversales d'étranglement (A) des deux étranglements réglables (D1, D2).
  9. Dispositif d'amortissement hydraulique suivant la revendication 1, caractérisé en ce que la section transversale d'étranglement (A) de l'autre étranglement réglable (D1) est définie par la paroi intérieure d'un alésage (39), prévu entre le parcours d'échappement (12) qui débouche dans l'alésage (40) et l'alésage de passage (19), et par au moins deux, de préférence trois, points d'étranglement sur la tête (26) montés en série, de préférence dans au moins une gorge longitudinale (38), de préférence plusieurs gorges longitudinales (38) de la tête (26) réparties dans la direction périphérique, et par deux collets (41, 43) conformés sur la tête (26), séparés par un rétrécissement (42) et coupés par la gorge longitudinale (38), collets dont le diamètre extérieur correspond approximativement au diamètre intérieur de l'alésage (39).
  10. Dispositif d'amortissement hydraulique suivant la revendication 1, caractérisé en ce que l'élément de réglage (14) est une vis de réglage (21) pouvant être vissée dans l'alésage (40), laquelle vis présente entre la tête (26) et une section filetée (24) un rétrécissement (25) situé dans la zone du débouché du parcours d'échappement (13) dans l'alésage (40).
  11. Dispositif d'amortissement hydraulique suivant l'une au moins des revendications précédentes, caractérisé en ce que l'élément de réglage (14) est ajustable mécaniquement, par exemple manuellement ou par moteur, par exemple par un actuateur (23), ou est réglable à distance par voie hydraulique ou électrique ou électromagnétique.
  12. Système de réglage (R) pour une pompe à cylindrée variable (P) ajustable par au moins un piston de réglage (10), le piston de réglage (10) pouvant être sollicité par une pression de réglage dérivée de la pression de refoulement de la pompe (P) par l'intermédiaire d'un distributeur 3/2 (7) à commande pilote de pression, et un dispositif d'amortissement hydraulique (D) étant prévu pour influer sur le comportement dynamique de la pompe à cylindrée variable (P), lequel dispositif présente un étranglement (D1, D2) dans un parcours d'échappement (12) du piston de réglage (10) et dans un parcours d'échappement (13) du distributeur 3/2 respectivement en direction d'un côté basse pression (17), caractérisé en ce que les deux étranglements (D1, D2) sont des étranglements réglables et sont couplés mécaniquement par un élément de réglage (14) commun, déplaçable linéairement sur une course de réglage (h), et que les sections transversales (A) des deux étranglements réglables (D1, D2) sont modifiables simultanément et en sens contraire par l'intermédiaire d'au moins une section partielle de la course de réglage (h).
EP09007166A 2009-05-28 2009-05-28 Dispositif d'amortissement hydraulique et système de réglage Active EP2256350B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
ES09007166T ES2367544T3 (es) 2009-05-28 2009-05-28 Dispositivo amortiguador hidráulico y sistema de regulación.
AT09007166T ATE516443T1 (de) 2009-05-28 2009-05-28 Hydraulische dämpfungsvorrichtung und regelsystem
EP09007166A EP2256350B1 (fr) 2009-05-28 2009-05-28 Dispositif d'amortissement hydraulique et système de réglage
US12/783,204 US8511081B2 (en) 2009-05-28 2010-05-19 Hydraulic damping assembly and regulating system

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EP09007166A EP2256350B1 (fr) 2009-05-28 2009-05-28 Dispositif d'amortissement hydraulique et système de réglage

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EP2256350B1 true EP2256350B1 (fr) 2011-07-13

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ITPR20090100A1 (it) * 2009-11-30 2011-06-01 Walvoil Spa Dispositivo di controllo del segnale di pressione di pilotaggio

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GB1095347A (fr)
JPS59713B2 (ja) 1974-04-08 1984-01-07 三菱重工業株式会社 ユアツポンプノ リユウリヨウセイギヨソウチ
DE3227452A1 (de) 1981-08-03 1983-02-17 Linde Ag, 6200 Wiesbaden Steuer- und regeleinrichtung fuer eine einstellbare hydrostatische einheit
US4480438A (en) 1982-01-20 1984-11-06 Vickers, Incorporated Power transmission
DE10247665B4 (de) * 2002-10-11 2006-05-11 Brueninghaus Hydromatik Gmbh Regelvorrichtung und Ventilblock für eine Regelvorrichtung
JP4096901B2 (ja) 2004-03-17 2008-06-04 コベルコ建機株式会社 作業機械の油圧制御装置

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EP2256350A1 (fr) 2010-12-01
ES2367544T3 (es) 2011-11-04
US20100310386A1 (en) 2010-12-09
US8511081B2 (en) 2013-08-20

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