EP3093505B1 - Dispositif de commande hydraulique et sélecteur - Google Patents

Dispositif de commande hydraulique et sélecteur Download PDF

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Publication number
EP3093505B1
EP3093505B1 EP15167051.0A EP15167051A EP3093505B1 EP 3093505 B1 EP3093505 B1 EP 3093505B1 EP 15167051 A EP15167051 A EP 15167051A EP 3093505 B1 EP3093505 B1 EP 3093505B1
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EP
European Patent Office
Prior art keywords
control
pressure
valve
hydraulic
pump
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.)
Not-in-force
Application number
EP15167051.0A
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German (de)
English (en)
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EP3093505A1 (fr
Inventor
Sascha Rümenap
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Priority to EP15167051.0A priority Critical patent/EP3093505B1/fr
Publication of EP3093505A1 publication Critical patent/EP3093505A1/fr
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Publication of EP3093505B1 publication Critical patent/EP3093505B1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • 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
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/653—Methods of control of the load sensing pressure the load sensing pressure being higher than the load 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/783—Sequential 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/85—Control during special operating conditions
    • F15B2211/851—Control during special operating conditions during starting

Definitions

  • the form pressure circuit includes a 3/2-way valve, which is pressure-controlled from a connected to the shuttle valve control line against a spring, which influences the predetermined form.
  • the 3/2-way valve under the force of the spring, connects the load pressure signal tap of the pressure line leading to the further proportional spool to the load pressure signal circuit, while the control line is shut off by the shuttle valve.
  • the 3/2-way valve upstream pressure relief valve limits the maximum, can be fed into the load pressure signal pressure, so that the delivery control causes the pump to initially build only the predetermined form in the pressure line.
  • the control line coming from the shuttle valve is connected to the load pressure signal circuit, while blocking the coming from the load pressure signal tap the pressure line control line and the pressure relief valve are inoperative.
  • the admission pressure circuit is arranged either in a housing block of the selector valve, or in an intermediate block.
  • the pressure relief valve and the 3/2-way valve are physically small and inexpensive, since they have to process only small amounts of control pressure medium. In any case, however, the incorporation of the 3/2-way valve with its connection channels inconveniently high effort.
  • the selector valve a 4/2-way solenoid valve between the pump line and the pressure line to the other proportional slide and the return.
  • the pressure line is additionally connected via a 2/2-way valve and a quantity-limiting throttle with the pressure relief valve of the form pressure circuit and the shuttle valve in the load pressure signal circuit.
  • the 2/2-way valve is against a spring influencing the form of a leading to the shuttle valve control line z. B. from pressure-controlled another hydraulic consumer. Since the form pressure circuit for adjusting the form is fed directly from the pressure line, at least the 2/2-way valve is bulking and expensive. The structural complexity of the 2/2-way valve, its inclusion, and its connection channels is high.
  • Out DE 4230 185 C2 is a 4/3-way proportional spool with a supply regulator in the load pressure signal circuit known in which the direction detection of the respective deflection a only in a respective control position continuous control pressure connection is used. Despite this additional control function for the control pressure of the spool and the housing are optimally short.
  • the invention has for its object to provide a hydraulic control of the type mentioned with structurally simplified form pressure circuit and a low-cost selector valve.
  • the selector valve itself undertakes the task to control the load pressure signal to the pressure relief valve when form in the pressure line to the further proportional spool form, eliminating the need to provide a separate switching valve for this control function.
  • This saving is also advantageous because omitted channels for an additional switching valve, which require high processing effort when training, for example, in a steel block housing and with multiple bends.
  • the selector valve is useful for hydraulic controls that are operated with a form pressure circuit because the selector valve itself can take over the task to fürzuêtn to the pressure relief valve of the form pressure circuit as soon as form is to build, however, to make the pressure relief valve inoperative as soon as is independent of load to control.
  • the selector valve is a proportional control spool incorporated into the load pressure signal circuit, preferably a proportional proportional control spool with proportional solenoids and pressure pilot controls.
  • the proportional spool is functionally associated with at least one hydraulic consumer and connects the pump in the first control position with this hydraulic consumer, whereas in a second control position the pump via the pressure line with each further proportional spool, while the hydraulic consumer is disconnected from the pump. This is useful in hydraulic controls such as hydraulic work vehicles with hydraulically extendable floor supports to extend and lock the supports in the second control position before further hydraulic consumers are controlled during the control of the floor supports are extended and must not be controlled.
  • the Control pressure connection in the proportional spool is only continuously controlled when the proportional spool is placed in the first control position.
  • the load pressure signal circuit connected via a hydraulic damping device to the pump delivery control.
  • This damping device dampens not only pressure fluctuations in the load pressure signal circuit, but may also prevent or mitigate undesirable lowering of the load pressure signal at the pump delivery control when switching the selector valve between its control positions.
  • the hydraulic damping device includes, for example, two series-connected throttles and two opposing check valves and may be housed in an input block of the hydraulic control.
  • Production technology favorable is connected to the control pressure connection in the selector valve, a first control line to the return, which contains the pressure relief valve, which is acted upon by a pre-pressure adjusting spring. As soon as the response pressure of the pressure limiting valve is reached in this control line via the control pressure connection, this prevents a further increase in the load pressure signal. In this case, the pressure relief valve against the spring from a second, also connected to the control pressure connection control line is opened.
  • the pump is a variable displacement pump with a control input belonging to the delivery control.
  • the variable-displacement pump is adjusted to build up the admission pressure in the pressure line via the control input.
  • Part of the delivery control may also be a pressure compensator circulation circuit to the return.
  • the pump is a fixed displacement pump, the conveyor side, preferably in an input block of the hydraulic control, to be connected to a conveyor-regulating pressure compensator circulation circuit.
  • the load pressure signal circuit is connected to a feed side of the pressure compensator circulation circuit, preferably via a hydraulic damping device arranged in the load pressure signal circuit.
  • control pressure connection could be accommodated in a conventional way in a spool because of the additional control function, but would then because of the additional Control function in an inappropriate extension of the piston valve and the housing result. Therefore, according to a particular important aspect of the invention in the selector valve, the control pressure connection between two axially adjacent Steuer effetsEinstichen in a axially displaceable spool piston housing bore and at least one of a plurality of separated recesses in the spool circumference continuously switchable. The outlines of these recesses, preferably in each case two adjacent recesses, overlap one another in the longitudinal direction of the spool.
  • the depressions are spaced apart from one another transversely to the longitudinal direction and are provided in the first control position within an axial section delimited in the longitudinal direction of the slide piston at least approximately in accordance with the adjustment stroke of the slide piston.
  • This limited axial section is longer than the longitudinal outline of each well.
  • the wells can be placed in the spool circumference so that they do not overlap with all other other control functions associated control channels in the housing bore, but are separated from each other by positive overlaps, so that working pressure can lick neither to the punctures, nor to the return, while the Spool is adjusted.
  • the length of the spool and the housing bore and thus of the housing is not extended by this design of the control pressure connection, but it remains the usual length of a multi-position multiway Wegeschiebers despite the control pressure connection.
  • the wells are blind holes in the spool circumference, which are preferably arranged along an imaginary thread line. This concept is favorable manufacturing technology.
  • the depressions can be equal to each other or different sizes. It is only necessary to ensure that they do not overlap with any working channels in the housing bore when the spool is adjusted.
  • the outlines of the depressions can have any geometric shapes. Instead of blind holes control notches or the like could be formed.
  • each control line recess in the housing bore seen in the longitudinal direction is smaller than the contour of a recess.
  • the pressure limiting valve and / or the shuttle valve are arranged in a housing block of the selector valve. This contributes to the compactness of the hydraulic control, which is created for example in the usual block design.
  • the pressure relief valve and / or the shuttle valve in an attached with a housing block of the selector valve to an input block of the hydraulic control intermediate block.
  • the latter measures result in minimal space in easy to be made connection channels to the pressure relief valve and / or shuttle valve.
  • Fig. 1 illustrates a hydraulic control S, for example, a hydraulic work vehicle such as a mobile concrete pump, a fire engine with aerial ladder, a forest crane or the like.
  • a hydraulic control S for example, a hydraulic work vehicle such as a mobile concrete pump, a fire engine with aerial ladder, a forest crane or the like.
  • the hydraulic consumers 34 are associated with extendable floor supports, for example, while the hydraulic consumers 34 'can be mast or ladder cylinders.
  • Allen hydraulic consumers 34, 34 ' is associated with a common pump 15 which sucks from a reservoir R and in the embodiment in Fig. 1 a variable displacement pump 16 with a control input 17 is.
  • control input 17 which belongs to a delivery control F, for example in an input block of the hydraulic controller S, performs a control line 18 to a hydraulic damping device 19 of a load pressure signal circuit 20, which in the embodiment shown two series-connected chokes 21, 22 and two opposing check valves 23, 24 includes.
  • the pump 15 On the delivery side, the pump 15 is connected to a pump line 25.
  • a return line 26 leads to the reservoir R.
  • FIG Fig. 1 is part of the delivery control F a arranged between the pump line 25 and the return line 26 2/2-way pressure compensator 27 which is pressure-controlled from the pump line 25 in Aufberichtvorides, however, in Zu Kunststofftechnisch via a control spring and z. B. leading to a pressure reducing valve 29, connected to a control pressure supply, not shown, control line for example Druckvorberichtungen of valves in the hydraulic control S.
  • a block with a selector valve W is connected, which is at least switchable between a first control position a and a second control position b (and here in a shut-off zero position), either by a hand lever or by proportional solenoids and Druckvor Kunststoffmaschineieux.
  • the selector valve W is connected via a pressure line 32 to at least one further proportional spool 49, and via a working line 33 to the or the hydraulic consumer 34, and allows a function selection e.g. such that either only the consumers 34 'are controllable and connected to the pump 15, or the pressure line 32 is disconnected and the working line 33 is acted upon.
  • the selector valve W has to prevent the other consumers 34 'are controlled as long as the extendable by the hydraulic consumers 34 floor supports are not properly extended, and also that the floor supports are not retracted, as long as further consumers 34' are controlled.
  • the hydraulic control S is equipped with a pre-pressure circuit Y assigned here to the selector valve W, which builds up the admission pressure in the pressure line 32 before any further proportional control slide 49 is deflected.
  • the selector valve W could be a switchable between the two control positions a and b control spool, but is in the embodiment in Fig. 1 a 4/3-proportional control slide 31 with zero position, in which in a housing bore 1 adjustable spool K a Last réelleabgriff 35 from the working line 33 and a Last réelleabgriff 36 from the pressure line 32 are provided.
  • a of the Last réelleabgriff 36 is connected via a channel 37 in the spool K with a control line 38 which includes a throttle 39 and leads to a control line 40 to a shuttle valve 47 in the load pressure signal circuit 20.
  • the control line 38 is also connected downstream of the throttle 39 with a node 41, from which a control line 42 to a control line groove 12 (based on the 3 and 4 explained) in the housing bore 1 leads.
  • This control line groove 12 is in the first control position a via a control pressure connection V, namely at least one recess 14 in the 3 and 4 , for example, connected to the further control line groove 13 in the housing bore 1, from which a control line 43 leads to a control side of a pressure relief valve 45 of the form pressure circuit Y, and a branching control line 44 to the return line 26.
  • the pressure relief valve 45 is disposed in this control line 44 and is acted upon by a pre-pressure determining spring 46 in the direction of control.
  • the shuttle valve 47 is connected with a lateral connection to the control line 40 and with the second lateral connection to a control line 48 to a load pressure tap of the further proportional control slide 49, while its middle connection is connected to the load pressure signal circuit 20, so that the respective higher load pressure signal, either from the control line 40 or the control line 48, in the load pressure signal circuit 20 to the damping device 19 and the conveyor control F is transmitted.
  • the embodiment of the hydraulic control S in Fig. 2 is different from that of Fig. 1 in that the pump 15 is a constant-displacement pump 16 ', and the pump delivery control F contains the circulation pressure compensator 27 between the pump line 25 and the return line 26.
  • the circulation pressure compensator 27 is on the control side from the pump line 25 réellevorteil, and zufest matter is acted upon by a control spring and from the control line 18, which leads here directly from the hydraulic damping device 19 to the circulation pressure compensator 27.
  • the further construction of the embodiment in Fig. 2 corresponds to the Fig. 1 ,
  • Fig. 1 set the selector valve W in the second control position b, then the pressure line 32 is depressurized and the working line 33 is pressurized in accordance with the load pressure signal, which rests on the load pressure tap 35 and is brought via the control line 40 and the shuttle valve 47 in the load pressure signal circuit 20 and by the hydraulic damping device 19 to the control input 17 of the variable displacement pump 16, the flow rate is adjusted accordingly.
  • the delivery rate is set in the pump line 25 via the pressure compensator 27.
  • the selector valve W is switched to the first control position a, so that the working line 33 is relieved to the return line 26 and the pressure line 32 is pressurized.
  • the load pressure signal in the load pressure signal circuit 20 and through the damping device 19 to the control input 17 is brought to the flow rate, for. the Verstellpumpe 16 auzuregeln accordingly.
  • the delivery rate is so highly regulated that the predetermined form, adjusted at the pressure relief valve 45 by the spring 46, is reached.
  • the control pressure connection V is also continuous at the same time. Even if the further proportional spool 49 is still in the zero position, pressure builds up in the pressure line 32, which is not only controlled via the Last réelleabgriff 36, the channel 37 and the continuous load pressure connection V in the control line 40, but also to the pressure relief valve 45, which limits the load pressure signal in the load pressure signal circuit 20 in such a way that the predetermined admission pressure in the pressure line 32 is established by means of the delivery control F, for example by the variable displacement pump 15.
  • the further consumers 34 are not controlled independently of the load until the load pressure signal in the control line 48 exceeds the load pressure signal in the control line 40 limited by the pressure relief valve 45 and the changeover valve 47 directly from the control line 48 Switches to the load pressure signal circuit 20. Thereafter, the other consumers are controlled 34 'load independent.
  • the function of the form pressure circuit Y in the embodiment of the hydraulic control S in Fig. 2 corresponds largely to the basis of Fig. 1 explained.
  • One difference is that the constant-displacement pump 16 'has constant delivery rate, but the circulation pressure compensator 27 in the second control position b of the selector valve W provides the necessary quantity.
  • the first control position a of the selector valve W is first controlled by the form and only later in accordance with the load pressure signal in the fed from the control line 48 load pressure signal circuit 20.
  • the selector valve W shown in section Fig. 3 is, for example, a way control slide for speed control of a hydraulic consumer, not shown.
  • the selector valve contains in a housing bore 1 a linearly displaceable spool K, which by an operation not shown at least between a first control position a (upper half of Fig. 3 ) and a zero position 0 (lower half) is adjustable.
  • a working line A with its mouth 10 is connected to the housing bore 1, and a pump line 9 (corresponding to the pump line 25 in the Fig. 1 and 2 ) and a return line (corresponding to the return line 26 in the Fig. 1 and 2 ).
  • Fig. 3 In the upper half of Fig. 3 is the spool K at the end of the control position a.
  • the working channel 8 in the spool K connects the pump line P to the working line A.
  • the control line recesses 5, 6 are connected via the bypass channel C.
  • the width of the working channel 8 corresponds to y '.
  • the stroke of the spool K between the zero position 0 (lower half of the figure) and the control position a corresponds to s'.
  • the stroke s ' is a measure Ü, a so-called Abdichtüberdeckung, greater than y'.
  • the length of the bypass channel C is limited to an axial section y (or to an axial section s) of the spool K, where y approximately corresponds to y 'and s'.
  • the bridging channel C connects the control line recesses 5, 6 over the entire stroke of the spool K, within which the recess 8 establishes a flow connection between the pressure line 9 and the working line 10.
  • the Steuer effetseinstiche 5, 6 are connected together until the working channel 8 in the zero position (lower half) arrives.
  • the length of the axial section s, y, over which the bypass channel C extends in the spool K, can be tuned to the operating conditions, for. B. on the stroke of the spool K, via which the control line bites 5, 6, the control lines 12, 13 to be connected to each other.
  • the bridging channel C consists of a plurality of individual, in the circumferential direction of the spool K spaced recesses 14 in the spool circumference, z. B. blind or blind holes.
  • the absolute distance between adjacent recesses 14 corresponds approximately to the Abdichtüberdeckung Ü.
  • the contours of adjacent recesses 14 overlap so far that (see Fig. 4 )
  • Fig. 4 are otherwise the dashed depressions 14 to illustrate the outline overlaps in the sectional plane of the left recess 14 shown in solid lines folded.
  • the axial distance between the mouth 9 and the nearest control line groove 6 is expediently d + Ü. d corresponds to the contour of a recess 14 seen in the longitudinal direction of the spool K. With average spool sizes, this distance can be about 4.5 to 6.0 mm, whereas previously this distance had to be between 8.0 and 10.0 mm for corresponding spool sizes.
  • the Steuer effetseinstich 6 can be moved even closer to the mouth 9, as shown. Although only a small amount of control pressure fluid compared to the amount of the working pressure fluid flows for the control function, the control function of the control pressure medium in the housing bore and in the spool actually needed in addition the same length as the control function for the working pressure medium.
  • the recesses 14 are selectively distributed over the axial section s or Ü (as with 14 'in the lower half of FIG Fig. 4 indicated), but so that between the outlines of two in the longitudinal direction of the spool K successive recesses 14 'as large as possible and the mutual seal between these recesses on the wall of the housing bore. 1 ensuring absolute distances, while they overlap in a projection transverse to the longitudinal direction in the longitudinal direction of the spool K with their outlines. Manufacturing technology, it is expedient to arrange the recesses 14 along an imaginary thread line in the circumference of the spool K. Within the axial section s could be distributed over the circumference of the spool K several similar acting groups then even smaller recesses 14 or 14 'may be provided.
  • each recess 14, 14 ' is at least as large as the intermediate distance x between the control line grooves 5, 6 seen in the longitudinal direction, is preferably as large as x plus the axial widths w of the control line grooves 5, 6 the depressions 14, 14 'even more than two Steuer effetseinstiche be assigned.
  • the recess 8 in the spool K of the mouths 9, 10 is separated.
  • the recesses 14 are moved out of the axial region of the control line grooves 5, 6.
  • the Steuer effetseinstiche 5, 6 are z. B. at the moment separated from each other, in which the outline of the rearmost in the direction of displacement recess 14, 14 'passes over the edge of the control line groove 5.
  • the length of the axial section s, y is chosen so that the control function begins as soon as the working channel recess 8 comes into contact with the openings 9, 10.
  • the control function for the control pressure medium ends as soon as this connection is released.
  • the contours of the recesses 14, 14 'need not be circular. It can, for. B. depending on the processing method in the production of the spool K any outline shape can be selected. Recesses on a peripheral side of the spool K can for example be connected to an inner channel of the spool K and / or through holes with recesses on the other peripheral side of the spool.

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

Claims (13)

  1. Commande hydraulique (S), en particulier pour véhicules hydrauliques de chantier, avec une pompe (15) commune destinée à l'alimentation de plusieurs consommateurs hydrauliques (34, 34'), avec une soupape de sélecteur (W), laquelle peut être commutée de manière sélective entre au moins deux positions de commande (a, b), avec tout au moins une autre soupape à tiroir proportionnelle (49), laquelle est raccordée à une conduite de pression (32) par la soupape de sélecteur (W), avec un circuit du signal de la pression de charge (20), lequel peut être sollicité à partir de capteurs de pression de charge (35, 36) et lequel est raccordé à un système de régulation de la distribution (F) de la pompe (15), avec un système de commutation de la pression d'alimentation (Y), lequel contient une soupape de limitation de la pression (45), et avec au moins un sélecteur de circuit distributeur (47), lequel relie avec le système de régulation de la distribution (F) soit le système de commutation de la pression d'alimentation (Y), soit un capteur du signal de la pression de charge de l'autre soupape de commande proportionnelle (49),
    caractérisée en ce que la soupape de limitation de la pression (45) du système de commutation de la pression d'alimentation (Y) est reliée directement avec un capteur du signal de la pression de charge (36) de la conduite de pression (32) et avec le sélecteur de circuit distributeur (47), par l'intermédiaire d'un raccordement de la pression de commande (V) dans la soupape de sélecteur (W) elle-même, lequel raccordement n'est continu que dans une première position de commande (a) de la soupape de sélecteur (W) ;
    caractérisée en ce qu'un restricteur de la pression de commande (39) est disposé entre le capteur du signal de la pression de charge (36) de la conduite de pression (32) et le sélecteur de circuit distributeur (47), ainsi que le raccordement de la pression de commande (V) ; et
    caractérisée en ce que la soupape de sélecteur (W) est une soupape à tiroir proportionnelle (31), laquelle est intégrée dans le circuit du signal de la pression de charge (20) et laquelle relie, dans la première position de commande (a), la pompe (15) avec tout au moins un consommateur hydraulique (34) qui peut être commandé par la soupape à tiroir proportionnelle (31), tout en séparant simultanément de la pompe (15) la conduite de pression (32) qui mène vers l'autre soupape à tiroir proportionnelle (49), et laquelle soupape de sélecteur (W) sépare, dans une deuxième position de commande (b), le consommateur hydraulique (34) de la pompe (15) et laquelle relie la pompe (15) avec l'autre soupape à tiroir proportionnelle (49) par l'intermédiaire de la conduite de pression (32).
  2. Commande hydraulique selon la revendication 1, caractérisée en ce que la soupape de sélecteur (W) est une soupape de commande à 4/3 voies pour le consommateur hydraulique (34) de tout au moins un support au sol.
  3. Commande hydraulique selon la revendication 1, caractérisée en ce que le circuit du signal de la pression de charge (20) est raccordé au système de régulation de la distribution (F) par l'intermédiaire d'un dispositif d'amortissement (19) hydraulique, de préférence un dispositif d'amortissement, lequel se trouve entre le circuit du signal de la pression de charge (20) et une conduite de commande (18) et lequel contient deux restricteurs (21, 22) installés en série et deux soupapes de retenue (24, 23) montées en parallèle et en sens contraire.
  4. Commande hydraulique selon la revendication 1, caractérisée en ce qu'une première conduite de commande (44), laquelle mène à la conduite de retour (26), est raccordée au raccordement de la pression de commande (V) par la soupape de limitation de la pression (45) qui présente un ressort (46) permettant de régler la pression d'alimentation, et caractérisée en ce qu'une deuxième conduite de commande (43), laquelle mène à un côté ouverture de la soupape de limitation de la pression (45) qui se trouve à l'opposé du ressort (46), est raccordée au raccordement de la pression de commande (V).
  5. Commande hydraulique selon la revendication 1, caractérisée en ce que la pompe (15) est une pompe à débit variable (16) comprenant une entrée de régulation (17), laquelle fait partie du système de régulation de la distribution (F).
  6. Commande hydraulique selon la revendication 1, caractérisée en ce que la pompe (15) est une pompe à cylindrée constante (16'), laquelle est raccordée côté distribution, de préférence dans un bloc d'entrée de la commande hydraulique (S), à un abaque de charge d'une balance de pression (27), lequel fait partie du système de régulation de la distribution (F), et caractérisée en ce qu'une conduite de commande (18) mène à un côté fermeture de l'abaque de charge d'une balance de pression (27) depuis un dispositif d'amortissement (19) hydraulique, lequel est disposé dans un circuit du signal de la pression de charge (20).
  7. Commande hydraulique selon la revendication 1, caractérisée en ce que, dans la soupape de sélecteur (W), le raccordement de la pression de commande (V) peut être commuté de manière continue entre au moins deux gorges de la conduite de commande (12, 13), lesquelles sont contiguës dans le sens axial, dans un perçage de carter (1) contenant un piston à tiroir (K) coulissant dans le sens axial, et tout au moins un parmi plusieurs renfoncements (14, 14') séparés qui sont situés dans la périphérie du piston à tiroir, selon laquelle les contours des renfoncements, de préférence respectivement de deux renfoncements contigus, se chevauchent l'un l'autre dans la direction longitudinale du piston à tiroir (K), mais sont en revanche espacés l'un de l'autre, transversalement par rapport à la direction longitudinale, et les renfoncements sont prévus à l'intérieur d'une section axiale (s) limitée dans le sens longitudinal du piston à tiroir (K), correspondant tout au moins à peu près à la course d'ajustement du piston à tiroir (K), dans la première position de commande (b), laquelle section axiale (s) est plus longue que l'ouverture de contour (d) de chaque renfoncement (14, 14'), vue dans le sens longitudinal.
  8. Commande hydraulique selon la revendication 7, caractérisée en ce que les renfoncements (14, 14') sont des trous borgnes, lesquels sont, de préférence, disposés dans la périphérie du piston à tiroir, le long d'une courbe de variation du filetage mise en place.
  9. Commande hydraulique selon la revendication 7, caractérisée en ce que les renfoncements (14, 14') sont de taille identique ou différente, les uns par rapport aux autres.
  10. Commande hydraulique selon la revendication 7, caractérisée en ce que l'écart entre les gorges de la conduite de commande (12, 13) dans le perçage de carter (1), vu dans le sens longitudinal, est inférieur à l'ouverture de contour (d) d'un renfoncement (14, 14').
  11. Commande hydraulique selon la revendication 7, caractérisée en ce que l'ouverture de chaque gorge de la conduite de commande (12, 13) dans le perçage de carter (1), vue dans le sens longitudinal, est inférieure à l'ouverture de contour (d) d'un renfoncement (14, 14').
  12. Dispositif de commande hydraulique selon tout au moins l'une des revendications précédentes caractérisé en ce que la soupape de limitation de la pression (45) et/ou le sélecteur de circuit distributeur (47) est, respectivement sont disposés dans un bloc carter (11) de la soupape de sélecteur (W).
  13. Commande hydraulique selon tout au moins l'une des revendications 1 à 11, caractérisée en ce que la soupape de limitation de la pression (45) et/ou le sélecteur de circuit distributeur (47) est, respectivement sont disposés dans un bloc carter (11) de la soupape de sélecteur (W), au niveau du bloc intermédiaire, lequel est installé au niveau du bloc d'entrée.
EP15167051.0A 2015-05-11 2015-05-11 Dispositif de commande hydraulique et sélecteur Not-in-force EP3093505B1 (fr)

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DE102020209387B3 (de) * 2020-07-24 2021-07-15 Hawe Hydraulik Se Vorwahlventil, Hydraulikventilverband und Hydrauliksteuervorrichtung
DK4019786T3 (da) 2020-12-28 2024-02-05 Danfoss Power Solutions Zhejiang Co Ltd Flervejsbelastningsventilarbejdssektion
DE102021202207B4 (de) 2021-03-08 2022-12-01 Hawe Hydraulik Se Vorwahlventil, Hydraulikventilverband und Hydrauliksteuervorrichtung

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Publication number Priority date Publication date Assignee Title
DE3710699C1 (de) * 1987-03-31 1988-08-18 Heilmeier & Weinlein Hydraulische Steuervorrichtung fuer eine Verbrauchergruppe
DE9111233U1 (fr) 1991-09-10 1991-10-31 Heilmeier & Weinlein Fabrik Fuer Oel-Hydraulik Gmbh & Co Kg, 8000 Muenchen, De
DE9111569U1 (fr) * 1991-09-17 1991-11-14 Heilmeier & Weinlein Fabrik Fuer Oel-Hydraulik Gmbh & Co Kg, 8000 Muenchen, De
DE102005035981A1 (de) 2005-07-28 2007-02-01 Putzmeister Ag Hydraulische Schaltungsanordnung, insbesondere für den Antrieb von Betonverteilermasten
EP1837529B1 (fr) 2006-03-20 2008-10-22 HAWE Hydraulik GmbH & Co. KG Commande hydraulique
DE102007055377A1 (de) * 2007-11-19 2009-05-20 Robert Bosch Gmbh Hydraulische Steueranordnung und Wegeventilsektion
DE102012220445A1 (de) * 2012-11-09 2014-05-15 Robert Bosch Gmbh Hydraulische Steuereinrichtung für einen Antrieb mit mehreren hydraulischen Aktoren

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Title
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