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EP0388635B1 - Dispositif de commande électrohydraulique - Google Patents

Dispositif de commande électrohydraulique Download PDF

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Publication number
EP0388635B1
EP0388635B1 EP90102933A EP90102933A EP0388635B1 EP 0388635 B1 EP0388635 B1 EP 0388635B1 EP 90102933 A EP90102933 A EP 90102933A EP 90102933 A EP90102933 A EP 90102933A EP 0388635 B1 EP0388635 B1 EP 0388635B1
Authority
EP
European Patent Office
Prior art keywords
control
piston
setting
valve
setting device
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
EP90102933A
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German (de)
English (en)
Other versions
EP0388635A1 (fr
Inventor
Paul Dipl.-Ing. Baier (Fh)
Eckard Schuttenberg
Walter Gerschwitz
Wolfgang Dipl.-Ing. Kötter
Reiner Dipl.-Ing. Kunz (Fh)
Klaus-Jürgen Dipl.-Ing. Geissler (FH)
Horst Holzweissig
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0388635A1 publication Critical patent/EP0388635A1/fr
Application granted granted Critical
Publication of EP0388635B1 publication Critical patent/EP0388635B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves

Definitions

  • the invention is based on an electrohydraulic actuating device according to the type of the main claim.
  • Such an electrohydraulic actuating device is already known from DE-A-3234 231, which works with a position control by force comparison for precise actuation of the control slide of a directional valve.
  • the actuator works with a differential piston, the two ends of which are controlled by two 3-way control valves.
  • a disadvantage of this double-acting actuator is that the mechanical components used for the return, such as measuring springs, control valves and their associated magnet actuation, are arranged in the longitudinal direction of the control slide of the directional control valve, so that there is a large axial overall length.
  • the way of tapping off the spool of the directional control valve is unfavorable and costly via two inner cones located in the piston, a ring of balls fixed to the housing and a component having an outer cone.
  • This design makes it very difficult to adjust the control device relative to the directional valve.
  • the measuring springs arranged inside the actuating unit cannot operate under operating conditions can be set.
  • the actuating device works with a differential piston which is acted upon on both sides in a deflection direction, which not only leads to a higher control oil consumption, but also to a more critical failure behavior of the device.
  • an electrohydraulic actuating device for the spool of a directional control valve in which the actuating piston has pressure surfaces of equal size and an oblique cam surface on a cone, which is used for position feedback.
  • the proportional control valve that controls the control piston is arranged here perpendicular to the longitudinal axis of the piston valve in the directional control valve, which makes adjustment easier.
  • This adjusting device has only a single measuring spring and a single cam surface, so that the force comparison for both directions takes place with the same measuring spring. This adjusting device is therefore not suitable for different strokes in both directions, where, in addition to the zero point, an operating point must be set after a certain stroke.
  • this control device works with a complex 4/3 proportional directional control valve, which is connected to a hydraulic full bridge and thus always controls a differential pressure on the control piston. Switching as a full bridge results in greater hysteresis and thus lower load rigidity. In addition, the position is returned by means of a complex slide sleeve.
  • the bridge circuit leads to a relatively high control oil consumption; Furthermore, the control valve must be energized to control the spring-centered central position of the spool. If the directional control valve is actuated via the additional, manual actuating device, the actuating device controls it; this leads to high actuation forces during manual actuation.
  • the electro-hydraulic actuating device according to the invention with the characterizing features of the main claim has the advantage that it enables a simple and inexpensive construction, which is also characterized by safe failure behavior and easy adjustment during operation. Different measuring springs can be used for both directions of operation, which can be individually adjusted.
  • the use of a pressure-balanced actuating piston and its control in a pressure build-up system ensure that the actuating device fails reliably. Both the adjustment of the adjusting device relative to the directional control valve and the setting of any working points can be carried out easily and inexpensively.
  • FIG. 1 An embodiment of the invention is shown in the drawing and explained in more detail in the following description.
  • the single figure shows a longitudinal section through an electrohydraulic actuating device in a simplified representation.
  • the figure shows a longitudinal section through an electrohydraulic actuating device 10, which is attached to the end of a directional control valve 11 and by means of which the longitudinally movable piston valve 12 is remotely adjustable.
  • the actuating device 10 has an actuating housing 13 which has a tubular housing part 15 starting from a flange 14.
  • This tubular housing part 15 accommodates an actuating piston 17 in a longitudinal bore 16 as a displaceable, piston-like part.
  • the tight and slidably guided control piston 17 divides the longitudinal bore 16 into a first control chamber 18 facing the directional control valve 11 and into an outer, second control chamber 19 which is further sealed by an outwardly projecting piston rod 21.
  • the piston rod 21 is also guided in the tubular housing part 15 and has an internal hexagon 22 at its outer, front end as a key surface.
  • a protective hood 23 plugged onto the housing part 15 encloses the protruding end of the piston rod 21.
  • the actuating piston 17 has a first, frustoconical cone 24, on which a first cam surface 25 extending obliquely to the longitudinal axis of the actuating piston 17 is formed.
  • the actuating piston has a second cone 26, on which the obliquely extending, second cam surface 27 is formed.
  • the actuating piston 17 with its two cone sections 24, 26 and with its piston rod 21 is guided coaxially with the piston valve 12 of the directional control valve 11 and coupled to the piston valve 12 by a threaded bolt 28.
  • the threaded bolt 28 is screwed on the one hand with its threaded end 29 directly into the piston slide 12, while at the other end 31 it is coupled to the actuating piston 17 by a positive, non-rotating connection, which can be designed in the form of a T-slot attachment 32 .
  • a positive, non-rotating connection which can be designed in the form of a T-slot attachment 32 .
  • the end wall 37 of the directional control valve 11 and, on the other hand, a shoulder 38 in the longitudinal bore 16 serve as housing-fixed stops for the two spring plates 34, 35.
  • the actuating housing 13 has two funnel-shaped housing projections 39, 41 which are placed next to one another, parallel to one another and perpendicular to the longitudinal axis of the actuating piston 17, on the tubular housing part 15, the central axes of which lie in the region of the cones 24, 26.
  • Each housing extension 39, 41 accommodates a first (44) or second control valve 45 in its multiple recesses 42 and 43, which are identical to one another. In the following, therefore, only the first control valve 44 is described, the same reference numerals being used for the identical second control valve 45 for the same components, but with the index '.
  • the first control valve 44 consists of a valve insert 46 and an associated feedback device 47.
  • the valve insert 46 has a valve housing 48 which is offset several times in accordance with the recess 42 and which can be screwed into the first housing extension 39 with a threaded connector 49 and thereby an internal spring chamber 51, one centrally located drain chamber 52 and an external control chamber 53 tightly separates from each other.
  • the spring chamber 51 is connected via an inlet channel 54 to an inlet connection 55 in the flange 14, which is supplied with control pressure medium from the directional control valve 11.
  • An outlet space 52 is connected via an outlet channel 56 to an outlet connection 57, which is likewise relieved of pressure via the directional valve 11 for the return.
  • the control chamber 53 has a connection to the first control chamber 18 via a control channel 58 which is offset from the plane of the drawing, this control channel 58 being shown in simplified form.
  • the valve housing 48 receives in its slide bore as a control slide a longitudinally movable control slide 59, which connects the spring chamber 51 to an armature chamber 62 via its longitudinal channel 61.
  • a pressure control edge 63 on the inlet side is formed on the hollow slide 59 by a transverse bore penetrating the longitudinal channel 61 and a discharge control edge 64 is formed by an external screwing in.
  • the armature chamber 62 is closed pressure-tight to the outside and receives an armature 65 which can be actuated by a magnet 66 placed on the valve housing 48.
  • the magnet 66 is a proportional magnet which exerts a force on the armature 65 and thus on the hollow slide 59 in accordance with the size of its electrical input signal.
  • the hollow slide 59 is supported with its end projecting into the spring chamber 51 on a measuring spring 67, which acts with its other end on a measuring pin 68 which is guided tightly and slidably in a bottom part 69 of the first housing attachment 39.
  • the measuring pin 68 thus seals the spring chamber 51 against the first control chamber 18 and probes with its spherical end in the first control chamber 18, the oblique, first cam surface 25.
  • the valve insert 46 and the feedback device 47 are thus arranged coaxially to one another and are perpendicular to the longitudinal axis of the actuating piston 17.
  • the identical, second control valve 45 is connected in parallel to the first control valve 44 to the inlet channel 54 and the outlet channel 56, while its control chamber 53 ' the corresponding control channel 58 'is connected to the second control chamber 19.
  • the adjusting piston 17 has between its actual piston and the two cones 24, 26 each a conical transition section 72, 73, which are particularly expediently designed as cones and which, together with a chamfer 74 facing the piston rod 21, serve to ensure that the adjusting piston 17th without dismantling the control valves 44, 45 and their measuring pins 68, 68 'can be removed and installed in the control housing 13; this design also favors the use of measuring pins 68, 68 'with a relatively small diameter.
  • the two magnets 66, 66 'on the control valves 44, 45 are de-energized.
  • the control pressure provided at the inlet connection 55 which moves in the low pressure range and can reach an order of magnitude of approximately 15-20 bar, reaches the spring chambers 51, 51 'via the inlet channel 54 and in each case via the longitudinal channels 61, 61' in the hollow slide 59 , 59 'in the anchor rooms 62, 62'.
  • the hollow slide 59, 59 ' are held by current-free magnets by their measuring springs 67 in the drawn starting positions, so that the control pressure at the pressure-balanced hollow slide 59, 59' only reaches up to the closed pressure control edges 63, 63 '.
  • the control pressure at the pressure-balanced hollow slide 59, 59' only reaches up to the closed pressure control edges 63, 63 '.
  • the control channels 58, 58 ' the control rooms 53, 53' and the open drainage control edges 64, 64 'to the drainage chambers 52, 52' and further to the drain connection 57.
  • no pressure force acts on the actuating piston 17.
  • the adjusting piston 17 and thus also the piston slide 12 coupled via the threaded bolt 28 are centered by the double-acting resetting device 33 in the neutral position shown.
  • control oil displaced from the second control chamber 19 flows through the control channel 58 ', the control chamber 53', the open drain control edge 64 'and an outer annular groove on the hollow slide valve 59' into the drain chamber 52 'and further via the drain channel 56 to the drain connection 57
  • the measuring spring 67 is tensioned more strongly by the measuring pin 68 running onto the first, inclined cam surface 25.
  • the actuating piston 17 now moves to the right until the force of the measuring spring 67 has become so great that it closes the pressure control edge 63 again and the drain control edge 64 does not yet open.
  • the hollow slide 59 is then in a force equilibrium in which the magnetic force exerted by the armature 65 on the hollow slide 59 is the same as the force of the counteracting measuring spring 67.
  • the actuating piston 17 has then reached a corresponding stroke to the right, the size of which is proportional to the current value entered at magnet 66.
  • the control piston 17 and thus the piston slide 12 can be deflected in a corresponding manner from the neutral position shown to the left, for which purpose the magnet 66 'is correspondingly energized at the second control valve 45 and thus a pressure build-up takes place in the second control chamber 19, which follows the control piston 17 left deflects.
  • the size of the stroke is proportional to the size of the electrical signal input to the magnet 66 '.
  • the electrohydraulic actuating device 10 thus works in both directions of movement with a position control by comparing the forces, the same effective pressure areas being formed on the actuating piston 17 in both control chambers 18, 19 and the actuating piston 17 being controlled via a pressure build-up system, so that the actuating device 10 assures safe failure behavior results.
  • the piston slide 12 In the neutral position, the piston slide 12 is centered by the resetting device 33, the spring plates 34, 35 of which abut the end wall 37 or the shoulder 38, while at the same time forming stops for the piston slide 12 and the actuating piston 17.
  • the length tolerances caused by the reset device 33 can lead to a longitudinal play of the spool 12, which can, however, be compensated for by means of the threaded bolt 28 which can be screwed into the spool 12.
  • the adjusting piston 17, and thus also the threaded bolt 28 coupled with it in a rotationally fixed manner is screwed into the piston slide 12 until the minimal play is achieved. This adjustment process can be carried out very easily from the outside and under operating conditions.
  • the various operating points can be set in an advantageous manner on the electrohydraulic actuating device 10.
  • An operating point is represented by the stroke of the piston slide 12 with a specific electrical control signal on a magnet. These operating points are set by tensioning the measuring springs 67, 67 ', the control valves 44, 45 being screwed correspondingly deep into their housing extensions 39, 41.
  • two working points are set on the actuating device 10, one working point for each direction of movement from the neutral position.
  • the directional control valve 11 is a 3-position valve, these operating points can be set identically for both directions of actuation. However, if there is a 4-position valve, a different operating point is set for each direction of actuation.
  • an actuation direction has only one switching position, the operating point can be set with a relatively small stroke.
  • the actuating device 10 is under operating conditions and is supplied with control oil via the directional valve 11.
  • the actuating direction of the actuating piston 17 to the right is set by screwing in the left control valve 44, while the actuating direction to the left is done by screwing in the second control valve 45.
  • the magnet 66 is subjected to a predetermined electric current depending on the stroke to be set and then the control valve 44 is screwed from the outside into the housing extension 39 until the piston slide 12 has reached the desired stroke.
  • the first valve insert 46 has a key surface 71 suitable for this.
  • the actuating device 10 thus works advantageously with two different or the same measuring springs 67, 67 'for both directions of actuation, which can be adjusted individually. These measuring springs can be adjusted from the outside under operating conditions, any working points being adjustable.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (14)

1. Dispositif de commande électro-hydraulique (10) pour actionner une pièce (12, 17) du type piston pouvant coulisser dans un alésage longitudinal (16), en particulier du tiroir de piston d'un distributeur (11), dans lequel sur les deux faces frontales d'un piston de commande (17) entraînant la pièce (12, 17) on dispose chaque fois une chambre de commande (18, 19), chacune de ces chambres de commande pouvant être soumise à l'action d'un agent sous pression ou mise en décharge par déplacement de la pièce (12, 17), centrée par un ressort de rappel (36) dans une position de base, dans les deux sens au moyen d'une vanne de régulation (44, 45) actionnée électromagnétiquement, chaque vanne de régulation présentant un tiroir de commande (59, 59′) sur lequel on peut pratiquer une comparaison entre l'amplitude du signal d'entrée électrique et la force d'un ressort taré (67, 67′), qui est couplé dans un guidage de retour (47) mécanique avec la pièce (12, 17) du type piston, grâce à quoi la partie servant au retour en position dans chaque sens d'actionnement présente une surface de came oblique (25, 27), dispositif de commande électrohydraulique, caractérisé en ce que les deux surfaces de came (25, 27) sont disposées, à une certaine distance l'une de l'autre, sur la pièce (12, 17) de type piston et le piston de commande (17) séparant entre elles les chambres de commande (18, 19) l'une de l'autre, piston qui présente des surfaces de compression de même grandeur dans les chambres de commande (18, 19), et en ce que les deux vannes de régulation (44, 45) sont disposées perpendiculairement à l'axe longitudinal de la partie (12, 17) de type piston et chaque vanne de régulation (44, 45) est en liaison opérationnelle avec une surface de came seulement (25, 27).
2. Dispositif de commande selon la revendication 1, caractérisé en ce que chaque vanne de régulation (44, 45) présente un insert de vanne (46, 46′), qui peut être monté de l'extérieur de façon réglable dans un boîtier de commande (13).
3. Dispositif de commande selon la revendication 2, caractérisé en ce que chaque insert de vanne (46, 46′) présente un tiroir de commande (59, 59′), qui est en liaison opérationnelle par l'intermédiaire des ressorts tarés (67, 67′) avec une tige de mesurage (68, 68′), de telle sorte que chaque tige de mesurage (68, 68′) est associée à une surface de came (25, 27), se trouve en position coaxiale par rapport au ressort taré (67, 67′) et par rapport au tiroir de commande (59, 59′) et est disposé perpendiculairement à l'axe longitudinal de la partie de type piston (12, 17).
4. Dispositif de commande selon la revendication 2 ou 3, caractérisé en ce que sur chaque insert de vanne (46, 46′) est disposé un électro-aimant (66, 66′) agissant de façon proportionnelle, dont l'armature (65, 65′) est couplée au tiroir de commande (59, 59′).
5. Dispositif de commande selon une ou plusieurs des revendications 1 à 4, caractérisé en ce que chaque vanne de régulation (44, 45) est formée comme une vanne 3 voies, qui au choix obture une chambre de commande (18, 19), la relie avec le raccord d'admission (35) de pression de commande ou un raccord de décharge (57).
6. Dispositif selon la revendication 5, caractérisé en ce que chaque vanne de régulation (44, 45) présente comme tiroir de commande un tiroir creux (59, 59′) dont les deux extrémités frontales sont soumises à l'action d'un agent sous pression par un raccord (55) d'admission de pression de commande et qui présente une collerette située extérieurement sur laquelle sont disposées l'arête de commande de pression (63) et l'arête de commande de décharge (64) du côté retour.
7. Dispositif de commande selon une ou plusieurs des revendications 1 à 6, caractérisé en ce que la pièce (17, 21, 28) coulissante, présentant le piston de commande (17), présente au moins une surface (22), pour être manoeuvrée par une clé, à une extrémité (21) sortant de façon étanche d'une chambre de commande (19) et à son extrémité opposée (24) est reliée, dans pouvoir tourner, à un téton fileté (28).
8. Dispositif de commande selon une ou plusieurs des revendications 3 à 7, caractérisé en ce que dans le boîtier de commande (13) la pièce (12, 17) de type piston est guidé dans un alésage longitudinal (16) en particulier du type trou borgne et le boîtier de commande (13) présente deux évidements (42, 43) disposés perpendiculairement à l'alésage longitudinal (16), recevant les inserts de vannes (46, 46′), évidements dans le fond desquels (69, 69′) les tiges de mesurage (68, 68′) sont guidées de façon étanche et en glissant, tiges qui font saillie dans les chambres de commande (18, 19) correspondantes.
9. Dispositif de commande selon la revendication 8, caractérisé en ce que le boîtier de commande (13) présente un flasque (14) pour un montage frontal sur un distributeur (11) et le boîtier de commande (13) reçoit un dispositif de rappel à double effet dans la zone comprise entre le flasque (14) et la première surface de came (25).
10. Dispositif de commande selon l'une des revendications 7 à 9, caractérisé en ce que le téton fileté (28) est couplé par l'intermédiaire d'une liaison (32) à engagement positif ne permettant aucune rotation, de façon desserrable avec le piston de commande (17) et est en particulier disposé dans la zone du dispositif de rappel (32).
11. Dispositif de commande selon une ou plusieurs des revendications 1 à 10, caractérisé en ce que les surfaces de cames (25, 27) sont formées respectivement sur un cône en forme de tronc de cône (24, 26).
12. Dispositif de commande selon une ou plusieurs des revendications 8 à 11, caractérisé en ce que la pièce (12, 17) montée de façon à pouvoir coulisser est guidée par son piston de commande (17) et son extrémité (21) en forme de tige de piston faisant saillie, dans le boîtier de commande (13) de façon mobile longitudinalement et étanche.
13. Dispositif selon la revendication 5 ou 6, caractérisé en ce que chaque vanne de régulation (44, 45) présente un tiroir de commande (59, 59′) à pression compensée.
14. Dispositif de commande selon une ou plusieurs des revendications 1 à 13, caractérisé en ce que des deux côtés du piston de commande (17) sont formées des sections de transition (72, 73) en particulier des cônes, évitant des variations brusques du diamètre extérieur.
EP90102933A 1989-03-22 1990-02-15 Dispositif de commande électrohydraulique Expired - Lifetime EP0388635B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3909433 1989-03-22
DE3909433A DE3909433A1 (de) 1989-03-22 1989-03-22 Elektrohydraulische stelleinrichtung

Publications (2)

Publication Number Publication Date
EP0388635A1 EP0388635A1 (fr) 1990-09-26
EP0388635B1 true EP0388635B1 (fr) 1992-06-03

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EP90102933A Expired - Lifetime EP0388635B1 (fr) 1989-03-22 1990-02-15 Dispositif de commande électrohydraulique

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DE (2) DE3909433A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19846418A1 (de) * 1998-10-08 2000-04-13 Mannesmann Rexroth Ag Hydraulikventil mit Sensor
US6637461B2 (en) * 2002-03-08 2003-10-28 Husco International, Inc. Electrically operated hydraulic actuator with force feedback position sensing
DE10330738B4 (de) * 2003-07-07 2007-03-22 Alpha Fluid Hydrauliksysteme Müller GmbH Elektrohydraulische Stelleinrichtung
CN108749803B (zh) * 2018-06-04 2024-02-13 中车长江车辆有限公司 用于停车制动的双向操作阀、制动装置及铁路货车
CN119467782B (zh) * 2025-01-07 2025-03-21 雅安宇焜芯材材料科技有限公司 一种分流管件及氮化镓生产废气排气装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2635472A1 (de) * 1975-08-06 1977-02-17 Applied Power Inc Servoeinrichtung und dadurch betaetigbares durchflussregulierventil

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Publication number Priority date Publication date Assignee Title
US4212323A (en) * 1977-08-18 1980-07-15 Tomco, Inc. Power assist proportional remote controller
DE3234231A1 (de) * 1982-04-21 1984-03-15 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum betaetigen eines schiebekoerpers, insbesondere des kolbenschiebers eines wegeventils
DE3214845A1 (de) * 1982-04-21 1983-11-03 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum betaetigen eines schiebekoerpers, insbesondere des kolbenschiebers eines wegeventils
DE3303697A1 (de) * 1982-04-21 1984-08-09 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum betaetigen eines schiebekoerpers, insbesondere des kolbenschiebers eines wegeventils

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2635472A1 (de) * 1975-08-06 1977-02-17 Applied Power Inc Servoeinrichtung und dadurch betaetigbares durchflussregulierventil

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Publication number Publication date
DE59000135D1 (de) 1992-07-09
EP0388635A1 (fr) 1990-09-26
DE3909433A1 (de) 1990-09-27

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