EP0376023A2 - Soupape électrohydraulique proportionnelle - Google Patents

Soupape électrohydraulique proportionnelle Download PDF

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Publication number
EP0376023A2
EP0376023A2 EP19890122724 EP89122724A EP0376023A2 EP 0376023 A2 EP0376023 A2 EP 0376023A2 EP 19890122724 EP19890122724 EP 19890122724 EP 89122724 A EP89122724 A EP 89122724A EP 0376023 A2 EP0376023 A2 EP 0376023A2
Authority
EP
European Patent Office
Prior art keywords
control
valve
proportional directional
auxiliary
connection
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.)
Granted
Application number
EP19890122724
Other languages
German (de)
English (en)
Other versions
EP0376023A3 (fr
EP0376023B1 (fr
Inventor
Eckard Schuttenberg
Berthold Dipl.-Ing. Pfuhl (Fh)
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 EP0376023A2 publication Critical patent/EP0376023A2/fr
Publication of EP0376023A3 publication Critical patent/EP0376023A3/fr
Application granted granted Critical
Publication of EP0376023B1 publication Critical patent/EP0376023B1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/355—Pilot pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/67—Methods for controlling pilot pressure

Definitions

  • the invention is based on an electrohydraulic proportional directional valve according to the preamble of the main claim.
  • this proportional valve In addition to the four main connections A, B, P, T, this proportional valve also has control connections X and Y for external control oil supply and discharge in the main valve. There are also auxiliary connections C1 and C2 in the main valve, but these are used for the function of the load tap for the pressure compensator.
  • This proportional valving til can therefore not meet any further safety requirements such as those required by professional associations or accident prevention regulations for hydraulic machines and systems in the safety area. Also, in special applications, this proportional valve can be too slow in the event of an emergency stop because the main spool is reset by the springs in the main valve, which can only exert a restoring force corresponding to a few bar pressure and the pressure medium must flow through the small cross-sections of the pilot valve .
  • the electrohydraulic proportional directional control valve according to the invention with the characterizing features of the main claim has the advantage that it can meet diverse security requirements with relatively little effort.
  • the dynamic behavior can also be considerably improved if the resetting of the main control spool is supported hydraulically by the spring forces by an intermediate pressure in the pilot control circuit.
  • electrical position indicators can be arranged on the main control valve as well as on the pilot valve in the case of very high safety requirements.
  • the main control slide can still be equipped with a leakage oil drain if the connected working cylinder is to be prevented from drifting.
  • tapping of the reliefs is incorporated directly in the main control slide, that is to say in an actuator which determines the flow.
  • a design according to claim 12 is also particularly expedient, as a result of which pressure build-up in a control chamber can be prevented particularly effectively. Tapping the relief directly in the control oil supply allows a particularly compact solution. This self-monitoring of the valve also guarantees a high level of safety. Further particularly advantageous configurations result from the remaining claims, the description and the drawing.
  • FIG. 1 shows a first electrohydraulic proportional directional control valve in a simplified representation and partly in longitudinal section
  • FIG. 1a shows the switching symbol of the pilot control stage in FIG. 1
  • FIGS. 2 to 6 different switching valves for use with the first proportional directional control valve according to FIG. 1 for realizing different safety requirements
  • FIG by a part of a second proportional directional control valve with a change in the tapping of the relief in the control circuit compared to FIG. 1 and FIG. 8 a partial section through a third exemplary embodiment.
  • FIG. 1 shows a simplified representation of an electrohydraulic proportional directional valve 10, which is used to control a double-acting working cylinder 11.
  • the proportional directional control valve 10 essentially consists of a hydraulically controlled main control valve 12, an electrically controlled pilot control valve 13 and a switching valve 14 connected to the main control valve 12.
  • Main control valve 12 and attached pilot valve 13 are known per se with regard to their basic structure from the literature reference mentioned at the beginning, to which reference is expressly made.
  • the proportional main control valve 12 is designed as a 4/3-way valve with four controlled main connections A, B, P and T and a main control spool 17 which can be moved continuously in three switching positions.
  • the main spool 17 is in the housing 15 in egg ner slide bore 18 tight and slidably guided.
  • the slide bore 18 penetrates a centrally located inlet chamber 19 which is connected to the main connection P, two adjacent motor chambers 21, 22 which are connected to the main connections A and B and two return chambers 23 and 24 which have a connection to the main connection T. .
  • the main port P is supplied in a manner not shown by a pump with pressure medium, while the main port T is relieved to the tank.
  • the two sides of the double-acting working cylinder 11 are connected to the main connections A and B.
  • the main control slide 17 projects with its front ends 25, 26 into a control chamber 27, 28, each of which receives a spring 29, 31 to form a double-acting resetting device 32 for the main control slide 17.
  • a control chamber 27, 28 By pressurizing a control chamber 27, 28 while simultaneously relieving pressure on the other control chamber 28, 27, the main control slide 17 can be deflected in both directions from its drawn central position against the force of the resetting device 32.
  • the pilot valve 13 is designed as a 4/4-way valve, the control functions of which can be found in the associated, simplified illustration according to FIG. 1a.
  • the pilot valve 13 has four controlled connections A, B, P, T and a pilot spool 33, which can be controlled by the single proportional magnet 16 against the force of a spring 34 in four switching positions 35, 36, 37 and 38.
  • the switch position 37 is designed as a neutral control position in which all four connections A, B, P, T of the pilot valve 13 are closed. From this neutral control position, the pilot spool 33 can be transferred into the two working positions 38 and 36, respectively, by appropriately actuating the proportional magnet 16, in which one of the connections A, B is alternately connected to the connection P, while the other connection B, A to Tank connection T is relieved.
  • the proportional magnet 16 is de-energized, the spring 34 presses the pilot spool 33 into its safety position 35, in which the two connections A, B are connected to one another and to the tank connection T and the P connection is shut off.
  • the pilot valve 13 is attached to the main control valve 12 in such a way that its connection P is connected to a control connection X of the main control valve 12 via a supply channel 39 in the housing 15. Furthermore, a relief channel 41 in the housing 15 leads from the connection T of the pilot valve 13 to a control connection Y of the main control valve 12. These two control connections X, Y are used for external control oil supply and discharge and thus form parts of a control circuit together with the channels 39, 41 42.
  • the supply duct 39 and the relief duct 41 cannot be influenced hydraulically by the main control slide 17 itself.
  • the connection B of the pilot valve 13 is connected via a first control channel 43 to the A-side control chamber 27 in the main control valve 12, while in a corresponding manner the connection A has a connection to the B-side control chamber 28 via a second control channel 44.
  • the slide bore 18 receiving the main control slide 17 is expanded in the region between the first return chamber 23 and the associated control chamber 27 to form a first annular chamber 45 which is connected to an auxiliary connection C1 arranged in the housing 15.
  • the main control slide 17 has in the area of this first annular chamber 45 a first annular groove 46 which, on the one hand, always has a connection with the first annular chamber 45 in the central position of the main control slide 17 and, on the other hand, is continuously connected to the A- via a longitudinal groove 47 on the outside of the slide end 25. side control room 27 is connected.
  • the slide bore 18 penetrates on the opposite valve side a second annular chamber 48 which has a connection to an auxiliary connection C2 and which has a corresponding second annular groove 49 in the main control slide 17 and an associated second longitudinal groove 51 with the B-side Control room 28 has connection.
  • the main control slide 17 has a leak oil drain 52 which is not of interest in the present context, in order to prevent undesired drifting of the working cylinder 11.
  • the two auxiliary connections C1, C2 are each connected via a line 53, 54 to the connections A, B of the switching valve 14, which is designed as a simple, spring-centered, electromagnetically actuated 4/3-way valve.
  • the switching valve 14 has a central, spring-centered zero position 55, in which it relieves both auxiliary connections C1, C2 to the tank connection T, while the connection P is hydraulically blocked.
  • a left switch position 56 all connections A, B, P, T are blocked, while in a right switch position 57, connection B to the tank is relieved and connections A and P are blocked.
  • the mode of operation of the electro-hydraulic proportional directional control valve 10 to meet special safety requirements is described as follows, the basic function of the two-stage proportional valve being assumed to be known, according to which the control oil supplied to the control connection X from the pilot valve 13, depending on the control position of the pilot valve 33, builds up pressure in the control spaces 27, 28 causes, while at the same time the other control chamber 28, 27 is relieved in order to deflect the main control spool 17 proportionally to both sides from the center position shown.
  • the control spaces 27, 28 of the main control spool 17 are connected to the auxiliary connections C1 and C2, which in turn are connected to each other via the longitudinal grooves 47, 51, the annular grooves 46, 49 and the annular chambers 45, 48 the switching valve 14 are connected.
  • the switching valve 14 can now un Different security requirements can be realized on the main control valve 12, as is often required in systems and machines with protective devices.
  • One of these requirements can e.g. be that, when the protective grille is open, the working cylinder 11 must be prevented from making an unauthorized closing movement, i.e. the main control slide 17 must not reach its flow direction P-A.
  • This requirement is met with the aid of the zero position 55 of the switching valve 14, since in this spring-centered neutral position both auxiliary connections C1, C2 to the tank are relieved and deflection of the main control spool 17 is therefore not possible even with a regulating pilot valve 13.
  • This can already be achieved with a relatively small-sized switching valve 14, which only has to have the same nominal flow rate as the pilot valve 13, so that the pressure medium possibly controlled by the pilot valve 13 into a control chamber can also be safely discharged to the tank, so that no disturbing pressure build-up takes place.
  • the switching valve 14 is brought into its left switching position 56, in which it shuts off both auxiliary connections C1, C2.
  • FIGS. 2 to 6 show different switching valves which can be used instead of the switching valve 14 in the proportional directional control valve 10 according to FIG. 1. These switching valves differ as follows, the spring-centered zero position 55 and the left (56) and right switching position 57 always being identified by the same reference numerals as in the switching valve 14.
  • FIG. 2 shows a switching valve 61 in which the spring-centered zero position 55 is designed so that normal control can be controlled with the proportional directional control valve 10. While in the right switching position 57 the auxiliary connection C2 is relieved, in the left switching position 56 the auxiliary connection C1 is relieved to the tank, so that in these switching positions 56, 57 the main control slide 17 can only be deflected in one direction and thus depending on the pin assignment the connections PA or PB are monitored.
  • FIG. 3 shows a third switching valve 62, which differs from the first switching valve 14 only in that, in the zero position 55, the two auxiliary connections C1 and C2 are connected to one another, while the tank connection T is blocked. This promotes rapid pressure equalization, especially if the switching valve has larger cross sections than the pilot valve 13.
  • FIG. 4 shows a fourth switching valve 63, which differs from the first switching valve 14 only in that, in the right switching position 57, the auxiliary connection C1 assigned to the A side of the tank is relieved.
  • FIG. 5 shows a fifth switching valve 64, which is designed as a 4/2 solenoid valve and only has the positions 55, 57, in which it alternately relieves one of the connections A, B to the tank T.
  • the fifth switching valve 64 it is achieved that the main control slide 17 can only ever be deflected in one direction. If the switching valve 64 sticks, a change of direction cannot be carried out. This means that the valve is self-monitoring.
  • FIG. 6 shows a sixth switching valve 65, which is designed as a spring-loaded 2/2 solenoid valve and which only controls an auxiliary connection C2, which can also be assigned C1 if required.
  • FIG. 7 shows a longitudinal section through part of a second proportional directional control valve 70, which works with other control means to avoid pressure build-up in a control room.
  • the second proportional directional control valve 70 differs from the first proportional directional control valve 10 as follows, the same reference numerals being used for the same components.
  • the supply channel 39 starting from the control connection X is guided to the pilot control valve 13 in a manner which can be influenced by the main control slide 17.
  • the supply channel 39 runs through an annular chamber 71 which is formed in the housing 15 between the first annular chamber 45 and the left return chamber 23.
  • the main control slide 17 has in the area of this annular chamber 71 an annular groove 72 which forms an auxiliary control edge 73.
  • This auxiliary control edge 73 has a positive overlap 74 with respect to the first annular chamber 45, which is smaller than the positive overlap with which the main control slide 17 is equipped between the main connections P and A.
  • a hydraulic cross-connection as in FIG. 1 is omitted between the left control chamber 27 and the first annular chamber 45.
  • the mode of operation of the second proportional directional control valve 70 with regard to its safety function is explained as follows: It is assumed that in the event of an unwanted deflection of the main control spool 17 from its spring-centered center position to the left into a working position, the switching valve 65 connected to the line 53 assumes its zero position, whereby it relieves the auxiliary connection C1 to the tank.
  • the main control spool 17 begins to move to the left, its auxiliary control edge 73 opens a connection from the control port X to the auxiliary port C1, so that control oil supplied in the control port X is no longer led from the regulating pilot valve 13 into the control chamber 28, but rather via the annular groove 72 to the auxiliary port C1 and continues to the tank.
  • the main control slide 17 thus relieves itself, as a result of which no pressure can be built up in the pilot valve 13. An unwanted deflection of the main control slide 17 to the left is therefore not possible.
  • the positive overlaps 74 on the main control slide 17 are matched to one another in such a way that the connection from the main connection P to A is not opened.
  • FIG. 8 shows a longitudinal section through part of a third proportional directional control valve 80, which differs from the second proportional directional control valve 70 as follows, the same reference numerals being used for the same components.
  • a second auxiliary control edge 82 is formed via an additional, second annular groove 81, which has a positive overlap 83 with respect to the first annular chamber 45.
  • the two annular grooves 72, 81 are connected to one another via transverse bores 84 in the main control slide 17.
  • pilot valve with a single proportional magnet
  • a pilot stage can also be used, which operates with two proportional magnets.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
EP89122724A 1988-12-30 1989-12-09 Soupape électrohydraulique proportionnelle Expired - Lifetime EP0376023B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3844336 1988-12-30
DE3844336A DE3844336A1 (de) 1988-12-30 1988-12-30 Elektrohydraulisches porportionalwegeventil

Publications (3)

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EP0376023A2 true EP0376023A2 (fr) 1990-07-04
EP0376023A3 EP0376023A3 (fr) 1991-04-17
EP0376023B1 EP0376023B1 (fr) 1994-03-09

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EP89122724A Expired - Lifetime EP0376023B1 (fr) 1988-12-30 1989-12-09 Soupape électrohydraulique proportionnelle

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EP (1) EP0376023B1 (fr)
DE (2) DE3844336A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0471884A1 (fr) * 1990-08-24 1992-02-26 MOOG GmbH Servodistributeur electrohydraulique
EP0718504A2 (fr) * 1994-12-23 1996-06-26 Robert Bosch Gmbh Système de commande hydraulique mono-bloc

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023200319A1 (de) 2023-01-17 2024-07-18 Robert Bosch Gesellschaft mit beschränkter Haftung Lüfterantriebsvorrichtung mit Proportionalventil

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2436900A1 (fr) * 1978-09-20 1980-04-18 Bosch Gmbh Robert Soupape de distribution electrohydraulique

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2436900A1 (fr) * 1978-09-20 1980-04-18 Bosch Gmbh Robert Soupape de distribution electrohydraulique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Bosch Hydraulik, Proportionalwegeventile, Hydraulik in Theorie un Praxis, 1983, Robert Bosch GmbH, Geschäftsbereich K6, Hydraulik *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0471884A1 (fr) * 1990-08-24 1992-02-26 MOOG GmbH Servodistributeur electrohydraulique
EP0718504A2 (fr) * 1994-12-23 1996-06-26 Robert Bosch Gmbh Système de commande hydraulique mono-bloc
EP0718504A3 (fr) * 1994-12-23 1997-01-22 Bosch Gmbh Robert Système de commande hydraulique mono-bloc

Also Published As

Publication number Publication date
DE3844336A1 (de) 1990-07-05
DE58907181D1 (de) 1994-04-14
EP0376023A3 (fr) 1991-04-17
EP0376023B1 (fr) 1994-03-09

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