EP0236742B1 - Servo valve for pneumatic-pressure control - Google Patents

Servo valve for pneumatic-pressure control Download PDF

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Publication number
EP0236742B1
EP0236742B1 EP87101581A EP87101581A EP0236742B1 EP 0236742 B1 EP0236742 B1 EP 0236742B1 EP 87101581 A EP87101581 A EP 87101581A EP 87101581 A EP87101581 A EP 87101581A EP 0236742 B1 EP0236742 B1 EP 0236742B1
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EP
European Patent Office
Prior art keywords
valves
control
piston
valve
chamber
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Expired
Application number
EP87101581A
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German (de)
French (fr)
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EP0236742A1 (en
Inventor
Werner Stumpe
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Robert Bosch GmbH
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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/565—Control of a downstream 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
    • F15B2211/635—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member

Definitions

  • the invention relates to a relay valve device according to the preamble of the main claim.
  • a relay valve device is known (US Patent 36 43 682).
  • This known relay valve device is used for the electrical remote adjustment of pneumatic pressures. Pilot solenoid valves are provided which are designed as slide valves; they cannot be influenced by the modulated pressure. As a result, the known device is not sensitive.
  • the invention has for its object to provide a sensitive control for a relay piston.
  • An additional pressure influencing of the pilot control solenoid valves is intended to ensure a wide range of grading options for the relay piston switching pressure.
  • FIG. 1 shows a first embodiment of the relay valve device and FIG. 2 shows a modification of the type according to FIG. 1.
  • a relay valve device is shown as valve block 1 with four 3/3-way solenoid valves 2, 3, 4 and 5 arranged next to one another, the magnets 6, 7, 8 and 9 of which are connected via lines to control electronics 10, into which a setpoint value is connected via a Encoder 11, e.g. B. can be entered via a brake pedal.
  • a Encoder 11 e.g. B. can be entered via a brake pedal.
  • the magnets 6, 7, 8 and 9 have armatures 12, 13, 14 and 15 and are designed as control magnets with control pistons 28, 29, 30 and 31.
  • the control pistons 28, 29, 30 and 31 have piston surfaces of different sizes, which have an area ratio of 1 2: 3: 4.
  • control piston 28 ', 29', 30 'and 31' which loaded the control piston 28, 29, 30 and 31. Due to their area differences, the control pistons 28, 29, 30, 31 are set to different pressure values, namely the control piston 28 to 0.5 bar, the control piston 29 to 1 bar, the control piston 30 to 2 bar and the control piston 31 to 4 bar.
  • control pistons 28-31 Under the control pistons 28-31 are a double valve 40, 41, 42 and 43, which rests with an inlet closing body on a housing-fixed inlet valve seat under the force of a valve spring 44, 45, 46 and 47.
  • a channel 48, 49 and 50 leads to a rear chamber 52, 53 and 54, and a correspondingly arranged relief chamber 55 of the first control piston 28 has an outside air connection 56, while from the outlet chamber 39 a channel 62 is Takes exit.
  • Spring chambers 57, 58, 59 and 60 of the valve spring 44-47 are jointly connected to a supply line 61.
  • the channel 62 leads to a control chamber 63 via a relay piston 64, the underside of which delimits a working chamber 65 and which has an extension 66 with which it can actuate a relay valve 67.
  • the relay valve 67 closes off a supply line 68 and connects a line 70 connected to a consumer 69 to a relief point 71.
  • control electronics 10 determines the solenoid valves 2, 3, 4 and 5 to be controlled in accordance with the predefined setpoint. For ease of understanding, only the symbols of simple switches are shown in the control electronics 10.
  • solenoid valve 2 If solenoid valve 2 is energized, it switches over. The outlet valve is closed and the inlet valve is opened. Then air can flow from the supply line 61 under control piston 28. The magnetic force, the spring force and the applied pressure are then weighed out on the control piston 28. In this way, the magnetic, spring and pressure forces acting on the control piston 28 determine the pressure introduced from the supply line 61 into the intermediate chamber 36. The introduced air flows via the channel 48 into the rear chamber 52 of the second control piston 29 and from there via the channel 49 to the third control piston 30 and from there via the channel 50 to the fourth control piston 31 and from there via the channel 62 into the control chamber 63 the relay piston 64.
  • That Realisventil 67 is switched over, and at the end of the relief point 71, supply air reaches the consumer 69 via the working chamber 65.
  • the relay piston 64 is only loaded by pressures, but not by spring forces, and its seal is protected because both in the switching stage and in the modulated state There are 64 equal pressures on the sides of the relay piston.
  • the first control piston 28 is set to 0.5 bar due to its surface design, this pressure is therefore controlled up to the relay piston 64. If a pressure of 2.5 bar is required by the setpoint generator 11, the binary breakdown in the control electronics 10 means that the control piston 30 must also be switched, which, as stated above, delivers a working pressure of 2 bar. Since 0.5 bar is already effective on the rear of the control piston 30, 2.5 bar must act on the front in order to keep this control piston 30 in equilibrium, and these 2.5 bar then reach the control chamber 63 of the relay piston 64. The relay valve 67 is adjusted accordingly.
  • the solenoid valves 2 and 4 remain de-energized and the solenoid valves 3 and 5 are energized.
  • the control piston 29 sets a pressure of 1 bar due to its special design of effective area and spring force, and the control piston 31 sets 4 bar, so that 5 bar are then effective on the relay piston 64.
  • the control piston 29 has atmospheric pressure as a reference on the piston rear side, while the control piston 31 has the 1 bar controlled by the control piston 29 as a reference variable.
  • the pressure on the relay piston 64 can be set from 0 to 7.5 bar (in 15 steps) in individual steps of 0.5 bar.
  • valves This is also the control amount for a valve.
  • the magnets 6, 7, 8 and 9 generate a defined force on the control pistons 28, 29, 30, 31 by means of a correspondingly regulated current. These control the corresponding pressures from the supply 61 to the control chamber 63. There, the pressure acts on the relay piston 64. A corresponding air pressure to the consumer 69 is regulated by the relay valve 67.
  • control magnets 6, 7, 8 and 9 have the advantage that many intermediate stages can be generated by correspondingly controlling them. With these control magnets it is possible to switch an intermediate stage between zero, half power and full power, so that the following picture results:
  • the control electronics determine the associated switch positions and magnets to set the pressure 4.7 bar:
  • each pressure can be set exactly (theoretically to 0.1 bar) without feedback via pressure sensors.
  • Is z. B a relay valve is acted upon by two control magnets, the first one having the appropriate pressures 0; 3; Switches 6 bar, the second control magnet takes over the infinitely variable fine adjustment between 0 and 3 bar. Due to the reduced control ranges of the individual magnets, an improved control accuracy can be achieved.
  • valve block 1 considered in the example according to FIG. 1 has normally closed valves. For some applications, however, it is advantageous to have an open valve position when de-energized to ensure control. An example of this is shown schematically in FIG. 2.
  • valve block 80 magnets 81, 82, 83 and 84 are biased against the magnetic control force by springs 85, 86, 87 and 88.
  • the valves here have the reference numbers 90, 91, 92 and 93.
  • the control piston device When the valve device is working, the control piston device will first close with the lowest control pressure. Where this control piston device is located in the series circuit (FIGS. 1 and 2) is - at least in theory - irrelevant. In Figure 2 it is e.g. B. the last valve 93 before the relay valve 67. The next control piston device that closes will apply the set reference pressure to the rear of the first (closed) control piston device. To keep the Ap on this first device, the pressure on the front will increase accordingly. The sum of all adjustable reference pressures determines the maximum possible pressure effective on the relay piston 64.

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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)
  • Magnetically Actuated Valves (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Description

Stand der TechnikState of the art

Die Erfindung bezieht sich auf eine Relaisventileinrichtung nach der Gattung der Hauptanspruchs. Eine derartige Relaisventileinrichtung ist bekannt (US-Patentschrift 36 43 682).The invention relates to a relay valve device according to the preamble of the main claim. Such a relay valve device is known (US Patent 36 43 682).

Diese bekannte Relaisventileinrichtung wird zur elektrischen Ferneinstellung von pneumatischen Drücken verwendet. Es sind Vorsteuermagnetventile vorgesehen, die als Schieberventile ausgebildet sind ; von dem ausgesteuerten Druck sind sie nicht beeinflußbar. Dadurch ist die bekannte Einrichtung nicht feinfühlig.This known relay valve device is used for the electrical remote adjustment of pneumatic pressures. Pilot solenoid valves are provided which are designed as slide valves; they cannot be influenced by the modulated pressure. As a result, the known device is not sensitive.

Der Erfindung liegt die Aufgabe zugrunde, eine feinfühlige Steuerung für einen Relaiskolben zu schaffen. Dabei soll eine zusätzliche Druckbeeinflussung der Vorsteuersteuermagnetventile eine vielfältige Stufungsmöglichkeit des Relaiskolben-Schaltdruckes gewährleisten.The invention has for its object to provide a sensitive control for a relay piston. An additional pressure influencing of the pilot control solenoid valves is intended to ensure a wide range of grading options for the relay piston switching pressure.

Diese Aufgabe wird gemäß der Erfindung bei einer gattungsgemäßen Relaisventileinrichtung durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst.This object is achieved according to the invention in a generic relay valve device by the characterizing features of claim 1.

Weitere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen.Further advantageous embodiments of the invention result from the subclaims.

Zeichnungdrawing

Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.Several embodiments of the invention are shown in the drawing and explained in more detail in the following description.

Es zeigen : Figur 1 eine erste Ausführung der Relaisventileinrichtung und Figur 2 eine Abwandlung der Bauart nach der Figur 1.FIG. 1 shows a first embodiment of the relay valve device and FIG. 2 shows a modification of the type according to FIG. 1.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Eine Relaisventileinrichtung ist als Ventilblock 1 dargestellt mit vier nebeneinander angeordneten 3/3-Wege-Magnetventilen 2, 3, 4 und 5, deren Magnete 6, 7, 8 und 9 über Leitungen an eine Steuerelektronik 10 angeschlossen sind, in die ein Sollwert über einen Geber 11, z. B. über ein Bremspedal eingebbar ist.A relay valve device is shown as valve block 1 with four 3/3-way solenoid valves 2, 3, 4 and 5 arranged next to one another, the magnets 6, 7, 8 and 9 of which are connected via lines to control electronics 10, into which a setpoint value is connected via a Encoder 11, e.g. B. can be entered via a brake pedal.

Die Magnete 6, 7, 8 und 9 haben Anker 12, 13, 14 und 15 und sind als Regelmagnete mit Regelkolben 28, 29, 30 und 31 ausgebildet. Die Regelkolben 28, 29, 30 und 31 haben verschieden große Kolbenflächen, die ein Flächenverhältnis von 1 2 : 3 :4 aufweisen.The magnets 6, 7, 8 and 9 have armatures 12, 13, 14 and 15 and are designed as control magnets with control pistons 28, 29, 30 and 31. The control pistons 28, 29, 30 and 31 have piston surfaces of different sizes, which have an area ratio of 1 2: 3: 4.

Unter jedem Regelkolben 28, 29, 30, 31 liegt je eine Regelfeder 28', 29', 30' und 31', die den Regelkolben 28, 29, 30 und 31 belasteten. Aufgrund ihrer Flächenunterschiede sind die Regelkolben 28, 29, 30, 31 auf verschiedene Druckwerte eingestellt, und zwar der Regelkolben 28 auf 0,5 bar, der Regelkolben 29 auf 1 bar, der Regelkolben 30 auf 2 bar und der Regelkolben 31 auf 4 bar. Unter den Regelkolben 28-31 befinden sich je ein Doppelventil 40, 41, 42 und 43, das mit einem Einlaß-Schließkörper an einem gehäusefesten Einlaß-Ventilsitz unter der Kraft einer Ventilfeder 44, 45, 46 und 47 anliegt. Von den Auslaßkammern 36, 37 und 38 führt je ein Kanal 48, 49 und 50 zu einer Rückseitenkammer 52, 53 und 54, und eine entsprechend angeordnete Entlastungskammer 55 des ersten Regelkolbens 28 hat einen Außenluftanschluß 56, während von der Auslaßkammer 39 ein Kanal 62 seinen Ausgang nimmt. Federräume 57, 58, 59 und 60 der Ventilfeder 44-47 sind gemeinsam an eine Vorratsleitung 61 angeschlossen.Under each control piston 28, 29, 30, 31 there is a control spring 28 ', 29', 30 'and 31', which loaded the control piston 28, 29, 30 and 31. Due to their area differences, the control pistons 28, 29, 30, 31 are set to different pressure values, namely the control piston 28 to 0.5 bar, the control piston 29 to 1 bar, the control piston 30 to 2 bar and the control piston 31 to 4 bar. Under the control pistons 28-31 are a double valve 40, 41, 42 and 43, which rests with an inlet closing body on a housing-fixed inlet valve seat under the force of a valve spring 44, 45, 46 and 47. From the outlet chambers 36, 37 and 38, a channel 48, 49 and 50 leads to a rear chamber 52, 53 and 54, and a correspondingly arranged relief chamber 55 of the first control piston 28 has an outside air connection 56, while from the outlet chamber 39 a channel 62 is Takes exit. Spring chambers 57, 58, 59 and 60 of the valve spring 44-47 are jointly connected to a supply line 61.

Der Kanal 62 führt zu einer Steuerkammer 63 über einen Relaiskolben 64, dessen Unterseite eine Arbeitskammer 65 begrenzt und der einen Ansatz 66 hat, mit dem er ein Relaisventil 67 betätigen kann. Das Relaisventil 67 schließt in seiner gezeichneten Stellung eine Vorratsleitung 68 ab und verbindet eine an einen Verbraucher 69 angeschlossene Leitung 70 mit einer Entlastungsstelle 71.The channel 62 leads to a control chamber 63 via a relay piston 64, the underside of which delimits a working chamber 65 and which has an extension 66 with which it can actuate a relay valve 67. In its drawn position, the relay valve 67 closes off a supply line 68 and connects a line 70 connected to a consumer 69 to a relief point 71.

WirkungsweiseMode of action

Im stromlosen Zustand sperren alle vier Magnetventile 2, 3, 4 und 5 die Vorratsleitung 61 ab. Wird der Sollwertgeber 11 betätigt, dann bestimmt die Steuerelektronik 10 entsprechend dem vorgegebenen Sollwert das beziehungsweise die anzusteuernden Magnetventile 2, 3, 4 und 5. Zum leichteren Verständnis sind in der Steuerelektronik 10 nur die Symbole einfacher Schalter dargestellt.In the de-energized state, all four solenoid valves 2, 3, 4 and 5 shut off the supply line 61. If the setpoint generator 11 is actuated, then the control electronics 10 determines the solenoid valves 2, 3, 4 and 5 to be controlled in accordance with the predefined setpoint. For ease of understanding, only the symbols of simple switches are shown in the control electronics 10.

Wird das Magnetventil 2 an Spannung gelegt, dann schaltet es um. Das Auslaßventil wird geschlossen und das Einlaßventil wird geöffnet. Dann kann Luft aus der Vorratsleitung 61 unter Regelkolben 28 strömen. Am Regelkolben 28 wiegen sich dann die Magnetkraft, die Federkraft und der eingesteuerte Druck aus. Auf diese Weise bestimmen die am Regelkolben 28 wirksamen Magnet-, Feder-und Druckkräfte den aus der Vorratsleitung 61 in die Zwischenkammer 36 eingesteuerten Druck. Die eingesteuerte Luft strömt über den Kanal 48 in die Rückseitenkammer 52 des zweiten Regelkolbens 29 und von dort über den Kanal 49 zum dritten Regelkolben 30 und von dort über den Kanal 50 zum vierten Regelkolben 31 und von dort über den Kanal 62 in die Steuerkammer 63 über dem Relaiskolben 64. Das Realisventil 67 wird umgeschaltet, und unter Abschluß der Entlastungsstelle 71 gelangt Vorratsluft über die Arbeitskammer 65 zum Verbraucher 69. Dabei ist der Relaiskolben 64 lediglich von Drücken, nicht aber von Federkräften belastet und seine Dichtung ist geschont, weil im Umschaltstadium und im ausgesteuerten Zustand auf beiden Seiten des Relaiskolben 64 gleiche Drücke herrschen.If solenoid valve 2 is energized, it switches over. The outlet valve is closed and the inlet valve is opened. Then air can flow from the supply line 61 under control piston 28. The magnetic force, the spring force and the applied pressure are then weighed out on the control piston 28. In this way, the magnetic, spring and pressure forces acting on the control piston 28 determine the pressure introduced from the supply line 61 into the intermediate chamber 36. The introduced air flows via the channel 48 into the rear chamber 52 of the second control piston 29 and from there via the channel 49 to the third control piston 30 and from there via the channel 50 to the fourth control piston 31 and from there via the channel 62 into the control chamber 63 the relay piston 64. That Realisventil 67 is switched over, and at the end of the relief point 71, supply air reaches the consumer 69 via the working chamber 65. The relay piston 64 is only loaded by pressures, but not by spring forces, and its seal is protected because both in the switching stage and in the modulated state There are 64 equal pressures on the sides of the relay piston.

Da der erste Regelkolben 28 aufgrund seiner Flächenauslegung auf 0,5 bar eingestellt ist, wird dieser Druck also bis zum Relaiskolben 64 durchgesteuert. Wird durch den Sollwertgeber 11 ein Druck von 2,5 bar gefordert, so ergibt sich durch die binäre Aufschlüsselung in der Steuerelektronik 10, daß zusätzlich der Regelkolben 30 zu schalten ist, der, wie oben ausgeführt, einen Arbeitsdruck von 2 bar liefert. Da auf der Rückseite des Regelkolbens 30 bereits 0,5 bar wirksam sind, müssen auf der Vorderseite 2,5 bar wirken, um diesen Regelkolben 30 im Gleichgewicht zu halten, und diese 2,5 bar gelangen dann in die Steuerkammer 63 des Relaiskolbens 64. Das Relaisventil 67 wird entsprechend verstellt.Since the first control piston 28 is set to 0.5 bar due to its surface design, this pressure is therefore controlled up to the relay piston 64. If a pressure of 2.5 bar is required by the setpoint generator 11, the binary breakdown in the control electronics 10 means that the control piston 30 must also be switched, which, as stated above, delivers a working pressure of 2 bar. Since 0.5 bar is already effective on the rear of the control piston 30, 2.5 bar must act on the front in order to keep this control piston 30 in equilibrium, and these 2.5 bar then reach the control chamber 63 of the relay piston 64. The relay valve 67 is adjusted accordingly.

Wenn der Sollwertgeber 5 bar vorgibt, so bleiben die Magnetventile 2 und 4 stromlos, und die Magnetventile 3 und 5 werden an Spannung gelegt. Der Regelkolben 29 stellt aufgrund seiner besonderen Bauart von Wirkfläche und Federkraft einen Druck von 1 bar ein, und der Regelkolben 31 stellt 4 bar ein, so daß am Relaiskolben 64 dann 5 bar wirksam sind. Dabei hat der Regelkolben 29 als Referenz auf der Kolbenrückseite Atmosphärendruck, während bei dem Regelkolben 31 die von dem Regelkolben 29 eingesteuerten 1 bar als Referenzgröße anstehen. Durch entsprechende Kombination läßt sich der Druck am Relaiskolben 64 - in einzelnen Stufen von 0,5 bar - von 0 bis 7,5 bar (d. h. in 15 Stufen) einstellen.If the setpoint generator specifies 5 bar, the solenoid valves 2 and 4 remain de-energized and the solenoid valves 3 and 5 are energized. The control piston 29 sets a pressure of 1 bar due to its special design of effective area and spring force, and the control piston 31 sets 4 bar, so that 5 bar are then effective on the relay piston 64. Here, the control piston 29 has atmospheric pressure as a reference on the piston rear side, while the control piston 31 has the 1 bar controlled by the control piston 29 as a reference variable. By means of a suitable combination, the pressure on the relay piston 64 can be set from 0 to 7.5 bar (in 15 steps) in individual steps of 0.5 bar.

Die Anzahl der Druckstufen ermittelt sich aus

Figure imgb0001
mit D = Anzahl der Druckstufen

  • S = Anzahl der Schaltstellungen der Ventile
  • M = Anzahl der Magnetventile.
The number of pressure levels is determined from
Figure imgb0001
 with D = number of pressure levels
  • S = number of switch positions of the valves
  • M = number of solenoid valves.

Im Beispiel sind 2 Schaltstellungen (Ein/Aus) durch die binäre Betrachtung vorhanden

Figure imgb0002
In the example there are 2 switching positions (on / off) due to the binary view
Figure imgb0002

Der Schaltstufensprung Ap für eine gleichmäßgie Stufung zwischen p = 0 und P = Pmax ermittelt sich aus :

Figure imgb0003
The switching step jump Ap for a uniform step between p = 0 and P = Pmax is determined from:
Figure imgb0003

Für das Beispiel mit Pmax = 7,5 bar; S = 2 und M = 4

Figure imgb0004
For the example with Pmax = 7.5 bar; S = 2 and M = 4
Figure imgb0004

Dies ist auch gleichzeitig der Regelbetrag eines Ventils. Die anderen Ventile sind entsprechend zu gestalten, um alle Werte zwischen 0,5 und 7,5 mit Ap = 0,5 darzustellen.This is also the control amount for a valve. The other valves are to be designed accordingly to display all values between 0.5 and 7.5 with Ap = 0.5.

Es ist noch zu bemerken, daß die Magnete 6, 7, 8 und 9 durch einen entsprechend eingeregelten Strom eine definierte Kraft auf die Regelkolben 28, 29, 30, 31 erzeugen. Diese steuern die entsprechenden Drücke aus dem Vorrat 61 zur Steuerkammer 63. Dort wirkt der Druck auf den Relaiskolben 64. Vom Relaisventil 67 wird ein entsprechender Luftdruck zum Verbraucher 69 eingeregelt.It should also be noted that the magnets 6, 7, 8 and 9 generate a defined force on the control pistons 28, 29, 30, 31 by means of a correspondingly regulated current. These control the corresponding pressures from the supply 61 to the control chamber 63. There, the pressure acts on the relay piston 64. A corresponding air pressure to the consumer 69 is regulated by the relay valve 67.

Die Anwendung der Regelmagnete 6, 7, 8 und 9 hat den Vorteil, daß sich durch entsprechende Ansteuerung derselben viele Zwischenstufen erzeugen lassen. Mit diesen Regelmagneten ist es möglich, eine Zwischenstufe zwischen Null, halber Kraft und voller Kraft zu schalten, so daß sich folgendes Bild ergibt :

Figure imgb0005
The use of control magnets 6, 7, 8 and 9 has the advantage that many intermediate stages can be generated by correspondingly controlling them. With these control magnets it is possible to switch an intermediate stage between zero, half power and full power, so that the following picture results:
Figure imgb0005

Nach der vorgenannten Gleichung (1) ergeben sich mit diesen drei Schaltstellungen für jeden der vier Magnete für den Ventilblock 1 insgesamt

Figure imgb0006
According to the aforementioned equation (1), these three switching positions result for each of the four magnets for the valve block 1 overall
Figure imgb0006

Will man z. B. einen Druck von 8 bar in der Steuerkammer 63 erreichen, so läßt sich mit der Kombination von vier Magneten und 3 Schaltstellungen in einem Ventilblock eine Stufung nach Gleichung (2) von :

Figure imgb0007
erreichen.Do you want z. B. achieve a pressure of 8 bar in the control chamber 63, the combination of four magnets and 3 switching positions in one valve block enables a gradation according to equation (2) of:
Figure imgb0007
 to reach.

Um mit dem Beispiel die Auswirkungen zu verdeutlichen, werden anschließend die einstellbaren Einzeldrücke aufgelistet. Magnetkräfte und Kolbenflächen sind dann entsprechend zu gestalten :

Figure imgb0008
In order to illustrate the effects with the example, the adjustable individual pressures are then listed. Magnetic forces and piston surfaces must then be designed accordingly:
Figure imgb0008

Zum Einstellen des Druckes 4,7 bar ermittelt die Steuerelektronik die zugehörigen Schaltstellungen und Magnete :

Figure imgb0009
The control electronics determine the associated switch positions and magnets to set the pressure 4.7 bar:
Figure imgb0009

Durch gezieltes Schalten der Magneten laßt sich jeder Druck genau (theoretisch auf 0,1 bar) ohne Rückmeldung über Drucksensoren einstellen.By specifically switching the magnets, each pressure can be set exactly (theoretically to 0.1 bar) without feedback via pressure sensors.

Ein weitere Vorteil läßt sich aus dem bisher Dargestellten ableiten : Da mit einem Regelmagneten beliebig viele Zwischenstufen möglich sind, läß sich für einen geschlossenen Regelkreis mit Druckrückmeldung die Regelung verfeinern.Another advantage can be derived from what has been presented so far: since any number of intermediate stages are possible with a control magnet, the control can be refined for a closed control circuit with pressure feedback.

Wird z. B. ein Relaisventil von zwei Regelmagneten beaufschlagt, wobei der erste durch entsprechende Gestaltung die Drücke 0 ; 3 ; 6 bar schaltet, übernimmt der zweite Regelmagnet die stufenlose Feinregelung zwischen 0 und 3 bar. Durch die reduzierten Regelbereiche der Einzelmagnete ist eine verbesserte Regelgenauigkeit zu erreichen.Is z. B. a relay valve is acted upon by two control magnets, the first one having the appropriate pressures 0; 3; Switches 6 bar, the second control magnet takes over the infinitely variable fine adjustment between 0 and 3 bar. Due to the reduced control ranges of the individual magnets, an improved control accuracy can be achieved.

Der in dem Beispiel nach Figur 1 betrachtete Ventilblock 1 hat stromlos geschlossene Ventile. Für einige Anwendungsfälle ist es aber von Vorteil, stromlos eine offene Ventilstellung zu haben, um die Durchsteuerung zu gewährleisten. Ein Beispiel dafür ist in der Figur 2 schematisch dargestellt.The valve block 1 considered in the example according to FIG. 1 has normally closed valves. For some applications, however, it is advantageous to have an open valve position when de-energized to ensure control. An example of this is shown schematically in FIG. 2.

In einem Ventilblock 80 sind Magnete 81, 82, 83 und 84 durch Federn 85, 86, 87 und 88 entgegen der Magnetregelkraft vorgespannt. Die Ventile tragen hier die Bezugszahlen 90, 91, 92 und 93. Bei der Arbeit der Ventileinrichtung wird zuerst die Regelkolben-Einrichtung mit dem kleinsten Regeldruck schließen. Wo diese Regelkolben-Einrichtung in der Reihenschaltung (Figur 1 und 2) sitzt, ist - zumindest theoretisch - belanglos. In der Figur 2 ist es z. B. das letzte Ventil 93 vor dem Relaisventil 67. Die nächste Regelkolben-Einrichtung, die schließt, wird mit dem eingestellten Referenzdruck die Rückseite der ersten (geschlossenen) Regelkolben-Einrichtung beaufschlagen. Um das Ap an dieser ersten Einrichtung zu halten, wird sich der Druck auf der Vorderseite entsprechend erhöhen. Die Summe aller einstellbaren Referenzdrücke bestimmt der am Relaiskolben 64 wirksame maximal mögliche Druck.In a valve block 80, magnets 81, 82, 83 and 84 are biased against the magnetic control force by springs 85, 86, 87 and 88. The valves here have the reference numbers 90, 91, 92 and 93. When the valve device is working, the control piston device will first close with the lowest control pressure. Where this control piston device is located in the series circuit (FIGS. 1 and 2) is - at least in theory - irrelevant. In Figure 2 it is e.g. B. the last valve 93 before the relay valve 67. The next control piston device that closes will apply the set reference pressure to the rear of the first (closed) control piston device. To keep the Ap on this first device, the pressure on the front will increase accordingly. The sum of all adjustable reference pressures determines the maximum possible pressure effective on the relay piston 64.

Claims (5)

1. Servo valve device for pneumatic pressure control system with pilot solenoid valves (2-5) which are modulable individually or conjointly in groups by an electronic control unit (10) and which make a control pressure available for a servo piston (64), characterized in that the pilot solenoid valves (2-5) are constructed as double valves (40-43 ; 90-93) and are provided with regulating pistons (28-31) formed directly on the armature (12-15) of the solenoid (6-9), the double valves each exhibiting an inlet valve spring-loaded in the closing direction and an outlet valve connected rigidly to the latter and cooperating with the associated regulating piston and being switchable by regulating solenoids (6-9) having the positions zero, half power and full power and pressure differentials engaging the regulating piston (28-31) into open position, into closed position and into intermediate positions, respectively referred to the position of the inlet valve ; in that the inlet valves are connected in parallel to a pressurized medium supply line (61) and control the admission of pressurized medium each to an outlet chamber (36-39), in that the outlet valves control the flow of pressurized medium between a rear chamber (52-55) on one side of the regulating piston (28-31) and the outlet chamber (36-39) on the other side of the regulating piston (28-31) ; in that the rear chamber (55) of the first solenoid vaive (2) is connected to a pressurized medium reducer (atmospheric connection 56), in that the outlet chambers (36-39) of the double valves (40-43 and 90-93) are connected to the rear chamber (52) of the next solenoid valve (3-5); and in that the outlet chamber (39) of the last double valve (43, 93) is connected to the control chamber (63) delimited by the servo pistol (64).
2. Servo valve device according to Claim 1, characterized in that the surface dimensions of the regulating pistons (28-31) are graduated in the ratio 1 : 2 : 3 : 4.
3. Servo valve device according to Claim 1 or 2, characterized in that each regulating piston (28-31) is spring-loaded.
4. Servo valve device according to one of Claims 1 to 3, characterized in that the double valves (40, 41, 42, 43) are constructed as valves open when deenergized referred to the position of the inlet valve.
5. Servo valve device according to one of Claims 1 to 3, characterized in that the double valves (90, 91, 92, 93) are constructed as valves closed when deenergized, referred to the position of the inlet valve.
EP87101581A 1986-03-08 1987-02-05 Servo valve for pneumatic-pressure control Expired EP0236742B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3607690 1986-03-08
DE19863607690 DE3607690A1 (en) 1986-03-08 1986-03-08 RELAY VALVE DEVICE FOR PNEUMATIC PRESSURE CONTROL

Publications (2)

Publication Number Publication Date
EP0236742A1 EP0236742A1 (en) 1987-09-16
EP0236742B1 true EP0236742B1 (en) 1989-10-11

Family

ID=6295849

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87101581A Expired EP0236742B1 (en) 1986-03-08 1987-02-05 Servo valve for pneumatic-pressure control

Country Status (3)

Country Link
EP (1) EP0236742B1 (en)
JP (1) JPS62224701A (en)
DE (2) DE3607690A1 (en)

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Publication number Priority date Publication date Assignee Title
KR920703354A (en) * 1990-02-02 1992-12-17 제임즈 다불류 머레이 Digital suspension
CN104007772A (en) * 2013-02-25 2014-08-27 广州市兆基饮水设备科技有限公司 Full intelligent safety pressure control system

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1703927A1 (en) * 1968-06-06 1971-04-08 Freital Plastmaschinen Delivery rate adjustment device for variable displacement pumps on hydraulically operated systems and machines, in particular injection molding machines
US3643682A (en) * 1970-10-26 1972-02-22 Sperry Rand Corp Power transmission
DE2302446A1 (en) * 1973-01-18 1974-07-25 Liebherr Aera Technik Gmbh DIGITAL PRESSURE REGULATING VALVE
US4020862A (en) * 1973-12-15 1977-05-03 Idra-Pressen G.M.B.H. Apparatus for controlling the volume and pressure of a pressure medium in a die-casting machine
DE3244920A1 (en) * 1982-12-04 1984-06-07 Wabco Westinghouse Steuerungstechnik GmbH & Co, 3000 Hannover DEVICE FOR CHANGING THE FORCE ACTING ON AN ACTUATOR

Also Published As

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DE3607690A1 (en) 1987-09-10
JPS62224701A (en) 1987-10-02
EP0236742A1 (en) 1987-09-16
DE3760756D1 (en) 1989-11-16

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