EP0167818B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0167818B1
EP0167818B1 EP19850106903 EP85106903A EP0167818B1 EP 0167818 B1 EP0167818 B1 EP 0167818B1 EP 19850106903 EP19850106903 EP 19850106903 EP 85106903 A EP85106903 A EP 85106903A EP 0167818 B1 EP0167818 B1 EP 0167818B1
Authority
EP
European Patent Office
Prior art keywords
valve
pipe
line
way valve
return
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
Application number
EP19850106903
Other languages
German (de)
English (en)
Other versions
EP0167818A1 (fr
Inventor
Friedrich-Wilhelm Höfer
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
Priority claimed from DE19843435304 external-priority patent/DE3435304A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0167818A1 publication Critical patent/EP0167818A1/fr
Application granted granted Critical
Publication of EP0167818B1 publication Critical patent/EP0167818B1/fr
Expired 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
    • 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
    • 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
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in 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
    • F15B2211/50—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
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means 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
    • F15B2211/50—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
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control 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
    • F15B2211/57—Control of a differential 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
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a control device according to the preamble of the main claim.
  • a control device known from the previously published document DE-A-2457451
  • relief of the spring space of the changeover valve is only possible with a certain delay when the directional control valves are in the neutral position.
  • pressure medium can also leak to the tank, which affects the position of the consumer. This increases the risk of accidents.
  • control device with the characterizing features of the main claim has the advantage that no pressure medium can leak through to the tank and load reduction and pressure increase is avoided in the switching transition.
  • the pressure raised at the changeover valve drops immediately when the directional control valves are returned to the neutral position, which means that the consumers connected to the directional control valves can change direction quickly.
  • FIG. 1 shows a circuit diagram of a control device and FIG. 2 shows a structural design of a detail.
  • a pump 11 draws pressure medium from a tank 13 via an inlet line 12 and conveys it into a pump line 14. From a point 15 shortly behind the pump 11 and from a second point 16, one line branches from the pump line 14 17 and 18 to the respective 7/3-way valves 19, 20 from.
  • the directional control valves 19, 20 are identical to one another, so that only the directional control valve 19 is described in more detail. It has the switch positions I, II, 111 and the connections a, b on one side and c, d, e, f, g on the other side.
  • switch position II which corresponds to the neutral position of the associated control slide 23
  • the connections a, b, e, f, g are blocked and the connections c, d are connected to one another.
  • switch position I connections a and e, b and c, f and g are connected to one another, and connection d is blocked.
  • a throttle 25 is formed on the control slide 23 in a connection 24 between the connection f and the connection g.
  • switch position 111 the connections a and c, b and e are connected to one another.
  • a line 27 branches off from the pump line 14 from the point 15 and leads to a return line 28 running to the tank 13.
  • a hydraulically pilot-controllable 2/2-way switching valve 29 is arranged in the line 27 and has a flow position I and a blocking position II and is loaded by a spring 30.
  • a line 32 branches off from the line 27 to one end of the switching valve 29.
  • a second line 33 leads from the point 31 to the other end face of the switching valve 29 loaded by the spring 30.
  • a throttle 34 is arranged in this line 33.
  • a line 37 leading to line 27 and opening after switching valve 29 is connected, in which a pressure relief valve 38 is arranged.
  • a line 39 also leads from the branch 36 to a shuttle valve 40.
  • This has a central connection 41, at which the line 29 opens, and two connections 42, 43.
  • a return line 46 leads to the connection 42 and leads to a second shuttle valve 47.
  • a line 48 branches off from the connection 43 and leads to the connection e of the directional control valve 19.
  • the shuttle valve 40 has a freely movable ball 49 without spring loading as a closing member.
  • a throttle 50 and a check valve 51 are arranged in series.
  • the check valve 51 secures the line 48 to the shuttle valve 40 between the throttle 50 and the directional control valve 19.
  • a line 53 leads from a point 53 from the line 48 to the connection f of the directional control valve 19.
  • a line 56 branches off from the line 48 and leads to the connection d of the Directional valve 19 leads.
  • the return line 28 opens at the connection c and the line 17 at the connection g.
  • a line 57 leads to a pressure chamber 58 of a double-acting working cylinder 59. Its pressure chamber 60 on the piston rod side is connected via a line 61 to the connection b of the directional control valve 19.
  • the return line 46 opens at the center connection 62 of the shuttle valve 47. From its connection 63, the return line 46 leads further to the tank 13.
  • the connection 64 is connected via a line 65 to the connection f of the second directional valve 20.
  • the shuttle valve 47 has a freely movable ball 66 without spring loading as a closing member.
  • a line 68 branches off from a point 67 and leads to the connection d of the second directional valve 20.
  • a line 70 leads from a second point 69 of the line 65 located between point 67 and directional control valve 20 to the connection e of the directional control valve 20.
  • the line 70 is secured by a check valve 71 to the line 65.
  • a return line 73 leading to the tank 13 opens at the connection c and the line 18 at the connection g.
  • a line 74 leads from the connection a of the directional control valve 20 to the pressure chamber 75 of a second double-acting working cylinder 76. Its pressure chamber 77 on the piston rod side is connected via a line 78 to the connection b of the directional control valve 20.
  • both directional control valves 19, 20 are in switch position II, lines 17, 18, 53, 48, 65, 70 are blocked.
  • the lines 53 and 48 are relieved of pressure via the line 56, the directional control valve 19 and the return line 28 to the tank 13.
  • Lines 65 and 70 are also relieved via line 68, directional control valve 20 and return line 73 to tank 13.
  • the pressure medium delivered by the pump 11 flows from the pump line 14 into the line 27, via the switching valve 29 in the flow position I into the return line 28 and back into the tank 13.
  • the pressure medium also flows from line 27 into line 32 and into line 33.
  • the pressure difference occurring at throttle 34 keeps switching valve 29 in its flow position I against the force of spring 30. As a result, only a small amount occurs at switching valve 29 , largely caused by the spring 30 pressure drop, so that the pump 11 delivers to the tank 13 with little pressure loss.
  • the pressure medium delivered by the pump 11 flows via the pump line 14 and the line 17 to the directional control valve 19, further via the connection 24 and the throttle 25 to line 53. From there it flows further via line 48, check valve 51 and line 57 into pressure chamber 58 of working cylinder 59. If an external load now acts on the piston rod of working cylinder 59, a corresponding load pressure acts in lines 57, 48. This closes the check valve 51 so that no pressure medium can flow out of the pressure chamber 58 of the working cylinder 59.
  • the pressure building up in the pump line 14 due to the pressure medium conveyed by the pump 11 can, however, now load from the pump line 14 via line 53, line 48, shuttle valve 40, line 39 and line 33 to the spring 30 Propagate side of switching valve 29.
  • the ball 49 of the shuttle valve 40 shuts off the connection 42. Due to the pressure building up on the switching valve 29, this is shifted into its blocking position 11.
  • the pump 11 can now build up further pressure in the pump line 14 and in the line 17. If this is greater than the load pressure, the check valve 51 opens and the pressure medium can flow via the line 57 into the pressure chamber 58 of the working cylinder 59.
  • the load acting on the working cylinder 59 is raised.
  • the pressure at the switching valve 29 is not raised.
  • the pressure medium delivered by the pump 11 flows from the pump line 14 into the line 18 and further via the connection 24 and the throttle 25 on the control slide 23 of the directional control valve 20 into line 65.
  • the check valve 71 is closed by the load pressure.
  • the current delivery pressure moves the ball 66 of the shuttle valve 47 to the port 63 and shuts it off.
  • the ball 49 of the shuttle valve 40 is pressed onto the connection 43 and shuts it off, so that the delivery pressure can act on the side of the switching valve 29 loaded by the spring 30.
  • the switching valve 29 is shifted into the blocking position II.
  • the check valve 71 opens and the pressure medium flows via line 74 into the pressure chamber 75 of the working cylinder 76.
  • the pressure medium flowing out of the other pressure chamber 77 flows through lines 78, 73 into the tank 13.
  • the directional control valves 19, 20 instead of the double-acting working cylinders 59, 76. It has proven to be advantageous not to raise the pressure at the switching valve 29 in the case of double-acting working cylinders and to increase this pressure only in the case of single-acting working cylinders.
  • the directional control valve 20 can also be designed as a 6/3 directional control valve. Of course, it is also possible that the pressure increase on the side opposite the spring 30 on the switching valve 29 is effective. The switching positions of the switching valve 29 are to be changed accordingly.
  • FIG. 2 shows a structural design of a detail of the exemplary embodiment according to FIG. 1 with a single-acting working cylinder.
  • the same components are again identified with the same reference numbers as before.
  • An approximately central longitudinal bore 82 is formed in a housing 81 of the directional control valve 19 or 20, in which the control slide 23 is slidably guided.
  • Eight annular grooves 84 to 91 are formed in the longitudinal bore 82.
  • the control slide 23 has five piston parts 94, 95, 96, 97, 98, which are separated from one another by annular grooves 99 to 102.
  • a control edge 105 facing the annular groove 99 is located on the piston part 94.
  • a control edge on the piston part 97 facing the annular groove 101 corresponds in its function to the throttle 25 in FIG. 1.
  • a line 107 connects the annular groove 85 to the pressure chamber 108 of a single-acting working cylinder 109.
  • the line 17 opens into the annular groove 90 and the return line 28 opens into the annular groove 84.
  • a channel which corresponds to the line 53 leads from the annular groove 89 to a channel corresponding to the line 48. This opens into the annular groove 86.
  • a channel corresponding to the line 56 connects the annular groove 87 to the connection 43 of the shuttle valve 40 and further via the throttle 50 to the line 48.
  • annular groove 87 can be connected to the annular groove 88 via the annular groove 100 on the control slide 23. A connection corresponding to line 56 in FIG. 1 can thereby be controlled.

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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 (7)

1. Dispositif hydraulique de commande (10) avec au moins un distributeur (19) adapté à la commande d'un dispositif utilisateur (59), et dont l'organe de commande (23) ferme, dans une position neutre, au moins une canalisation de fonctionnement (57, 61) aboutissant au dispositif utilisateur (59), et la relie alternativement, dans deux positions de fonctionnement (I, III) à une canalisation d'arrivée (14,17) ou à une première canalisation de retour (28), avec une soupape de commutation (29) pour renvoyer directement le fluide sous pression, refoulé dans la canalisation d'arrivée (14, 17) par une source (11) de fluide sous pression, dans la première canalisation de retour (28), avec une canalisation de commande (32, 33), associée à la soupape de commutation (23) et partant de la canalisation d'arrivée (14, 17), canalisation de commande sur laquelle estbranché au moins du premier emplacement d'étranglement (34), dont la différence de pression agit, contre l'action d'un ressort (30), sur un organe de fermeture de la soupape de commutation (29), avec une première soupape à deux voies (40), qui, par l'intermédiaire d'un raccordement médian (41) et d'une première canalisation (39) s'y raccordant et débouchant entre le premier emplacement d'étranglement (34) et la chambre du ressort (30) de la soupape de commutation (29), est raccordée à la canalisation de commande (32, 33); le premier raccordement de siège de cette soupape à deux voies étant relié à une seconde canalisation de retour (46) et son second raccordement de siège (43) étant en communication par une seconde canalisation (48) avec le premier distributeur, (19), dispositif caractérisé en ce que sur la seconde canalisation (48), allant au premier distributeur (19), est disposé un second emplacement d'étranglement (50) dont la pression rè- gnant du côté de la première soupape à deux voies (40) agit par l'intermédiaire de cette première soupape à deux voies (40) sur le côté,-sollicité par le ressort (30), de la soupape de commutation (29), cette seconde canalisation (48) étant protégée par rapport au second .emplacement d'étranglement (50) par une première soupape anti-retour (41), et la canalisation d'arrivée (14, 17) étant en communication avec la seconde canalisation (48) par l'intermédiaire du premier distributeur (19) au moins dans une position de fonctionnement (I, III) de ce distributeur.
2. Dispositif de commande selon la revendication 1, caractérisé en ce que la seconde canalisation (48), entre la première soupape à deux voies (40) et la première soupape anti-retour (51), est susceptible d'être délestée vers le réservoir (13) par l'intermédiaire d'une troisième canalisation (56), en position neutre (II) du premier distributeur (19), et que cette troisième canalisation (56) est fermée dans au moins une position de fonctionnement (I, III).
3. Dispositif de commande selon la revendication 1, et/ou 2, caractérisé en ce que la canalisation d'arrivée (14,17) est en communication, dans au moins une position de fonctionnement (I, III) du premier distributeur (19), avec la seconde canalisation (48) entre le second étranglement (50) et la première soupape anti-retour (51 ).
4. Dispositif de commande selon une des revendications 1 à 3, caractérisé en ce que la troisième canalisation (56) débouche dans la seconde canalisation (48) entre la première soupape à deux voies (40) et le second étranglement (50).
5. Dispositif de commande selon une des revendications 3 à 4, caractérisé en ce qu'un second distributeur (20) est susceptible d'être raccordé par l'intermédiaire d'une seconde soupape à deux voies (47) à la seconde canalisation de retour (46), et ce que sur une quatrième canalisation (70), allant de la deuxième soupape à deux voies (47) au deuxième distributeur (20), est disposée une seconde soupape anti-retour (71), protégeant la quatrième canalisation (70) par rapport à la seconde soupape à deux voies (47), et la quatrième canalisation (70) étant susceptible d'être reliée, au moins dans une position de fonctionnement (I, III) du distributeur (20), par l'intermédiaire de ce deuxième distributeur (20) à la canalisation d'arrivée (14,18).
6. Dispositif de commande selon une des revendications 1 à 5, caractérisé en ce que, sur le premier distributeur (19), est raccordé un équipement utilisateur à simple action.
7. Dispositif de commande selon une des revendications 1 à 6, caractérisé en ce qu'un équipement utilisateur à double action (76) est raccordé au second distributeur (20).
EP19850106903 1984-07-10 1985-06-04 Dispositif de commande hydraulique Expired EP0167818B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3435304 1984-07-10
DE19843435304 DE3435304A1 (de) 1983-10-10 1984-09-26 Verfahren und vorrichtung zur vergroesserung der bandbreite eines hochgeschwindigkeitsmodulators

Publications (2)

Publication Number Publication Date
EP0167818A1 EP0167818A1 (fr) 1986-01-15
EP0167818B1 true EP0167818B1 (fr) 1988-06-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850106903 Expired EP0167818B1 (fr) 1984-07-10 1985-06-04 Dispositif de commande hydraulique

Country Status (1)

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EP (1) EP0167818B1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4230185A1 (de) * 1991-09-10 1993-03-11 Heilmeier & Weinlein Wegeschieber fuer hydrauliksteuerungen

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Publication number Priority date Publication date Assignee Title
DE3722083C1 (de) * 1987-07-03 1988-09-15 Heilmeier & Weinlein Hydraulische Steuervorrichtung
DE3733679A1 (de) * 1987-10-05 1989-04-13 Rexroth Mannesmann Gmbh Steuerschaltung fuer einen mit einer verstellpumpe betriebenen hydraulischen kraftheber
DE3733677A1 (de) * 1987-10-05 1989-04-13 Rexroth Mannesmann Gmbh Lastunabhaengige steuereinrichtung fuer hydraulische verbraucher

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Publication number Priority date Publication date Assignee Title
US3971216A (en) * 1974-06-19 1976-07-27 The Scott & Fetzer Company Load responsive system with synthetic signal
DE2457451A1 (de) * 1974-12-05 1976-06-10 Bosch Gmbh Robert Hydraulische steuereinrichtung
DE2620041A1 (de) * 1976-05-06 1977-11-24 Bosch Gmbh Robert Hydraulische steuereinrichtung
US4089169A (en) * 1976-08-19 1978-05-16 The Scott & Fetzer Company Pressure actuated signal fluid control for load responsive systems

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4230185A1 (de) * 1991-09-10 1993-03-11 Heilmeier & Weinlein Wegeschieber fuer hydrauliksteuerungen

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