EP2891805A2 - Système de commande et soupape de commande pour un tel système de commande - Google Patents

Système de commande et soupape de commande pour un tel système de commande Download PDF

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Publication number
EP2891805A2
EP2891805A2 EP14190831.9A EP14190831A EP2891805A2 EP 2891805 A2 EP2891805 A2 EP 2891805A2 EP 14190831 A EP14190831 A EP 14190831A EP 2891805 A2 EP2891805 A2 EP 2891805A2
Authority
EP
European Patent Office
Prior art keywords
control
valve
pressure
port
pressure medium
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
EP14190831.9A
Other languages
German (de)
English (en)
Other versions
EP2891805B1 (fr
EP2891805A3 (fr
Inventor
Wolfgang Kauss
Benoit Galtier
Guillaume Fremiot
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
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Filing date
Publication date
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Publication of EP2891805A2 publication Critical patent/EP2891805A2/fr
Publication of EP2891805A3 publication Critical patent/EP2891805A3/fr
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Publication of EP2891805B1 publication Critical patent/EP2891805B1/fr
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Anticipated expiration legal-status Critical

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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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line

Definitions

  • the invention is based on a hydraulic control arrangement according to the preamble of claim 1 and a control valve for such a hydraulic control arrangement.
  • a hydraulic control arrangement is known.
  • This has a plurality of control valves or throttle control valves, which are each used to control an actuator.
  • the control valve With the control valve, a pressure medium connection between the control valve associated actuator and a hydraulic pump and between the actuator and a tank controllable.
  • the control arrangement and the control valves are designed in open-center (OC) construction.
  • OC open-center
  • valve slide starting from the basic position, is displaced in the direction of first switching positions or in the opposite direction in the direction of the second switching position, then a pressure medium connection between the hydraulic pump and the actuator is opened and the circulation channel is controlled at the same time.
  • the Zuseuu für of the circulation channel leads to an increase in pressure in the pump line.
  • a check valve associated with the control valve opens, and the actuator is supplied with pressure medium from the pump line. With such a control valve thus takes place a pressure control.
  • a size of the fluid volume flow flowing to the actuator via the control valve can in this case only be controlled between 0 and a maximum fluid volume flow.
  • the height of the fluid volume flow determines, for example, the speed of the actuator, which may be a hydraulic cylinder.
  • the actuator which may be a hydraulic cylinder.
  • a limitation of the height of the fluid volume flow below the maximum flow rate of the hydraulic pump is only possible if a part of the flow rate under a maximum pressure to the tank on the Circulating channel is throttled. Furthermore, the height of the fluid volume flow is not load pressure independent.
  • a valve in the form of a differential pressure controller to keep a pressure difference across the pilot valve constant.
  • the differential pressure regulator acts together with a control cylinder of a hydraulic pump in the form of a variable displacement pump. If the valve slide of the control valve is now moved from its basic position in the direction of switching positions, the circulation channel is closed, thus increasing a pressure downstream of the pilot aperture. This, in turn, causes the variable displacement pump to pivot the variable displacement pump so that a pressure upstream of the pilot orifice also increases to maintain the pressure difference across the pilot orifice constant. If the pressure in the pump line then exceeds the load pressure of the actuated actuator, then the check valve associated with the control valve opens and the actuator is supplied with pressure medium. Again, the height of a fluid flow to the actuator can not be controlled and limited load independent.
  • the invention has for its object to provide a hydraulic control arrangement or a throttle control, which can control a size of a fluid volume flow to an actuator, in particular load pressure independent, in a simple manner.
  • Another object of the invention is to provide a control valve for such a control arrangement which is simple and inexpensive.
  • a hydraulic control arrangement in particular a throttle control, is provided with a hydraulic pump for supplying pressure medium to at least one actuator.
  • the actuator On a high-pressure side of the hydraulic pump or on a pump line, the actuator is connected via a control valve.
  • the control valve has a metering orifice. With the metering orifice, in this case, a flow cross-section between the hydraulic pump and the actuator can be set.
  • a circulation flow path is connected to the high pressure side of the hydraulic pump via a pilot orifice.
  • the circulation flow path can be connected to a tank via the control valve (throttle control valve) arranged downstream of the pilot valve.
  • the differential pressure regulator can tap the pressure upstream and downstream of the pilot diaphragm in order to cooperate with the control arrangement for keeping the pressure difference constant.
  • the pressure medium connection of the circulation flow path is opened, in particular completely, via the control valve.
  • the pressure medium connection of the circulation flow path is controlled by the control valve, and additionally a pressure medium connection between the circulation flow path and the actuator, in particular opened downstream of the metering orifice.
  • the differential pressure regulator is thus connected to the actuator via the control valve when the metering orifice is controlled
  • the differential pressure regulator with controlled metering orifice now taps the pressure downstream of the pilot diaphragm and the metering orifice and upstream of the pilot diaphragm and the metering orifice, the pressure difference across the pilot diaphragm and, secondly, also via the metering orifice is thus kept constant.
  • a control of a fluid volume flow from the hydraulic pump to the actuator was previously not possible.
  • a maximum fluid flow rate could previously be provided only at a maximum pump pressure, resulting in high losses.
  • a hydraulic control arrangement according to the invention has extremely low hydraulic losses, resulting in energy savings and cost reduction.
  • the hydraulic pump is preferably a variable displacement pump, which is pivotable via a control cylinder.
  • the differential pressure regulator can in this case cooperate with the variable displacement pump and the actuating cylinder in such a way that the pressure difference across the pilot diaphragm and with the metering diaphragm open is also constant over the metering diaphragm.
  • the differential pressure regulator can be designed as a continuously adjustable 3/2-way valve.
  • a valve slide can be acted upon by a spring force of a valve spring and the pressure downstream of the pilot diaphragm or upstream of the control valve in the direction of a basic position.
  • the actuating cylinder In the basic position of the actuating cylinder can be relieved to the tank so that the variable displacement is pivoted in the direction of a higher flow rate.
  • the valve spool In the opposite direction of the valve spool can be acted upon by the pump pressure or by the pressure of the high pressure side of the hydraulic pump in the direction of switching positions.
  • the actuating cylinder can be supplied with pressure medium from the variable displacement pump such that the variable displacement pump is pivoted in the direction of a smaller flow rate.
  • a check valve is associated with the control valve and / or the actuator to hold a load of the actuator if the load pressure is higher than the pump pressure.
  • the check valve is preferably arranged upstream of the metering orifice. It may for example be formed in the control valve or arranged outside the control valve.
  • a further check valve is arranged for load-holding in the pressure medium flow path between the pilot diaphragm and the control valve.
  • This check valve may also be formed in the control valve in the pressure medium flow path between the pilot orifice and the working port of the control valve. It is also conceivable to arrange this check valve outside of the control valve.
  • control valves are fluidly connected in parallel to the high pressure side of the hydraulic pump.
  • the circulation flow path extends over all the control valves. With regard to the circulation flow path, the control valves are thus arranged fluidly in series.
  • the control and limitation of the fluid volume flow from the hydraulic pump to the respective actuator can be carried out independently of the load pressure in a single movement and, incidentally, for the load pressure-highest actuator.
  • the control valve preferably has two working ports to which the actuator is connected. Furthermore, it has a pressure connection for the hydraulic pump and a tank connection. In a basic position of the valve spool, all connections can be blocked. Upon a displacement of the valve spool outgoing from the basic position in the direction of first switching positions, the first working port can then be connected to the pressure port via the metering orifice and the second working port to the tank port. If the valve slide is moved from its basic position in the direction of second switching positions, the second working port can be connected to the pressure port via the metering orifice and the first working port to the tank port. It is conceivable to provide a control valve with only one working port, whereby the valve spool, starting from its basic position, can only be displaced in one direction.
  • the control valve may have an input port and an output port.
  • a pressure medium connection between the input connection and the first working connection can be controlled via the valve slide.
  • a pressure medium connection can then be controlled between the input connection and the second working connection.
  • variable displacement pump can be assigned a maximum pressure regulator. This is designed such that it interacts when reaching a set maximum pump pressure in such a way with the variable displacement pump or the actuating cylinder, that the maximum pump pressure is not exceeded.
  • valve spool of the control valve is spring-centered in its basic position. It can for example be electrically, hydraulically or manually operable.
  • a hydraulic cylinder in particular in the form of a differential cylinder, is provided.
  • the hydraulic control arrangement or the throttle control is preferably used in compact construction machines, in particular backhoe loaders, telescopic loaders, wheel loaders and mini and compact excavators for actuating their actuators or their working hydraulics.
  • control valve or the control valves are arranged in a valve block.
  • the variable displacement can be arranged with the actuating cylinder.
  • control valve may have an inlet connection and an outlet connection for the circulation flow path, wherein a displacement of the valve slide starting from the basic position in the direction of the first switching positions a pressure medium connection between the input port and the first working port is controlled, a pressure medium connection between the second working port and the tank port is controlled and in addition a pressure medium connection between the second working port and the pressure port is opened.
  • the second working port is advantageously connected to the rod-side chamber of the differential cylinder.
  • valve spool At the valve spool, only a comparatively small flow cross section for the pressure medium displaced from the rod side is released to the tank, so that a larger part of the pressure medium displaced from the rod side flows via the control valve to the first working port and thus to the bottom side of the differential cylinder due to the pressure ratio.
  • About the metering orifice of the valve spool now flows a sum of the back flowing from the rod side of the differential cylinder and flowing from the variable flow of fluid.
  • the differential pressure regulator of the variable displacement pump measures and limits the pressure difference across the metering orifice. In a limiting case, when the pressure fluid connection between the second working port and the tank is closed, the variable displacement pump only promotes the displaced by a piston rod of the differential cylinder volume.
  • a control valve according to the invention for the hydraulic control arrangement has at least one working connection, preferably two working connections, for connecting an actuator.
  • the control valve preferably has a pressure port or pressure port for connecting a hydraulic pump, a tank port or tank passage, and an input and an output port or an input and output port for a recirculation flow path.
  • Such a control valve is extremely simple in terms of device design and, when used in a conventional hydraulic control arrangement or throttle control, as a substitute for the control valves used there, leads to the advantages explained above.
  • a valve housing of the control valve may be provided between the pressure port and the working port upstream of the valve spool in the direction of pressure fluid flow toward the valve spool opening check valve.
  • control valve may have a further second working port.
  • the valve slide in a valve bore of the valve housing or a valve block or a valve disc is slidably disposed.
  • the valve slide preferably has a first control edge for controlling the pressure medium connection between the pressure connection and the first working connection.
  • a pressure medium connection between the input port and the output port can be controlled in a first direction of displacement of the valve spool.
  • the pressure medium connection between the input connection and the first working connection can be controlled via a third control edge.
  • a fourth control edge can be used to control the pressure medium connection between the second working connection and the tank connection.
  • a fifth control edge may be used to control the pressure medium connection between the inlet and outlet ports in a second direction of displacement of the valve spool.
  • a sixth control edge preferably serves for controlling the pressure medium connection between the input connection and the second working connection.
  • a seventh control edge is provided for controlling the pressure medium connection between the first working port and the tank port.
  • With an eighth control edge can a Pressure fluid connection between the second working port and the input port to be controlled. If the control valve is designed for only one working connection, then it is conceivable to provide only the first, second, third and seventh control edges.
  • the first, the third and the fourth control edge open a flow cross-section.
  • the second control edge in this case preferably controls a flow cross section.
  • the sixth control edge can remain closed.
  • the sixth, seventh and eighth control edge can open a flow cross-section, while the fifth control edge is heading for a flow cross-section.
  • the third control edge can remain closed.
  • the third and the eighth control edges can be formed by at least one radial bore in the valve slide. This can each open via a in the valve slide, in particular axially introduced blind hole, via which it is then fluidly connected to the respective working port, in particular via an introduced into the valve spool radial bore.
  • the third and eighth control edge can also be designed in each case as a bore star.
  • a check valve opening in the direction of the pressure medium flow towards the working connection can be provided.
  • the blind hole is stepped and formed from an end face of the valve slide ago.
  • a valve seat is formed, on which a valve body of the check valve can sealingly abut.
  • the valve body is in this case arranged in a larger diameter portion having the blind hole.
  • the valve body is acted upon by a spring force of a valve spring, which is supported on a closure element occluding the blind hole bore. If the valve body lifted from the valve seat, so he gives a fluid connection between the Blind hole and at least one opening in the area of the working port radial bore free.
  • FIG. 1 shows a hydraulic control assembly 1, which is used as a throttle control for compact construction machinery and a flow control and - limit allows.
  • the control arrangement 1 has a first control valve 2 designed as a throttle valve and a second control valve 4 designed as a throttle valve. These serve to control a respective actuator 6 or 8.
  • a hydraulic machine in the form of a variable displacement pump 10 is provided with an actuating cylinder 12 intended.
  • the control arrangement 1 has a differential pressure regulator 14 and a maximum pressure regulator 16.
  • the maximum pressure regulator 16 in this case limits a maximum pump pressure of the variable displacement pump 10.
  • the variable displacement pump 10 conveys pressure fluid from a tank line 20 connected to a tank 18 into a pump line 22, which constitutes the high-pressure side of the variable displacement pump 10.
  • a respective control valve 2 and 4 connected to a pressure line 24.
  • a respective pressure line 24 then opens into a pressure port P of the control valve 2 and 4, respectively.
  • a respective control valve 2 or 4 is connected to the tank 18, wherein the Tank line 28 extends from a tank port T of the control valve 2 and 4, respectively.
  • a respective control valve 2 or 4 has a first and second working port A and B.
  • a first working line 30 is connected and to a respective second working port B, a second working line 32.
  • the actuators 6 and 8 are designed as hydraulic cylinders in the form of differential cylinders. They each have a piston 34 which separates a first cylinder chamber 36 from a second cylinder chamber 38. The second cylinder chamber 38 is in this case penetrated by a piston rod 40, whereby it is designed as an annular chamber.
  • a circulation flow path in the form of a circulation line 42 is connected to the pump line 22. This extends here via the control valves 2 and 4 and opens into the tank 18.
  • a respective control valve 2 or 4 has an input terminal D and an output terminal D '.
  • a pilot diaphragm 44 is arranged in the circulation line 42.
  • the differential pressure regulator 14 grips the pressure via a control line 48 downstream of the pilot orifice 44-between the latter and the first control valve 2 -via a control line 46 and upstream of the pilot orifice 44-between the variable displacement pump 10 and the pilot orifice 44.
  • the differential pressure regulator 14 is designed in such a way that, in cooperation with the actuating cylinder 12 and the variable displacement pump 10, it keeps a pressure difference ⁇ p constant over the pilot orifice 44.
  • the differential pressure controller 14 is designed for this purpose as a continuously adjustable 3/2-way valve.
  • a valve spool of the differential pressure regulator 14 is acted upon in the direction of a basic position 0 by the pressure medium of the control line 46 and a spring force of a valve spring 50 and opposite in the direction of switching positions a from the pressure medium of the control line 48.
  • a connecting line 52 is relieved to the maximum pressure regulator 16 to the tank 18 and in the switching positions a, the connecting line 52 is connected to the pump line 22.
  • the maximum pressure regulator 16 is also designed as a continuously adjustable 3/2-way valve.
  • a valve spool is in this case via a valve spring 54 with a spring force in the direction of a basic position 0 applied.
  • an effective in this direction pressure surface of the valve spool is connected via a branch line 56 to the tank 18.
  • Opposite in the direction of switching positions a of the valve spool is acted upon via a control line 58 with pressure medium from the pump line 22.
  • a connection between the connecting line 52 and a cylinder line 60 is opened, wherein the cylinder line 60 is connected to the actuating cylinder 12.
  • the switching positions a the cylinder line 60 to the pump line 22 in fluid communication.
  • the adjusting cylinder 12 is configured as a differential cylinder and has a piston 62 which separates a first cylinder chamber 64 from a second cylinder chamber 66.
  • the second cylinder chamber 66 is in this case penetrated by a piston rod 68, wherein the piston rod 68 is connected to the variable displacement pump 10 in order to pivot it.
  • the first cylinder chamber 64 is connected to the cylinder line 60.
  • the actuating cylinder 12 pivots about its piston rod 18, the variable displacement pump 10 in the direction of a larger delivery volume.
  • the variable displacement pump 10 is acted upon by a spring force of a spring 70. It is conceivable to design the differential cylinder alternatively as a plunger cylinder.
  • the control valve 4 is designed as a continuously adjustable 6/3-way valve.
  • the working ports A, B, the tank port T and the pressure port P are locked, and the input port D is connected to the output terminal D '.
  • the pressure medium connection between the pressure port P and the first working port A is opened, with which the first cylinder chamber 36 of the actuator 8 can be supplied with pressure medium.
  • the second working port B is connected to the tank port T and thus relieves the second cylinder chamber 38 of the actuator 8 to the tank.
  • An opening cross-section between the pressure port P and the working port A depends on a displacement of the valve spool in the direction of the first switching positions x.
  • Valve spool is thus used as a metering orifice 72.
  • the connection between the input connection D and the output connection D ' is controlled and, in turn, a pressure medium connection between the input connection D and the first working connection A is opened.
  • a check valve 74 opening towards the actuator 8 is provided.
  • the connection between the input terminal D and the output terminal D ' is also controlled again and at the same time a connection between the first working port B and the inlet port D via a check valve 76 is opened.
  • the check valve 76 opens according to the check valve 74 in a pressure fluid flow direction from the input terminal D to the actuator 8 and the second working port B.
  • the input terminal D downstream of the metering orifice 72 is connected to the respective working port A, B.
  • the check valves 26, 74 and 76 serve to load in the event that a pump pressure is below the load pressure.
  • FIG. 2 the control valve 2 is shown.
  • This has a valve housing 78, in which a slide bore 80 is formed for a valve spool 82.
  • a tank channel 84 is further provided, which extends approximately transversely to the longitudinal direction of the valve spool 82.
  • the tank channel 84 may extend through the entire valve block and open into a tank connection to the valve block.
  • a pump channel 86 is provided in the valve housing 78, which extends corresponding to the tank channel 84 approximately parallel to this.
  • the working ports A and B are provided in the valve housing 78.
  • the spool bore 80 is included in the valve housing 78 of a total of nine annular grooves 88 to 104, which are arranged in series one behind the other.
  • the two outer annular grooves 88 and 104 are in this case connected to the tank channel 84.
  • the annular groove 88 adjacent to the annular groove 90 is connected to the first working port A and the annular groove 104 adjacent to the annular groove 102 with the second working port B.
  • the provided after the annular groove 90 annular groove 92 is connected to the pump channel 86.
  • the connection with the pump channel 86 takes place via a check valve 106 arranged in the valve housing 78.
  • the central annular groove 96 is connected to the outlet port D ', see also Fig.1 , connected.
  • the annular grooves 94 and 98 adjacent to the central annular groove 96 are respectively connected to the input terminal D, see also Fig.1 ,
  • valve spool 82 In the Fig. 2 shown basic position 0 of the valve spool 82 is the pressure medium connection between the annular grooves 94 and 96 via a control edge 108th the valve spool 82 is opened. Via a further control edge 110 and the pressure medium connection between the annular groove 98 and the annular groove 96 is opened. All other annular grooves 88, 90, 92, 100, 102, 104 are separated from each other. If the valve spool 82 from the in FIG. 2 shown shifted to the right, so he gets into the switch positions x, see also FIG. 1 , In this case, a pressure medium connection between the pump channel 86 and the first working port A is opened up via a control edge 112 of the valve slide 82.
  • the flow cross section between the annular grooves 94, 96 and 98 is controlled via the control edge 108 and via a further control edge 114. Furthermore, the second working port B is connected to the tank channel 84 via a control edge 116 of the valve spool 82.
  • the connection of the input terminal D to the first working port A, see also FIG. 1 via a introduced into the valve spool 82 bore star 118 which opens into an axial blind hole 120 of the valve spool 82. In the switching positions x of the bore star 118 is disposed in the region of the annular groove 94 and represents a control edge 122.
  • the blind hole 120 is introduced from an end face of the valve spool 82 and extends in the axial direction, in particular via the annular grooves 88 to 92. In the region of the annular groove 90, which is connected to the first working port A, 82 radial bores 124 are introduced in the valve spool. These also open in the blind hole 120.
  • the blind hole 120 is stepped, whereby at the step transition, a valve seat is formed. This is located in the axial direction between the radial bores 124 and the bore star 118.
  • the valve seat is in this case a valve body 126 of the check valve 74, see also FIG. 1 , assigned.
  • the valve body 126 is slidably guided in the blind hole 120 and is acted upon by a spring force of a valve spring 128 in the direction of the valve seat.
  • the valve spring 128 in turn is supported on a screw 130 (closure element), which is screwed into the valve spool 82 from.
  • a screw 130 closure element
  • valve spool 82 off FIG. 2 starting from the basic position shown in the direction of switching positions y, see also FIG. 1 shifted, a pressure medium connection between the second working port B and the pump channel 86 is controlled via a control edge 132 of the valve spool 82.
  • control edge 110 then the pressure medium connection between the annular groove 98 and the annular groove 96 is controlled.
  • control edge 134 the pressure medium connection between the annular groove 96 and the annular groove 94 is controlled.
  • a control edge 136 of the valve spool 82 a pressure medium connection between the first working port A and the tank channel 84 is opened.
  • the valve spool 82 is designed mirror-symmetrically and thus is also in the switching positions y a pressure medium connection between the input terminal D and the second working port B before. This is done via a bore star 136, which serves as a control edge 138, a blind hole 140, the check valve 76 and the radial bore 142nd
  • control edges 124, 112, 108, 110, 132 and 116 each have fine control notches.
  • the operation of the control valve is in the second switching positions y substantially corresponding to the first switching positions x.
  • the bore star 136 seen in the axial direction towards the radial bore 142 offset This results in that when the valve spool 82 is fully moved in the direction of the switching positions x, the bore star 136 is located in the region of the annular groove 100 and thus connected to the pump channel 86.
  • a differently configured check valve 144 is further provided in the blind bore 140.
  • the valve body 146 has a through-bore with a nozzle, with which pressure medium from the bore star 136 in the spring chamber 150 can flow. If the valve body 146 rests on the valve seat, the pressure in the bore star 136 acts in the opening direction on a pressure surface A 1 and the pressure of the radial bore 142 via an annular pressure surface A 2 and thus the pressure of the second working connection B. In the closing direction acts on a pressure surface A 3 of the valve body 146 then the pressure in the spring chamber 150.
  • the pressure surface A 3 is the sum of the pressure surface A 1 and A 2 .
  • the valve body 146 If the pressure of the working port B exceeds the pressure in the bore star 136 and thus the pressure in the pump channel 86, the valve body 146 is moved away from its valve seat and thus away from the bore star 136 and a connection between the bore star 136 and the radial bore 142 is opened. In turn, this is the second working port B with the pump channel 86 in communication. It can thus flow pressure medium from the second working port B to the first working port A, whereby a so-called "regeneration" of pressure medium is present. The variable 10 from FIG. 1 then has to promote less pressure medium.
  • a hydraulic control arrangement for controlling at least one consumer.
  • the control arrangement forms an open-center system.
  • a control valve is provided, via which a circulation flow path extends. This is connected on the one hand to a hydraulic pump and on the other hand to a tank.
  • the circulation flow path is connected via a pilot orifice, which is thus provided between the hydraulic pump and the control valve. If the control valve actuates the consumer via a metering orifice, the circulation flow path is simultaneously controlled and, in addition, a connection between the circulation flow path and the consumer downstream of the metering orifice is opened.
  • About one Differential pressure regulator is then kept a pressure difference across the pilot diaphragm and the metering orifice constant, whereby a fluid volume flow to the load load pressure independent via the metering orifice is variable.

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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)
EP14190831.9A 2013-12-02 2014-10-29 Système de commande et soupape de commande pour un tel système de commande Active EP2891805B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013224655.2A DE102013224655A1 (de) 2013-12-02 2013-12-02 Steueranordnung und Steuerventil für eine derartige Steueranordnung

Publications (3)

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EP2891805A2 true EP2891805A2 (fr) 2015-07-08
EP2891805A3 EP2891805A3 (fr) 2015-09-02
EP2891805B1 EP2891805B1 (fr) 2020-01-01

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Publication number Priority date Publication date Assignee Title
ITUB20159571A1 (it) * 2015-12-18 2017-06-18 Walvoil Spa Dispositivo valvolare idraulico a piu' sezioni di lavoro con sistema di controllo della pompa con linea di by-pass
DE102020208932A1 (de) 2020-07-16 2022-01-20 Robert Bosch Gesellschaft mit beschränkter Haftung Ventil mit selbsttätiger Rücklaufreduzierung bei ziehenden Lasten

Family Cites Families (8)

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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
DE2514624C3 (de) * 1975-04-03 1986-10-23 Danfoss A/S, Nordborg Steuereinrichtung für mindestens einen hydraulisch betriebenen doppeltwirkenden Verbraucher
US4089169A (en) * 1976-08-19 1978-05-16 The Scott & Fetzer Company Pressure actuated signal fluid control for load responsive systems
DE2939327C2 (de) * 1979-09-28 1984-10-25 Mannesmann Rexroth GmbH, 8770 Lohr Steuerblock für mehrere zugleich schaltbare hydraulische Verbraucher
DE10325295A1 (de) * 2003-06-04 2004-12-23 Bosch Rexroth Ag Hydraulische Steueranordnung
KR100518769B1 (ko) * 2003-06-19 2005-10-05 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 유압펌프 토출유량 제어회로
US9133605B2 (en) * 2012-02-27 2015-09-15 Husco International, Inc. Flow sensing based variable pump control technique in a hydraulic system with open center control valves
EP2956676B1 (fr) * 2013-02-15 2019-07-17 Parker Hannifin Corporation Système hybride à centre ouvert sensible à une charge variable

Non-Patent Citations (1)

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Title
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DE102013224655A1 (de) 2015-06-03
EP2891805B1 (fr) 2020-01-01
EP2891805A3 (fr) 2015-09-02
IN2014DE03040A (fr) 2015-07-10

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