EP2891805B1 - Steueranordnung und Steuerventil für eine derartige Steueranordnung - Google Patents

Steueranordnung und Steuerventil für eine derartige Steueranordnung Download PDF

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Publication number
EP2891805B1
EP2891805B1 EP14190831.9A EP14190831A EP2891805B1 EP 2891805 B1 EP2891805 B1 EP 2891805B1 EP 14190831 A EP14190831 A EP 14190831A EP 2891805 B1 EP2891805 B1 EP 2891805B1
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EP
European Patent Office
Prior art keywords
control
valve
pressure
pressure medium
port
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.)
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Application number
EP14190831.9A
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German (de)
English (en)
French (fr)
Other versions
EP2891805A2 (de
EP2891805A3 (de
Inventor
Wolfgang Kauss
Benoit Galtier
Guillaume Fremiot
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2891805A3 publication Critical patent/EP2891805A3/de
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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.
  • Such a hydraulic control arrangement is known from data sheet RE 64 122 / 05.03 from Rexroth.
  • This has a plurality of control valves or throttle control valves, which are each used to control an actuator.
  • a pressure medium connection between the actuator assigned to the control valve and a hydraulic pump and between the actuator and a tank can be controlled with the control valve.
  • the control arrangement and the control valves are designed in an open center (OC) design.
  • a circulation channel extends from the control valves, starting from a high-pressure side or a pump line of the hydraulic pump and opening into the tank. The circulation channel is opened in a respective basic position of a valve spool of a respective control valve.
  • valve slide If the valve slide is shifted from the basic position in the direction of the first switching positions or in the opposite direction in the direction of the second switching position, a pressure medium connection between the hydraulic pump and the actuator is opened and the circulation channel is closed at the same time.
  • the control of the circulation channel leads to an increase in pressure in the pump line. If the pump pressure then exceeds a load pressure of the actuated actuator, a check valve assigned to the control valve opens, and the actuator is supplied with pressure medium from the pump line. Pressure control is thus carried out with such a control valve.
  • a size of the fluid volume flow flowing through the control valve to the actuator can only be controlled between 0 and a maximum fluid volume flow.
  • the level of the fluid volume flow determines, for example, the speed of the actuator, which can be a hydraulic cylinder.
  • Limiting the level of the fluid volume flow below the maximum delivery volume flow of the hydraulic pump is only possible if a part of the delivery volume flow is below the maximum pressure to the tank Circulation channel is throttled. Furthermore, the level of the fluid volume flow is not independent of the load pressure.
  • the differential pressure controller interacts with an actuating cylinder of a hydraulic pump in the form of a variable pump. If the valve spool of the control valve is now moved from its basic position in the direction of switching positions, the circulation channel is closed, which increases the pressure downstream of the pilot orifice. This in turn leads to the variable pressure controller pivoting the variable pump such that a pressure upstream of the pilot orifice also rises in order to keep the pressure difference across the pilot orifice constant. If the pressure in the pump line then exceeds the load pressure of the actuated actuator, the check valve assigned to the control valve opens and the actuator is supplied with pressure medium. Here too, the level of a fluid volume flow to the actuator cannot be controlled and limited independently of the load.
  • the invention has for its object to provide a hydraulic control arrangement or a throttle control that can easily control a size of a fluid volume flow to an actuator, in particular independent of the load pressure.
  • 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 is connected to a high-pressure side of the hydraulic pump or to a pump line via a control valve.
  • the control valve has a metering orifice for controlling the actuator.
  • a flow cross-section between the hydraulic pump and the actuator can be set with the metering orifice.
  • a circulation flow path is connected to the high-pressure side of the hydraulic pump via a pilot orifice.
  • the circulating flow path can be connected to a tank via the control valve (throttle control valve) arranged downstream of the pilot valve.
  • a pressure difference across the pilot orifice can be kept constant using a differential pressure regulator.
  • the differential pressure controller can tap the pressure upstream and downstream of the pilot orifice in order to cooperate with the control arrangement for keeping the pressure difference constant.
  • the pressure medium connection of the circulating flow path via the control valve is opened, in particular completely.
  • the pressure medium connection of the circulating flow path is controlled by the control valve, and additionally a pressurized medium connection between the circulating flow path and the actuator downstream of the metering orifice is opened.
  • the differential pressure controller is thus connected to the actuator via the control valve when the metering orifice is open Since the differential pressure controller now taps the pressure downstream of the pilot orifice and the metering orifice and upstream of the pilot orifice and the metering orifice, the pressure difference is kept constant on the one hand via the pilot orifice and on the other hand also via the metering orifice.
  • the fluid volume flow to the actuator can thus be set independently of the load via an opening cross section of the metering orifice. So far only throttle controls are from the prior art Control arrangements are known whose characteristic property is that only a pump pressure can be controlled.
  • a hydraulic control arrangement according to the invention furthermore has extremely low hydraulic losses, which leads to energy savings and cost reductions.
  • the hydraulic pump is preferably a variable displacement pump which can be pivoted via an actuating cylinder.
  • the differential pressure controller can interact with the variable displacement pump and the actuating cylinder in such a way that the pressure difference across the pilot orifice and, when the metering orifice is open, is also constant via the metering orifice.
  • 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 orifice or upstream of the control valve in the direction of a basic position.
  • the actuating cylinder In the basic position, the actuating cylinder can be relieved of the load on the tank in such a way that the variable displacement pump is pivoted in the direction of a higher delivery volume flow.
  • the valve slide can be acted upon by the pump pressure or by the pressure on 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 adjusting pump in such a way that the adjusting pump is pivoted in the direction of a smaller delivery volume flow.
  • a check valve is advantageously assigned to the control valve and / or the actuator in order 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. For example, it can be formed in the control valve or arranged outside of the control valve.
  • Another check valve for holding the load in the pressure medium flow path is preferably arranged between the pilot orifice and the control valve.
  • This check valve can also be formed in the control valve in the pressure medium flow path between the pilot orifice and the working connection 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 control valves. With regard to the circulation flow path, the control valves are thus fluidly arranged in series with one another. With the hydraulic control arrangement according to the invention, the fluid volume flow for a respective actuator can thus be both controlled and limited and adapted to the individual requirements of a respective actuator.
  • the control and limitation of the fluid volume flow from the hydraulic pump to the respective actuator can take place independently of the load pressure during a single movement and, moreover, for the actuator with the highest load pressure.
  • the control valve preferably has two working connections to which the actuator is connected. It also 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. When the valve spool is displaced from the basic position in the direction of the first switching positions, the first working connection can then be connected to the pressure connection via the metering orifice and the second working connection can be connected to the tank connection. If the valve slide is shifted from its basic position towards second switching positions, the second working connection can be connected to the pressure connection via the metering orifice and the first working connection can be connected to the tank connection. It is conceivable to provide a control valve with only one working connection, with which the valve spool can only be displaced in one direction from its basic position.
  • the control valve can have an input port and an output port.
  • a pressure medium connection between the input port and the first working port can be controlled via the valve slide.
  • a pressure medium connection between the input port and the second working port can then be opened.
  • variable displacement pump can be assigned a maximum pressure regulator. This is designed in such a way that, when a set maximum pump pressure is reached, it interacts with the variable displacement pump or the actuating cylinder in such a way that the maximum pump pressure is not exceeded.
  • the valve spool of the control valve is advantageously spring-centered in its basic position.
  • it can be actuated electrically, hydraulically or manually.
  • a hydraulic cylinder in particular in the form of a differential cylinder, is provided as the actuator, for example.
  • 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. All other valves and possibly also the variable displacement pump with the adjusting cylinder can also be arranged in this. Alternatively, it is conceivable to provide a valve disk for a respective control valve.
  • control valve can have an input connection and an output connection for the circulating flow path, with a pressure medium connection between the input connection and the first working connection being opened when the valve slide is shifted from the basic position in the direction of the first switching positions, a pressure medium connection between the second working connection and the tank connection is controlled and additionally a pressure medium connection between the second working connection and the pressure connection is controlled.
  • control valve is used to control a differential cylinder.
  • the second working connection is advantageously connected to the rod-side chamber of the differential cylinder.
  • a control valve according to the invention for the hydraulic control arrangement preferably has at least one working connection, preferably two working connections, for connecting an actuator. Furthermore, the control valve preferably has a pressure connection or pressure channel for connecting a hydraulic pump, a tank connection or tank channel as well as an input and an output connection or an input and output channel for a circulation flow path.
  • a continuously adjustable valve spool When a continuously adjustable valve spool is shifted from a basic position in the direction of switching positions, a pressure medium connection between the working connection and the pressure connection and the working connection and the input connection can be opened his. With this shift, a pressure medium connection between the input connection and the output connection can also be controllable.
  • Such a control valve is extremely simple in terms of device technology and, when used in a conventional hydraulic control arrangement or throttle control, leads to the advantages explained above as a replacement for the control valves used there.
  • a check valve that opens in the direction of pressure medium flow toward the valve slide can be provided between the pressure connection and the working connection upstream of the valve slide.
  • control valve can have a further second working connection.
  • the valve slide is advantageously arranged to be displaceable in a valve bore of the valve housing or a valve block or a valve disk.
  • 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 second control edge can be used to control a pressure medium connection between the input connection and the output connection in a first direction of displacement of the valve slide.
  • the pressure medium connection between the inlet 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 can be used to control the pressure medium connection between the input and the output connection in a second direction of displacement of the valve spool.
  • a sixth control edge is preferably used to control the pressure medium connection between the input port and the second work port.
  • a seventh control edge is provided for controlling the pressure medium connection between the first working connection and the tank connection.
  • an eighth control edge one Pressure medium connection between the second working port and the input port can be controlled. If the control valve is only designed for one working connection, it is conceivable to provide only the first, second, third and seventh control edge.
  • the first, third and fourth control edges can preferably open a flow cross section.
  • the second control edge preferably controls a flow cross section.
  • the sixth control edge can remain controlled.
  • the sixth, seventh and eighth control edge can open a flow cross-section, while the fifth control edge controls a flow cross-section.
  • the third control edge can remain controlled.
  • the third and the eighth control edge can be formed by at least one radial bore in the valve slide. This can open in each case via a blind hole, in particular axially made, through which it is then fluidly connected to the respective working connection, in particular via a radial hole made in the valve slide.
  • the third and eighth control edge can also each be designed as a bore star. A check valve opening in the direction of pressure medium flow towards the working connection can be provided in the blind hole.
  • the blind hole is advantageously of stepped design and introduced from one end of the valve spool.
  • a valve seat is formed on a step transition, on which a valve body of the check valve can rest in a sealing manner.
  • the valve body is arranged in a section of the blind hole having a larger diameter. In the direction of the valve seat, the valve body is acted upon by a spring force of a valve spring, which is supported on a closure element closing the blind hole. If the valve body is lifted from the valve seat, it gives a pressure medium connection between the Blind hole and at least one radial bore opening in the area of the working connection.
  • Figure 1 shows a hydraulic control arrangement 1, which is used as a throttle control for compact construction machines and enables volume flow control and limitation.
  • 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 and 8, respectively.
  • a hydraulic machine in the form of a variable displacement pump 10 with an actuating cylinder 12 is used to supply pressure to the actuators 6 and 8 intended.
  • the control arrangement 1 has a differential pressure regulator 14 and a maximum pressure regulator 16.
  • the maximum pressure regulator 16 limits a maximum pump pressure of the variable displacement pump 10.
  • variable displacement pump 10 pumps pressure medium from a tank line 20 connected to a tank 18 into a pump line 22, which represents the high pressure side of the variable displacement pump 10.
  • a respective control valve 2 or 4 with a pressure line 24 is connected to the pump line 22.
  • a check valve 26 which opens in the pressure medium flow direction away from the variable pump 10 and towards the respective control valve 2 or 4 is provided in the pressure line 24.
  • a respective pressure line 24 then opens into a pressure connection P of the control valve 2 or 4.
  • a respective control valve 2 or 4 is connected to the tank 18 with a tank line 28, the Tank line 28 extends from a tank port T of the control valve 2 or 4.
  • a respective control valve 2 or 4 has a first and a second working connection A and B.
  • a first working line 30 is connected to a respective first working connection A and a second working line 32 to a respective second working connection B.
  • 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 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 also connected to the pump line 22. This extends over the control valves 2 and 4 and opens into the tank 18.
  • a respective control valve 2 or 4 has an input port D and an output port D '.
  • a pilot orifice 44 is arranged in the circulation line 42 in the pressure medium flow path between the pump line 22 and the first control valve 2.
  • the differential pressure regulator 14 taps downstream of the pilot orifice 44 - between the latter and the first control valve 2 - the pressure via a control line 46 and upstream of the pilot orifice 44 - between the variable displacement pump 10 and the pilot orifice 44 - the pressure via a control line 48.
  • 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 via the pilot orifice 44.
  • the differential pressure regulator 14 is designed 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 in the opposite direction in the switching positions a by the pressure medium of the control line 48.
  • a connecting line 52 to the maximum pressure regulator 16 to the tank 18 is relieved 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 slide is in this case via a valve spring 54 with a spring force in the direction of a home position 0.
  • a pressure surface of the valve slide that is effective in this direction is connected to the tank 18 via a branch line 56.
  • the valve spool is pressurized with pressure medium from the pump line 22 via a control line 58.
  • a connection between the connecting line 52 and a cylinder line 60 is opened, the cylinder line 60 being connected to the actuating cylinder 12.
  • switch positions a the cylinder line 60 is in pressure medium connection with the pump line 22.
  • the actuating cylinder 12 is designed 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 penetrated by a piston rod 68, the piston rod 68 being 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 the variable displacement pump 10 in the direction of a larger delivery volume via its piston rod 18.
  • the variable displacement pump 10 is acted upon by a spring force of an adjusting spring 70. It is conceivable to alternatively design the differential cylinder as a plunger cylinder.
  • the control valve 4 is designed as a continuously adjustable 6/3-way valve.
  • the working connections A, B, the tank connection T and the pressure connection P are blocked, and the input connection D is connected to the output connection D '.
  • the valve spool is shifted from the basic position 0 in the direction of the first switching positions x, the pressure medium connection between the pressure port P and the first working port A is opened, whereby 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 the second cylinder chamber 38 of the actuator 8 is relieved of the load on 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.
  • the valve slide is therefore used as a metering orifice 72.
  • the connection between the input port D and the output port D ' is activated and, in return, a pressure medium connection between the input port D and the first working port A is opened.
  • a check valve 74 opening towards the actuator 8 is provided in the pressure medium flow path between D and the first working port A.
  • the connection between the input port D and the output port D ' is also activated again and at the same time a connection between the first working port B and the input port D is opened via a check valve 76.
  • the check valve 76 opens in the same way as the check valve 74 in a pressure medium flow direction from the input port D to the actuator 8 or the second working port B.
  • the input port D is thus connected downstream of the metering orifice 72 to the respective working port A, B.
  • Control valves 2 and 4 now enable load-independent volume flow control. If the valve slide of the control valve 2 is moved, for example, from its basic position 0 in the direction of the switching positions x, then both the pressure connection P and the input connection D are connected to the first working connection A. This means that the differential pressure controller 14 keeps the pressure difference constant both via the pilot orifice 44 and via the orifice 72. Thus over the opening cross section Metering orifice 72, the volume flow to the actuator 6 can be set independently of the load pressure.
  • the check valves 26, 74 and 76 serve to hold the load in the event that a pump pressure is below the load pressure.
  • control valve 2 is shown. This has a valve housing 78 in which a slide bore 80 for a valve slide 82 is formed. A tank channel 84 is also provided in the valve housing 78 and extends approximately transversely to the longitudinal direction of the valve slide 82. Control valves 2 and 4 are off Figure 1 formed in a common valve block, the tank channel 84 can extend through the entire valve block and open into a tank connection on the valve block. In addition, a pump channel 86 is provided in the valve housing 78, which extends approximately parallel to the tank channel 84. Furthermore, the working connections A and B are provided in the valve housing 78.
  • the slide bore 80 is comprised in the valve housing 78 by a total of nine ring grooves 88 to 104, which are arranged one behind the other in a row.
  • the two outer ring grooves 88 and 104 are connected to the tank channel 84.
  • the annular groove 90 adjacent to the annular groove 88 is connected to the first working connection A and the annular groove 102 adjacent to the annular groove 104 is connected to the second working connection B.
  • the annular groove 92 provided after the annular groove 90 is connected to the pump channel 86.
  • the connection to the pump channel 86 takes place via a check valve 106 arranged in the valve housing 78.
  • the central ring groove 96 is with the outlet connection D ', see also Fig.1 , connected.
  • the annular grooves 94 and 98 adjacent to the central annular groove 96 are each connected to the input connection D, see also Fig.1 ,
  • the basic position 0 of the valve slide 82 shown is the pressure medium connection between the annular grooves 94 and 96 via a control edge 108 of the valve slide 82 opened.
  • the pressure medium connection between the annular groove 98 and the annular groove 96 is also opened via a further control edge 110. All other ring grooves 88, 90, 92, 100, 102, 104 are separated from one another. If the valve slide 82 from the in Figure 2 shown basic position shifted to the right, it reaches the switching positions x, see also Figure 1 , A pressure medium connection between the pump channel 86 and the first working port A is then opened 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.
  • the second working connection B is connected to the tank channel 84 via a control edge 116 of the valve slide 82.
  • the connection of the input port D to the first working port A takes place via a bore star 118 which is introduced into the valve slide 82 and which opens into an axial blind hole 120 of the valve slide 82.
  • the bore star 118 is arranged in the region of the annular groove 94 and represents a control edge 122.
  • the blind bore 120 is introduced from an end face of the valve slide 82 and extends in the axial direction, in particular over the annular grooves 88 to 92. In the region of the annular groove 90, which is connected to the first working connection A, radial bores 124 are made in the valve slide 82. These also open into the blind bore 120.
  • the blind bore 120 is of stepped construction, with which a valve seat is formed at the step transition. This is located in the axial direction between the radial bores 124 and the bore star 118.
  • the valve seat is a valve body 126 of the check valve 74, see also Figure 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-in 130 (closure element) which is screwed into the valve slide 82.
  • the input connection D is thus connected via the annular groove 94, the bore star 118, the blind hole 120, the check valve 74 to the radial bore 124 and thus the annular groove 90, which in turn is connected to the first working connection A.
  • the valve spool 82 is off Figure 2 starting from the basic position shown in the direction of switching positions y, see also Figure 1 , shifted, a pressure medium connection between the second working port B and the pump channel 86 is opened via a control edge 132 of the valve slide 82.
  • the pressure medium connection between the annular groove 98 and the annular groove 96 is then controlled with the control edge 110.
  • the pressure medium connection between the annular groove 96 and the annular groove 94 is controlled by a further control edge 134.
  • a pressure medium connection between the first working port A and the tank channel 84 is opened with a control edge 136 of the valve slide 82.
  • the valve slide 82 is of mirror-symmetrical design and thus there is also a pressure medium connection between the input port D and the second working port B in the switching positions y. This takes place via a bore star 136, which serves as the control edge 138, a blind bore 140, the check valve 76 and the radial bore 142.
  • control edges 124, 112, 108, 110, 132 and 116 each have fine control notches.
  • control valve in the second switching positions y is essentially the same as the first switching positions x.
  • valve 144 In the second embodiment of a control valve 144 according to Figure 3 regeneration of a volume flow is provided when the valve slide 82 goes out from its in the Figure 3 shown basic position in the direction of the first switching position x is moved to the right.
  • the bore star 136 In contrast to the embodiment Figure 2 the bore star 136 is offset towards the radial bore 142, viewed in the axial direction. This leads to the fact that when the valve slide 82 is completely moved in the direction of the switching positions x, the bore star 136 is located in the area of the annular groove 100 and is therefore connected to the pump channel 86.
  • a differently designed check valve 144 is also provided in the blind bore 140.
  • the valve body 146 has a through bore with a nozzle, with which pressure medium can flow from the bore star 136 into its spring chamber 150.
  • the pressure in the bore star 136 acts on a pressure surface A 1 in the opening direction and the pressure of the radial bore 142 and thus the pressure of the second working connection B via an annular pressure surface A 2. In the closing direction, this acts on a pressure surface A 3 of the valve body 146 then the pressure in the spring chamber 150.
  • the pressure area A 3 is the sum of the pressure area A 1 and A 2 . If the pressure of the working connection 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.
  • the second working connection B is in turn connected to the pump channel 86.
  • Pressure medium can thus flow from the second working connection B to the first working connection A, with which there is a so-called "regeneration" of pressure medium.
  • the variable pump 10 from Figure 1 must then convey less pressure medium.
  • a hydraulic control arrangement for controlling at least one consumer forms an open center system.
  • a control valve is provided for the at least one consumer, 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 to the hydraulic pump via a pilot orifice, which is thus provided between the hydraulic pump and the control valve. If the control valve controls the consumer via a metering orifice, the circulating flow path is simultaneously closed and, in addition, a connection between the circulating flow path and the consumer downstream of the metering orifice is opened. About one The differential pressure controller then maintains a pressure difference across the pilot orifice and the orifice, which means that a fluid volume flow to the consumer can be varied independently of the load pressure via the orifice.

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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 Steueranordnung und Steuerventil für eine derartige Steueranordnung Active EP2891805B1 (de)

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

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

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EP (1) EP2891805B1 (enrdf_load_stackoverflow)
DE (1) DE102013224655A1 (enrdf_load_stackoverflow)
IN (1) IN2014DE03040A (enrdf_load_stackoverflow)

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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
DE102019219451A1 (de) * 2019-07-26 2021-01-28 Robert Bosch Gmbh Hydraulische Druckmittelversorgungsanordnung für eine mobile Arbeitsmaschine und Verfahren
DE102020208932A1 (de) 2020-07-16 2022-01-20 Robert Bosch Gesellschaft mit beschränkter Haftung Ventil mit selbsttätiger Rücklaufreduzierung bei ziehenden Lasten

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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
WO2014127356A1 (en) * 2013-02-15 2014-08-21 Parker-Hannifin Corporation Variable load sense open center hybrid system

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IN2014DE03040A (enrdf_load_stackoverflow) 2015-07-10
EP2891805A2 (de) 2015-07-08
DE102013224655A1 (de) 2015-06-03
EP2891805A3 (de) 2015-09-02

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