CN115701492A - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
CN115701492A
CN115701492A CN202210916157.3A CN202210916157A CN115701492A CN 115701492 A CN115701492 A CN 115701492A CN 202210916157 A CN202210916157 A CN 202210916157A CN 115701492 A CN115701492 A CN 115701492A
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CN
China
Prior art keywords
valve
control device
pressure
proportional valve
working
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Pending
Application number
CN202210916157.3A
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Chinese (zh)
Inventor
A·冈德
H·弗莱冈
J·L·比罗德
M·韦根
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of CN115701492A publication Critical patent/CN115701492A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/30—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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/765—Control of position or angle of the output member

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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)

Abstract

The invention relates to a hydraulic control device (1) for actuating a hydraulic actuator (2), comprising: two working lines (4, 6) in which in each case an unlockable check valve (23, 24) is arranged; a proportional valve (10) via which the two working lines (4, 6) can be connected to a pressure medium source (8) or a pressure medium tank (9); and a short-circuit line (25) which connects the two working lines (4, 6) to one another with the two check valves (26, 27) in between, wherein one check valve (26) of the check valves arranged in the short-circuit line (25) is designed to be lockable and the other check valve (27) of the check valves arranged in the short-circuit line (25) is designed to be unlockable.

Description

Hydraulic control device
Technical Field
The invention relates to a control device for controlling the hydraulic pressure of a hydraulic actuator/consumer, in particular a differential hydraulic cylinder, according to the preamble of claim 1.
Background
In order to realize a linear drive request by an actuator, for example a hydraulic cylinder, it is necessary that the hydraulic control device can perform the following functions: force-position control, switching between normal switching and regeneration switching, load holding and pressure or force protection. Here, regeneration may refer to a feedback of fluid from the (piston) rod side of the hydraulic cylinder to the piston side of the hydraulic cylinder in such a way that both sides are fluidly connected to each other. The load holding function refers to the movement of the piston of the blocking hydraulic cylinder.
For this purpose, the internal known control device has a directional control valve which, depending on the switching position, connects two working lines, which are connected to pressure chambers of the actuator (hydraulic cylinder) acting in opposite directions, to a pressure medium source or a pressure medium sink. In each case one check valve is arranged in each of the two working lines (power pressure lines), which check valves can be unlocked by a pressure application in each case to the other working line. Furthermore, a load-dependent valve is arranged in the short-circuit line connecting the two working lines, which valve switches between a load-holding function and a normal and regeneration-switched function. That is to say, the function switching takes place without an electrical control signal. A disadvantage of this known control device is, however, that it cannot be used during load changeover and therefore four-quadrant operation cannot be realized. Furthermore, the mutually unlockable check valves do not have a clearly defined switching state, which strongly hampers the control functionality. Furthermore, the functional switching between standard and regeneration on must already be set mechanically at the time of planning or at the start of operation.
Another internal known control device also has a directional control valve which, depending on the switching position, applies or releases pressure to or from both working lines and in each case has a check valve arranged in both working lines. The first magnetic valve is used to unlock the non-return valve and the second magnetic valve is used to short-circuit the two working lines, so that the load holding function and the standard and regeneration switching function can be switched via valve control. This means that the function is switched by means of two electrical control signals. However, this solution has the disadvantage that two magnetic valves are required, so that such a control device is expensive, based on the number of magnetic valves and the required power electronics for the final stage to be switched on.
Disclosure of Invention
The object of the present invention is to provide a hydraulic control device with which the described hydraulic functions can be implemented, which at the same time is simple, compact and cost-effective to construct.
This object is achieved by a hydraulic control device having the features of claim 1. Advantageous embodiments of the invention are the subject matter of the dependent claims.
The control device according to the invention is used for actuating a hydraulic actuator, in particular a differential hydraulic cylinder. The control device has two working lines, one of which can be connected for actuating the actuator to a pressure chamber of the actuator acting in the opposite direction and in each of which an unlockable check valve is arranged, the blocked flow direction of which can be released from the direction of the pressure chamber by or by hydraulic actuation. The control device also has a proportional valve, by means of which the pressure chamber of the two working lines, which is pressure-loaded depending on the (on-off) position of the proportional valve, can be connected to a pressure medium source or to a pressure medium sink for the purpose of pressure relief of the pressure chamber concerned. The control device also has a short-circuit line which connects the two working lines to one another with the two check valves having opposite throughflow directions being connected in between. According to the invention, one check valve arranged in the short-circuit line is configured to be lockable and the other check valve arranged in the short-circuit line is configured to be unlockable.
According to the invention, the control device has a preferably magnetically controlled switching valve, by means of which the unlockable check valve arranged in the working line and the unlockable check valve arranged in the short-circuit line can be hydraulically actuated in the switching position of the switching valve.
In other words, the control device according to the invention has a first working line which can be connected to (or with) a first pressure chamber of an actuator, so that the actuator can be adjusted in a first direction, in particular in a direction of displacement of a hydraulic cylinder as an example of such an actuator, by applying a pressure to the first working line, and a second working line which can be connected to (or with) a second pressure chamber of the actuator, so that the actuator can be adjusted in a second direction, in particular in a direction of displacement of a hydraulic cylinder as an example of such an actuator, by applying a pressure to the second working line. In this case, a first check valve is arranged in the first working line and a second check valve is arranged in the second working line, which check valves each enable a pressure medium flow only in the direction of the actuator or the respective pressure chamber and block a pressure medium flow in the blocking direction/counter/opposite direction. The first and second check valves are configured to be unlocked, more precisely in the sense that the locking direction is (controllably) released/unlocked when pressure loads the control joint of the respective check valve. The control device also has a proportional valve for continuously adjusting the hydraulic resistance and, depending on the position, connecting the first working line or the second working line for pressure application to the pump/pressure medium source or the tank/pressure medium tank. The control device additionally has a short-circuit line, via which the two working lines are or can be fluidically connected to one another. In this case, the third check valve arranged in the short-circuit line makes it possible to achieve a pressure medium flow in only one throughflow direction from one of the working lines into the other working line, in particular from the second working line into the first working line, and to block the pressure medium flow in the blocking direction/reverse direction, in particular from the first working line into the second working line.
The fourth check valve arranged in the short-circuit line makes it possible to achieve a pressure medium flow in only one throughflow direction from the other working line into one of the working lines, in particular from the first working line into the second working line, and to block the pressure medium flow in the blocking direction/reverse direction, in particular from the second line into the first line. The third check valve is designed to be lockable, i.e. the throughflow direction is (controllably) closed/locked when the control connection of the third check valve is acted upon by pressure. The fourth check valve is configured to be unlocked, more precisely in the sense that the locking direction is (controllably) released/unlocked when the pressure loads the control connection of the fourth check valve.
According to the present invention, the control device has an on-off valve that controls/opens/closes the first, second, and third check valves. This means that the switching valve releases the pressure in the first switching position to the control connections of the first, second and third check valves, i.e. the three check valves are not controlled (in the aforementioned sense), and in the second switching position the control connections of the first, second and third check valves are pressurized, i.e. the three check valves are controlled (in the aforementioned sense).
In a simple manner, the control device according to the invention has (only) one switching valve, by means of which three of the four check valves can be hydraulically actuated simultaneously.
The configuration according to the invention of the control device has the advantage that three hydraulic functions, namely standard switching/force-position control, regenerative switching and load holding, can be implemented and that at the same time only the proportional valve (with integrated control), the magnetically controlled switching valve and the logic element in the form of a lockable/unlockable check valve can be switched in a defined manner between the hydraulic functions. A particularly simple and cost-effective construction is thus obtained, which does not adversely affect the functionality. It is thus possible to provide a highly integrated actuator with a three-in-two switching function.
According to an advantageous further development of the invention, the releasable non-return valve arranged in the short-circuit line can be hydraulically actuated when the first of the two working lines is pressurized. This has the advantage that the pressure in the first working line caused by friction can be used in order to open the unlockable non-return valve between the two working lines, so that the two working lines can be connected to one another.
According to an advantageous further development, the short-circuit line can be connected downstream of an unlockable check valve arranged in the working line to the working line.
In a preferred embodiment, the proportional valve can have a zero position, in which the two working lines are relieved, and a plurality of actuating positions, in which the hydraulic resistance between the working lines on the one hand and the pressure medium source and the pressure medium sink on the other hand can be set. This makes it possible to implement all the required hydraulic functions with a control device of simple design.
In an advantageous further development, the force-position adjustment can be effected in the actuated switching position of the switching valve and in the actuating position of the proportional valve, the regeneration is effected in the actuated switching position of the switching valve and in the actuating position of the proportional valve, and the load holding function is effected in the non-actuated switching position of the switching valve and in the zero position of the proportional valve.
According to an advantageous further development, the control electronics and the power electronics can be mounted directly on the proportional valve for controlling the proportional valve. A particularly compact construction can thus be achieved.
The proportional valve can be designed in particular as an integrated shaft control valve (IAC valve), so that already existing components can be used.
In a preferred embodiment, one or both of the two working lines can be connected to the pressure medium reservoir via a pressure regulating/limiting valve. This means that the first working line can be connected to the pressure medium reservoir via the first pressure control valve and/or the second working line can be connected to the pressure medium reservoir via the second pressure control valve. The pressure protection or force protection of the hydraulic control device can be achieved by providing the pressure regulating valve.
In a preferred embodiment, a pressure sensor can be arranged in one of the two working lines or in both working lines. That is to say that a first pressure sensor is arranged in the first working line and/or a second pressure sensor is arranged in the second working line. By detecting the pressure in the working line, a force-position control can be effected by means of a hydraulic control device.
According to an advantageous further development, the control device can have a stroke sensor for detecting the position of the actuator and the proportional valve has an input for the signal of the stroke sensor. By detecting the position of the actuator, in particular of the hydraulic cylinder, which is transmitted to the proportional valve, an effective force-position adjustment can be achieved.
According to an advantageous further development, the proportional valve can have a second stroke measuring sensor for detecting the position of the control piston of the proportional valve. That is to say, the stroke measuring system is integrated in the proportional valve, so that the position data of the control piston can be used for the regulation.
Drawings
Preferred embodiments of the invention are explained in more detail below with the aid of schematic drawings.
Fig. 1 is a simplified hydraulic circuit diagram of a hydraulic control device.
Detailed Description
Fig. 1 shows a preferred embodiment of a hydraulic control device 1. The control device 1 is used to operate a hydraulic actuator 2. The actuator, which is in particular designed as a differential hydraulic cylinder, can be supplied with pressure medium via a pressure medium source (not shown) and can be relieved of pressure via a pressure medium sink (not shown). In this case, a first pressure chamber 3 on the piston side of the actuator 2 is connected to a first working line 4 of the control device 1 and a second pressure chamber 5 on the piston rod side of the actuator 2 is connected to a second working line 6 of the control device 1. The actuator 2 has a stroke measuring sensor 7 for detecting the position of the actuator 2, that is to say of the differential hydraulic cylinder. Depending on the connection of the control device 1, the first working line 4 and the second working line 6 can be connected to a pressure medium source via a pressure connection 8/P connection of the control device 1 or to a pressure medium sink via a tank connection 9/T connection of the control device 1.
The control device 1 has a proportional valve 10, which depending on the switching position connects the pressure connection 8 or the tank connection 9 to the first working line 4 (connection a) or to the second working line 6 (connection B). In a first final switching position 11 of the proportional valve 10, the pressure connection 8 is connected to the first working line 4 and the tank connection 9 is connected to the second working line 6. In a second final switching position 12 of the proportional valve 10, the tank connection 9 is connected to the first working line 4 and the pressure connection 8 is connected to the second working line 6. In the intermediate switching position 13 of the proportional valve 10, there is no pressure operation between the pressure connection 8 and the tank connection 9, and the first working line 4 and the second working line 6 are relieved of pressure toward the tank connection 9. The switch intermediate position 13 is a floating position. In the zero position 14 of the proportional valve 10, the first working line 4 and the second working line 6 are connected to the tank connection 9 and the pressure connection 8 is blocked. The zero position 14 is a floating position. The proportional valve 10 can be operated by an electromagnet 15. The proportional valve 10 is in the null position 14 without manipulation. The proportional valve 10 has a stroke measuring sensor 16 for detecting the position of the control piston of the proportional valve 10. Furthermore, the proportional valve 10 has control electronics 17. The proportional valve 10 may have an input for the signal of the stroke measuring sensor 7.
The control device 1 has a switching valve 18 which, depending on the switching position, connects the pressure connection 8 or the tank connection 9 to a control line 19. In a first switching position 20 of the switching valve 18, the control line 19 is connected to the tank connection 9. In a second switching position 21 of the switching valve 18, the control line 19 is connected to the pressure connection 8. The on-off valve 18 can be operated by an electromagnet 22. The switching valve 18 is in the first switching position 20 without actuation.
In the first working line 4 a first non-return valve 23 is arranged, which is arranged between the proportional valve 10 and the actuator 2. The first non-return valve 23 effects a pressure medium flow in the direction of the actuator 2/in the direction of the proportional valve 10 and blocks the pressure medium flow from the actuator 2/back to the proportional valve 10. The first check valve 23 is designed to be switchable. The first check valve 23 can be hydraulically actuated, in particular, via the control line 19, that is to say via the switching valve 18. The first check valve 23 is unlockable and thus prevented from closing upon hydraulic actuation.
In the second working line 6 a second non-return valve 24 is arranged, which is arranged between the proportional valve 10 and the actuator 2. The second non-return valve 24 effects a pressure medium flow in the direction of the actuator 2/in the direction of the proportional valve 10 and blocks a pressure medium flow from the direction of the actuator 2/back to the proportional valve 10. The second check valve 24 is designed to be switchable. The second check valve 24 can be hydraulically actuated, in particular, via the control line 19, that is to say via the switching valve 18. The second check valve 24 is unlockable, thus preventing closing upon hydraulic actuation.
The control device 1 has a short-circuit line 25 which connects the first working line 5 with the second working line 6. The short-circuit line 25 is connected downstream of the first check valve 23 to the first working line 4 and downstream of the second check valve 24 to the second working line 6. A third check valve 26 is arranged in the short-circuit line 25, which third check valve effects a flow of pressure medium in the direction of the second working line 6 and blocks a flow of pressure medium back in the direction of the second working line 6. The third check valve 26 is designed to be switchable. The third check valve 26 can be hydraulically actuated, in particular, via the control line 19, that is to say via the switching valve 18. The third check valve 26 is latchable and thus prevented from opening upon hydraulic actuation. In the short-circuit line 25, a fourth check valve 27 is arranged, which effects a pressure medium flow in the direction of the first working line 4 and blocks the pressure medium flow in the direction back into the first working line 4. The fourth check valve 27 is designed to be switchable. The fourth check valve 27 can be actuated hydraulically via the first working line 4. The fourth check valve 27 is unlockable and thus prevents closing upon hydraulic actuation.
The control device 1 also has a first pressure sensor 28 connected to the first working line 4 and a second pressure sensor 29 connected to the second working line 6. The control device 1 also has a first pressure-limiting valve 30 which connects the first working line 4 to the tank connection 9 and a second pressure-limiting valve 31 which connects the second working line 6 to the tank connection 9.
The hydraulic control device 1 operates in the following manner.
In a first operating state, a hydraulic function is achieved in which regeneration is switched on, the hydraulic cylinder being moved out and the two pressure chambers 3, 5 of the hydraulic cylinder being hydraulically connected via the short-circuit line 25. During the setting of the proportional valve 1, that is to say the proportional valve 10, the pressure connection 8 is connected to the first working line 4, and the switching valve 18 is closed, that is to say is in its first switching position 20. The hydraulic cylinders are displaced and can be adjusted by means of the force-position adjustment via the proportional valve 10, and the fourth, unlockable check valve in the short-circuit line 25 is opened by the pressure in the first working line 4 or in the first pressure chamber 3, which pressure is caused by friction, so that the first working line 4 and the second working line 6 are connected to one another and the hydraulic cylinders can be displaced at a faster speed.
In the second operating state, the hydraulic function of the force-position control is implemented. During the adjustment of the proportional valve 1, that is to say the proportional valve 10 is not in the zero position 14, and the switching valve 18 is opened, that is to say in its second switching position 21. The force-position control is carried out via the proportional valve 10, in particular also via the stroke sensor 16 and the input for the signal of the stroke sensor 7. The third, lockable check valve 26 is hydraulically actuated via the switching valve 18, so that the first working line 4 and the second working line 6 are separated from one another. The first unlockable check valve 23 and the second unlockable check valve 24 are hydraulically actuated by the switching valve 18, so that they are opened in a defined manner and a four-quadrant operation is achieved.
In the third operating state, the hydraulic function of the load remaining switched on is implemented. The proportional valve 1 is not being adjusted, that is to say the proportional valve 10 is in the zero position 14 and the switching valve 18 is closed, that is to say is in the first switching position 20. The check valves 23, 24, 26, 27 are not hydraulically actuated and are in their basic position. The connection between the first working line 4 and the second working line 6 is closed in a defined manner and the first unlockable check valve 23 and the second unlockable check valve 24 are closed in a defined manner by the load. The non-return valves 23, 24, 26, 27 are preferably designed in the form of seat valve structures, so that no leakage and therefore no slow cylinder movements are possible.

Claims (10)

1. A hydraulic control device (1) for actuating a hydraulic actuator (2), in particular a differential hydraulic cylinder, comprises:
two working lines (4, 6), one of which can be connected to the pressure chambers (3, 5) of the actuator (2) acting in opposite directions for actuating the actuator (2), and in each of which a check valve (23, 24) is arranged, which can be opened in a controlled manner and whose closed flow direction can be released from the direction of the pressure chambers (3, 5) by hydraulic actuation;
a proportional valve (10) via which the two working lines (4, 6) can be connected to a pressure medium source for pressurizing the associated pressure chamber (3, 5) or to a pressure medium tank for relieving the associated pressure chamber (3, 5), depending on the position of the proportional valve (10); and
a short-circuit line (25) which connects the two working lines (4, 6) to one another with the interposition of two check valves (26, 27) having opposite throughflow directions,
it is characterized in that the preparation method is characterized in that,
one of the check valves (26) arranged in the short-circuit line (25) is configured to be controllably lockable and the other check valve (27) arranged in the short-circuit line (25) is configured to be controllably unlockable, and
the control device has a switching valve (18) by means of which a non-return valve (23, 24) which is arranged in the working line (4, 6) and can be unlocked in a controlled manner and a non-return valve (26) which is arranged in the short-circuit line (25) and can be locked in a controlled manner are hydraulically actuated in a single switching position (21) of the switching valve (18).
2. Control device (1) according to claim 1, characterized in that a check valve (27) which can be controllably unlocked and which is arranged in the short-circuit line (25) is hydraulically actuated when pressure is applied to the first working line (4) of the two working lines (4, 6).
3. Control device (1) according to claim 1 or 2, characterized in that the short-circuit line (25) is connected downstream of a check valve (23, 24) which is arranged in the working line (4, 6) and can be unlocked in a controlled manner to the working line (4, 6).
4. A control device (1) according to any one of claims 1 to 3, characterised in that the proportional valve has a zero position (14), in which the two working lines (4, 6) are relieved, and an adjusting position (11, 12, 13), in which the hydraulic resistance between the working lines (4, 6) on the one hand and the pressure medium source and the pressure medium sink on the other hand can be set.
5. A control device (1) according to claim 4, characterized in that the force-position adjustment is effected in the actuated switching position (21) of the switching valve (18) and in the actuating position (11, 12, 13) of the proportional valve (10), the regeneration switch-on is effected in the actuated switching position (21) of the switching valve (18) and in the actuating position (11, 12, 13) of the proportional valve (10), and the load-holding function is effected in the non-actuated switching position (20) of the switching valve (18) and in the zero position (14) of the proportional valve (10).
6. Control device (1) according to any one of claims 1 to 5, characterized in that the regulating electronics and the power electronics for controlling the proportional valve (10) are mounted directly on the proportional valve (10).
7. A control device (1) according to any one of claims 1 to 6, characterised in that one or both working lines (4, 6) of the two working lines (4, 6) can be connected to a pressure medium tank via a pressure regulating valve (30, 31).
8. The control device (1) according to any one of claims 1 to 7, characterised in that a pressure sensor (28, 29) is arranged in one or both working lines (4, 6) of the two working lines (4, 6).
9. A control device (1) according to any one of claims 1 to 8, characterised in that the control device has a stroke measuring sensor (7) for detecting the position of the actuator (2) and the proportional valve (10) has an input for the signal of the stroke measuring sensor (7).
10. Control device (1) according to any one of claims 1 to 9, characterized in that the proportional valve (10) has a second stroke measuring sensor (16) for detecting the position of the control piston of the proportional valve (10).
CN202210916157.3A 2021-08-02 2022-08-01 Hydraulic control device Pending CN115701492A (en)

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DE102021208330.7 2021-08-02
DE102021208330.7A DE102021208330B3 (en) 2021-08-02 2021-08-02 Hydraulic control arrangement

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009001137A (en) * 2007-06-21 2009-01-08 Shin Meiwa Ind Co Ltd Cargo handling device for container cargo handling vehicle
DE102016106616B4 (en) 2016-04-11 2023-07-06 Schwing Gmbh Electrohydraulic control circuit for a large manipulator
DE102018004769A1 (en) * 2018-06-13 2019-12-19 Hydac Mobilhydraulik Gmbh control device
JP6859411B2 (en) * 2019-09-26 2021-04-14 古河ユニック株式会社 Speed-up valve device

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EP4130493A1 (en) 2023-02-08
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