EP2881594A1 - Hydraulic control assembly - Google Patents
Hydraulic control assembly Download PDFInfo
- Publication number
- EP2881594A1 EP2881594A1 EP14190832.7A EP14190832A EP2881594A1 EP 2881594 A1 EP2881594 A1 EP 2881594A1 EP 14190832 A EP14190832 A EP 14190832A EP 2881594 A1 EP2881594 A1 EP 2881594A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fluid flow
- valve
- flow path
- metering orifice
- pressure
- 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
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- 239000012530 fluid Substances 0.000 claims abstract description 119
- 238000001514 detection method Methods 0.000 claims abstract description 68
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 18
- 230000001276 controlling effect Effects 0.000 claims abstract description 10
- 230000001105 regulatory effect Effects 0.000 claims abstract description 8
- 238000006073 displacement reaction Methods 0.000 claims description 34
- 230000000903 blocking effect Effects 0.000 claims 1
- 230000007935 neutral effect Effects 0.000 description 14
- 238000010586 diagram Methods 0.000 description 8
- 230000011664 signaling Effects 0.000 description 6
- 238000011982 device technology Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
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Classifications
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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
- F15B11/16—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
- F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
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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
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- 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
- 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
- F15B13/028—Shuttle valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—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
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
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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
- 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
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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
- 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
- F15B2211/40—Flow control
- F15B2211/455—Control of flow in the 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6058—Load sensing circuits with isolator 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—Methods of control of the load sensing pressure
- F15B2211/652—Methods of control of the load sensing pressure the load sensing pressure being different from the load pressure
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/85978—With pump
- Y10T137/85986—Pumped fluid control
Definitions
- the invention is based on a hydraulic control arrangement according to the preamble of claim 1.
- a control arrangement which is designed in the form of a load-sensing (LS) control.
- LS load-sensing
- the highest load pressure is reported to a variable displacement pump and regulated so that in a pump line there is a pump pressure lying by a certain pressure difference Ap over the load pressure.
- Adjustable metering orifices of the LS control for the consumers are assigned to individual pressure balances, which also maintain a constant pressure difference via the metering orifices of the load-pressure-lower hydraulic consumers.
- the individual pressure compensators are arranged upstream of the metering orifices and throttle the fluid flow between the pump line and the metering orifices so strongly that the pressure upstream of the metering orifices is independent of the pump pressure only by a certain pressure difference above the individual load pressure.
- the load pressure-highest consumer slows down because the pump pressure applied by its metering orifice drops and thus the pressure difference across this metering orifice becomes smaller.
- the invention has for its object to provide a hydraulic control arrangement which corresponds in particular functionally about the LS control and / or the LUDV control, which is simple in design, has a low space requirement, has low energy requirements and is inexpensive.
- a hydraulic control arrangement for consumers has a metering orifice for a respective consumer for controlling a quantity of fluid flow from a hydraulic pump to the respective consumer.
- a respective metering orifice is fluidly connected to the input side of the hydraulic pump, in particular directly or indirectly via at least one further valve.
- On the output side of a respective metering orifice a respective consumer is provided.
- a respective metering orifice is assigned a respective detection orifice.
- the detection apertures are arranged fluidly in series. Via the detection apertures, a flow-sensing (FS) fluid flow path extends from the hydraulic pump. The FS fluid flow path is thus connectable to the hydraulic pump upstream of the detection apertures.
- FS flow-sensing
- the fluid flow path then ends at a control device, in particular downstream of the detection apertures.
- the control device serves to control a size of a fluid flow from the hydraulic pump to the metering orifices.
- a respective detection orifice is designed in such a way that when it falls below a certain pressure difference above a respective metering orifice (undersupply), it blocks or controls the FS-fluid flow path.
- the detection diaphragm assigned to the metering orifice opens or controls the FS fluid flow path.
- the control device of the hydraulic pump for controlling the fluid flow from the hydraulic pump to the consumers or to the metering orifices can advantageously be influenced. In particular, it can thus be recognized by the control device with the FS fluid flow path, whether there is an insufficient supply.
- the FS fluid flow path thus serves to transmit an FS signal.
- This solution has the advantage that the control device of the hydraulic pump for controlling the fluid flow no longer uses the highest load pressure, as in the prior art described above, but makes the control of the hydraulic pump of the FS fluid flow path dependent, so whether it is open or closed is. If it is open, that is to say all detection apertures arranged fluidly in series are open, then there is no undersupply of an orifice or of a consumer. If, on the other hand, a detection orifice is closed, then the FS fluid flow path is blocked and the control device can, for example, control the hydraulic pump such that the undersupply of the metering orifices is counteracted.
- the FS fluid flow path influences the control device in such a way that blockage or injection of the FS fluid flow path through at least one of the detection diaphragms results in a hearing of the fluid flow from the hydraulic pump to the consumers.
- An opening or control of the FS fluid flow path through all the detection apertures advantageously results in a reduction of the fluid flow from the hydraulic pump to the consumers.
- a respective detection panel may have a valve element.
- the valve element is in this case preferably acted upon in the opening direction by the pressure medium upstream of its associated metering orifice and in the closing direction by the pressure medium downstream of its associated metering orifice and additionally by a spring force of a, in particular adjustable, detection spring.
- the spring force of the detection spring of the detection aperture advantageously determines the pressure difference at which the valve slide of the detection aperture is actuated in the direction of the closed position.
- control device may preferably be provided a pump control for adjusting a delivery volume of the hydraulic pump designed as a variable displacement pump.
- control device is an inlet pressure compensator designed as a fixed displacement pump.
- the pump control has the advantage that the variable displacement pump can be swung back when the FS fluid flow path is open, and thus there is no undersupply at the metering orifices. If, however, the FS fluid flow path is blocked, then the variable displacement pump can be pivoted by the pump control in the direction of increasing the delivery volume. It is conceivable that due to the FS fluid flow path, the control device may be formed without a volumetric flow regulator.
- a respective metering orifice may be formed as a continuously adjustable directional control valve. This can lock in a neutral position, a pressure fluid connection between the associated consumer and the hydraulic pump and alsêtn in switching positions a pressure medium connection between the associated consumer and the hydraulic pump. With the directional valve thus an opening cross-section is adjustable.
- a respective metering orifice is associated with an individual pressure compensator. This is preferably used to maintain an approximately constant pressure difference across the metering orifice.
- a respective individual pressure compensator is provided in addition to a respective detection panel additionally a respective individual pressure compensator is provided.
- the individual pressure compensator can be upstream or downstream of the metering orifice.
- At least one individual pressure compensator together with the associated detection aperture is designed as an individual valve with a common valve element.
- all individual pressure compensators are formed with their associated detection apertures as individual valves. This has the advantage that device technology simple and inexpensive only one valve must be used.
- the individual valve may advantageously be upstream or downstream of the metering orifice.
- the valve element of a respective individual valve is designed as a valve slide.
- This can have a basic position and, starting from this, be displaceable in the direction of first switching positions. Furthermore, it can be displaceable in the direction of second switching positions which adjoin the first switching positions.
- the valve spool can advantageously fulfill the functions of the detection panel and the individual pressure compensator.
- the FS fluid flow path may be opened and locked in the home position.
- a pressure medium connection between the hydraulic pump and the consumer can be controlled. In the first switching positions, the pressure medium connection between the hydraulic pump and the consumer can then be throttled or completely open.
- the pressure medium connection between the hydraulic pump and the consumer is then preferably completely opened.
- the pressure difference across the metering orifice is controlled by the individual valve in the first and second switching positions, in which the FS fluid flow path is completely open.
- the pump control can swing back the swivel pump.
- the valve element of the individual valve is in the basic position, wherein the FS fluid flow path is blocked and the pressure medium connection from the hydraulic pump to the metering orifice or to the consumer is completely opened.
- the pump control can in this case then pivot the variable displacement pump in the direction of an increased delivery volume.
- the valve slide of the individual valve of the highest-load consumer can preferably be positioned in the region of its first switching positions in the adjusted mode, since no excess pressure is provided by the hydraulic pump, in contrast to the prior art. This leads to an energy saving, since a control reserve for so-called extreme situations is no longer necessary.
- valve element in a further embodiment of the individual valve, can be acted upon in the direction of the basic position by the spring force of the detection spring and the pressure medium downstream of the associated metering orifice. In the direction of the first and second switching positions, the valve element may be acted upon by the pressure medium upstream of the associated metering orifice.
- control arrangement may be formed with an individual pressure compensator downstream of the metering orifice.
- an FS fluid flow path can be provided in a control arrangement, which is in principle designed as LUDV control arrangement.
- a respective metering orifice an individual pressure compensator with a valve spool.
- This can lock in a basic position, a pressure medium connection between the metering orifice and the associated consumer and aufêtn starting from the basic position in the direction of first switching positions the pressure medium connection between the metering orifice and the associated consumer throttled.
- the valve switch can continue to control the pressure medium connection between the metering orifice and the associated consumer in the direction of second switching positions.
- valve spool of a respective individual pressure compensator of the further embodiment can also be acted upon in the direction of the first and second switching positions by the pressure medium downstream of the metering orifice and in the direction of the basic position of the highest load pressure of the consumer.
- the individual pressure compensators of the further preferred embodiment can be connected to a common LS line.
- the valve spool of a respective individual pressure compensator can then connect the LS line throttled in the second switching positions with a consumer line connected to the consumer downstream of the metering orifice.
- the valve spool In the first switching positions and in the basic position, the valve spool can block or control the connection between the LS line and the consumer line.
- the valve spool can be acted upon in the direction of the basic position via the LS line from the highest load pressure of the consumer.
- the pump control may preferably have an adjusting cylinder for adjusting the delivery volume of the variable.
- the adjusting cylinder is preferably regulated via a control valve.
- a piston of the adjusting cylinder can further limit a cylinder space which can be charged to reduce the delivery volume of the variable displacement pump with pressure medium.
- pressure medium can be discharged from the cylinder space.
- the cylinder chamber is in particular directly connected to the FS fluid flow path, in particular throttled.
- the control valve may have a valve slide, which is acted upon by a, in particular adjustable, valve spring with a spring force in the direction of a basic position. In the direction of switching positions, it can be acted upon with pressure medium of an output side of the hydraulic pump and thus with a pump pressure.
- a pressure medium connection between the FS fluid flow path and the cylinder space is preferably controlled and directed between the output side of the hydraulic pump and the cylinder chamber.
- the pressure medium connection between the FS fluid flow path and the cylinder chamber can be controlled and controlled between the output side of the hydraulic pump and the cylinder chamber.
- the FS fluid flow path is connected via a throttle to a tank, whereby a defined pressure prevails in the FS fluid flow path even with a closed detection orifice.
- the hydraulic control arrangement may be provided in a valve block. It is conceivable that the valve block is formed from valve disks, wherein in a respective valve disk, the valves are provided for a respective consumer.
- the hydraulic control arrangement 1 has a valve block 2, which has valve disks 4, 6 and 8.
- a respective valve disk 4 to 8 has two working ports A, B for connecting a hydraulic consumer, such as a hydraulic cylinder on.
- the valve discs 4 to 8 are in this case configured the same and each have a metering orifice 10 and an individual valve 12.
- a respective individual valve 12 in this case forms an individual pressure compensator, which is connected upstream of the respective metering orifice 10, and a detection diaphragm according to the invention.
- the design of the metering orifices 10 will be explained with reference to the valve disk 4.
- the metering orifice 10 is designed as a continuously adjustable 5/4-way valve.
- a valve spool of the metering orifice 10 is spring-centered in a neutral position 0.
- the valve slide can be adjusted starting from the neutral position 0 in the direction of a first switching position a or in the opposite direction starting from the neutral position 0 in the direction of second switching positions b. If the valve spool is moved further, starting from the second switching positions b, then it arrives in free or floating positions c.
- In the first switching positions a is a pressure medium connection between a supply line 16 extending from an in FIG.
- the individual valve 12 is also explained in more detail with reference to the valve disk 4. It is designed as a continuously adjustable 4/3-way valve. Via a detection spring 30, a valve spool is acted upon in the direction of a basic position 0 with a spring force. Starting from the basic position 0, it is displaceable in the direction of first shift positions a. Subsequent to the switching positions a, it is displaceable in the direction of second switching positions b.
- a flow-sensing (FS) fluid flow path 32 extends across the individual valves 10 of the valve discs 4 through 8. Regarding this FS fluid flow path 32, the individual valves 12 are in series arranged.
- the FS fluid flow path 32 is blocked and opened in the first and second switching positions a, b.
- the FS fluid flow path 32 is only opened when all valve spools of the individual valves 12 are not in their neutral position 0. If, on the other hand, one of the valve spools or several of the valve spools of the individual valves 12 is in the basic position 0, the FS fluid flow path 32 is blocked.
- the FS fluid flow path 32 is seen upstream of the individual valves 12 connected to the supply line 16 and extends through the individual valve 12 of the valve disc 8 to the individual valve 12 of the valve disc 6 and from here to the individual valve 12 of the valve disc 4. Downstream of the last individual valve 12 of Valve disk 4, the FS fluid flow path 32 is then connected to a pump control, not shown, designed as a variable displacement hydraulic pump.
- valve spool of a respective individual valve 12 is, as already explained above, acted upon by the spring force of the detection spring 30 in the direction of the basic position 0.
- the valve spool via a control line 34 from the pressure medium of Supply line 16 downstream of the individual valve 12 and upstream of the metering orifice 10 acted upon.
- the FS fluid flow path 32 is blocked and the supply line 16 to the metering orifice 10 is completely opened.
- the FS fluid flow path 32 is opened and the feed line 16 to the metering orifice is likewise completely open.
- the FS fluid flow path 32 is then opened again and the feed line 16 to the metering orifice 10 is blocked.
- the inventive hydraulic control arrangement according to FIG. 1 differs from conventional LS control arrangements, in particular by the fact that the FS fluid flow path 32 is provided, which is up and steuste of the detection orifices of the individual valves 12.
- the FS fluid flow path 32 thus serves to transmit an FS signal, which is explained below, which is why a message of a load pressure, for example via LS reporting lines and a Shuttle valve cascade is reported to a pump control is no longer necessary.
- the individual valves 12 are provided which, in contrast to individual pressure compensators, have an additional control edge for controlling the FS fluid flow path.
- variable displacement pump not shown
- the valve spools of the individual valves 12 are arranged in the second switching position b, whereby the FS fluid flow path 32 is opened.
- This pressure medium is then forwarded from the supply line 16 to the pump control of the variable, which serves as an FS signal.
- the FS fluid flow path 32 interacts with the pump control in such a way that when the FS fluid flow path 32 is open (FS signal open), the variable displacement pump pivots back.
- the metering orifice 10 of the valve disc 8 is in its second switching position b, whereby a connected to the working ports A, B of the valve disc 8 consumer is supplied with pressure medium via the supply line 16.
- the individual valves 12 of the valve disks 4 and 6 are in the second switching position b. If the load connected to the valve disk 8 is now in undersupply, that is to say the pressure difference across the metering orifice 10 is below a predetermined pressure difference, then the valve slide of the individual valve 12 of the valve disk 8 is moved into the basic position 0.
- the FS fluid flow path 32 is therefore blocked by the individual valve 12 of the valve disc 8. There is thus no pressure fluid from the supply line 16 via the FS fluid flow path 32 for pump control.
- the FS fluid flow path 32 interacts with the pump regulation such that in this case the variable displacement pump is pivoted in the direction of increasing the delivery volume.
- the individual valve 12 of the valve disk 8 is completely or almost completely opened with respect to the feed line 16 to the metering orifice 10, for which reason it has minimal hydraulic losses, in contrast to a conventional LS control arrangement from the prior art.
- valve spool of the individual valve 12 of the valve disk 8 is moved into its first switching position a.
- the FS fluid flow path 32 is thus opened again and at the same time the supply line 16 to the metering orifice 10 of the valve disc 8 is fully or almost completely opened, which in turn leads to minimal hydraulic losses.
- the pivot pump is swung back again.
- both the valve spool of the metering orifice 10 of the valve disc 6 and the valve spool of the metering orifice 10 of the valve disc 8 are located, for example, in the second switching positions b.
- the pressure difference of the metering orifices 10 of the valve disks 6 and 8 are in this case adjusted via the individual valves 12.
- the consumer connected to the valve disk 6 should be the highest-load consumer, which is why the individual valve 12 of the valve disk 6 controls the FS fluid flow path 32.
- his valve spool is in the home position 0 or in the first switching position a.
- variable displacement pump is controlled with the pump control so that the required pressure difference is applied to the metering orifice 10.
- the connection in the first valve disc 6 between the supply line 16 and the metering orifice 10 is thus completely open, which leads to minimal hydraulic losses.
- the other individual valve 12 of the valve disc 8 with the load pressure-lower consumer then regulates the pressure difference across the metering orifice 10 of the valve disc 8 in a conventional manner by its valve slide in the switching positions a or b.
- the FS fluid flow path 32 is thus completely opened via the individual valve 12 of the valve disc 8.
- each individual valve 12 signals the FS signal via the FS fluid flow path 32 when the associated metering orifice 10 is not undersupplied. If there is no overall shortage, the FS signal is reported via the open FS fluid flow path 32 to the pump control, which pivots back the variable displacement pump accordingly. If only one hydraulic consumer is used, then For example, the individual valve 12 associated therewith is used to control the FS fluid flow path 32 and thus adjust the pump pressure to control the variable displacement pump. If several consumers are operated, then the individual valve 12 of the load-pressure-highest consumer is used to control the FS fluid flow path 32 and thus to control the variable displacement pump and the remaining individual valves 12 are used as conventional individual pressure compensators.
- FIG. 2 a further illustration of the hydraulic control arrangement 1 is shown.
- the valve discs 4, 6 and 8 are shown here as blocks. They serve as placeholders for those in the Figures 3 - 6 illustrated sections 36 of hydraulic control assemblies 1 different embodiments.
- hydraulic consumers 38 are shown by way of example. These are differential cylinders, which are each connected to the working ports A, B of the valve disks 4-8.
- variable displacement pump 40 with a pump control 42 shown.
- This has an adjusting cylinder 44 with a piston 46.
- the piston 46 can be acted upon via the cylinder chamber 48 with pressure medium in the direction of pivoting back of the variable displacement pump 40.
- the piston 46 is acted upon by a spring force of a spring 50.
- the pump control 42 further includes a control valve 52 which is designed as a continuously adjustable 3/2-way valve.
- a valve spool is acted upon in the direction of a basic position 0 with a spring force of an adjustable valve spring 54.
- the valve spool can be acted upon via a control line 56 from the pressure medium in the supply line 16, wherein the supply line 16 is connected on the output side to the variable displacement pump 40.
- a pressure medium connection between the FS fluid flow path 32 and the cylinder chamber 48 of the adjusting cylinder 44 is opened by the control valve 52.
- this connection is controlled and, on the other hand, a pressure medium connection between the supply line 16 and the cylinder chamber 48 is opened.
- the FS fluid flow path 32 is in this case downstream of in FIG. 2 Not shown detection aperture connected to the control valve 52. Further, extending from the FS fluid flow path 32 downstream of the in FIG.
- a branch line 58 which is connected via a throttle 60 directly to the cylinder chamber 48.
- a further throttle 62 is provided, via which the branch line 58 and thus the FS fluid flow path 32 is connected to a tank 64.
- FIG. 3 the section 36 of a second embodiment of the control arrangement 1 is shown.
- the section 36 for the valve discs 4-8 provided.
- the metering orifice 10 is in contrast to the embodiment of FIG. 1 designed as a 6/3-way valve.
- a valve spool of the metering orifice 10 is spring-centered in a neutral position 0. Starting from the neutral position 0, it is displaceable in the direction of the first shift positions a. Conversely, it is displaceable starting from the neutral position 0 in the direction of second switching positions b.
- the feed line 16 is connected via the metering orifice 10 to a connecting line 66, which in turn is connected in the first switching position a via the metering orifice 10 to the working line 18 for the working connection A.
- the working line 20 for the working connection B is connected to the drainage line 22.
- the second switching positions b the supply line 16 is again connected via the metering orifice 10 with the connecting line 66, which is then further connected via the metering orifice 10 with the working line 20 for the working port B.
- the working line 18 is then connected to the drain line 22.
- the individual valves 12 in their function as individual pressure balances regulate the pressure difference across the associated metering orifice such that it remains essentially the same and corresponds to a pressure equivalent of the spring force of the detection spring 30. If the fluid flow conveyed by the variable-displacement pump 40 is no longer sufficient, with which at least one metering orifice 10 is undersupplied, then the valve spool of that individual valve 12 is displaced in the direction of its basic position 0, whose metering orifice 10 is undersupplied. The valve spool of the individual valve 12 is thus moved to its normal position 0 when the pressure difference of the associated metering orifice 10 is less than the pressure equivalent of the detection spring 30. The FS fluid flow path 32 is thus disabled.
- FS fluid flow path 32 is then connected to tank 64 via branch line 58.
- the control valve 52 then regulates a delivery pressure of the variable displacement pump 40 to the value set by the valve spring 54, which in particular corresponds to the maximum permissible delivery pressure. This in turn leads to an increase in the delivery volume of the variable displacement pump 40 until there is no shortage of supply.
- valve spool of a metering orifice 10 in the neutral position 0 the valve spool of the associated individual valve 12 is moved to its second switching position b.
- the FS fluid flow path 32 is this individual valve 12 is open.
- a delivery volume of the variable displacement pump 40 is adjusted to the lowest possible value, so that energy losses are at a standstill of the consumer 38 as low as possible.
- FIG. 4 shows a portion 36 of a hydraulic control assembly 1 according to a third embodiment.
- a respective individual valve 12 of the metering orifice 10 downstream The individual valve 12 is arranged in the connecting line 66.
- the connecting line 66 In the basic position 0 of the individual valve 12, the connecting line 66 is completely opened. In the first switching position a, however, the connecting line 66 is throttled open and closed in the switching position b.
- the FS fluid flow path 32 is controlled by the individual valve 12 according to the first and second embodiments.
- the valve spool of the individual valve 12 is pressurized via the branch line 24, which branches off from the connecting line 66 between the individual valve 12 and the metering orifice 10, with pressure medium in the direction of the basic position 0. In the opposite direction, it is acted upon by pressure medium via the control line 34, which branches off from the feed line 16 upstream of the metering orifice 10.
- An operation of the control arrangement according to FIG. 4 essentially corresponds to the operation of the control arrangement according to FIG. 3 ,
- FIG. 5 is the section 36 of the control arrangement 1 from FIG. 2 shown according to a fourth embodiment.
- This is based on a LUDV control arrangement with downstream individual pressure compensator.
- the metering orifice 10 is corresponding to the Figures 3 and 4 educated.
- an individual pressure compensator 68 and a detection diaphragm 70 are now provided separately from one another.
- the individual pressure compensator 68 is in this case arranged in the connecting line 66. It is designed as a continuously adjustable 3/3-way valve.
- the valve spool of the individual pressure compensator 68 can be brought into a basic position 0 here. Starting from this, it is displaceable in the direction of first switching positions a and subsequently further in the direction of second switching positions b.
- a Load pressure signaling line 72 connected to the individual pressure compensator 68. From this branches off a control line 74, which acts on the valve spool of the individual pressure compensator 68 with pressure medium in the direction of its basic position 0. In the opposite direction of the valve spool is acted upon via a control line 76 with pressure medium, which branches off from the connecting line 66 between the metering orifice 10 and the individual pressure compensator 68.
- the connecting line 66 In its first switching positions a of the individual pressure compensator 68, the connecting line 66 is opened throttled. In the second switching positions b, the connecting line 66 is completely opened and additionally the load pressure signaling line 72 throttled connected to the connecting line 66.
- the connecting line 66 is controlled and the load pressure signaling line 72 separated from it.
- the individual pressure compensators 68 of the valve discs 4 to 8 off FIG. 2 thus sharing the load pressure signaling line 72, see also FIG. 2 , in which then the highest load pressure is applied.
- the detection panel 70 is designed as a 2/2-way valve.
- a valve slide of the detection panel 70 is acted upon in the direction of a basic position 0 by the spring force of the detection spring 30. Starting from the basic position 0, it can be adjusted counter to the spring force in the direction of a switching position a.
- the valve spool In addition to the spring force of the valve spool is acted upon in the direction of its basic position 0 via a control line 78 from the pressure medium of the connecting line 66 between the metering orifice 10 and the individual pressure compensator 68.
- the valve spool via a control line 80 from the pressure medium of the supply line 16 upstream of the metering orifice 10 can be acted upon.
- the detection panel 70 blocks the FS fluid flow path 32.
- the switching position a of the FS fluid flow path 32 is open.
- the control arrangement is in accordance with FIG. 2 in synopsis with FIG. 5 used in the usual way.
- the FS fluid flow path 32 is then opened via the detection panel 70.
- the detection panel 70 closes the FS fluid flow path 32, with which in turn the variable displacement pump 40 according to the embodiments FIG. 3 and 4 their delivery volume increased. Without the detection panel 70, the variable displacement 40 would a sub-supply no information about a too low fluid flow received.
- the individual pressure compensator 68 which is assigned to the load-pressure-highest consumer, is in accordance with the embodiment FIG. 5 completely open, resulting in low energy losses according to the previous embodiments.
- a further embodiment of a control arrangement 1 shows the section 36 according to FIG. 6 in synopsis with FIG. 2 ,
- the metering orifice 10 is in this case accordingly FIG. 3 educated.
- the detection panel 70 is corresponding FIG. 5 educated.
- the valve spool of the detection valve 70 is acted upon in the direction of the basic position 0 by the pressure medium of the connecting line 66 by a control line 82 branches off from this.
- the opposite direction of the valve spool is acted upon by the pressure medium of the supply line 16 upstream of the metering orifice 10 via a control line 84 branching off therefrom.
- variable displacement 40 off FIG. 2 is then adjusted in the direction of increasing a delivery volume.
- a hydraulic control arrangement for a plurality of consumers.
- a metering orifice for controlling a fluid flow is provided.
- a respective metering orifice is assigned a detection aperture.
- the detection apertures are arranged fluidly in series.
- a flow-sensing (FS) fluid flow path extends over the detection apertures. Upstream of the detection apertures, the fluid flow path is connected to a hydraulic pump and downstream of the detection apertures to a control device of the hydraulic pump. If a consumer is under-supplied with pressure medium, the corresponding detection panel closes the flow-sensing fluid flow path. In this case, the regulating device interacts with this FS fluid flow path in such a way that the fluid flow from the hydraulic pump is thereby increased. If none of the consumers are undersupplied, then the FS fluid flow path is Fully opened via the detection panels and the control device reduces the fluid flow from the hydraulic pump.
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Abstract
Offenbart ist eine hydraulische Steueranordnung für eine Mehrzahl von Verbrauchern (38). Für einen jeweiligen Verbraucher ist hierbei eine Zumessblende (10) zum Steuern eines Fluidstroms vorgesehen. Einer jeweiligen Zumessblende ist eine Detektionsblende (12,70) zugeordnet. Die Detektionsblenden sind dabei fluidisch in Reihe angeordnet. Ein Flow-Sensing (FS)- Fluidströmungspfad (32) erstreckt sich hierbei über die Detektionsblenden. Stromaufwärts der Detektionsblenden ist der Fluidströmungspfad mit einer Hydropumpe (40) und stromabwärts der Detektionsblenden mit einer Regelvorrichtung (42) der Hydropumpe verbunden. Ist ein Verbraucher mit Druckmittel unterversorgt, so schließt die entsprechende Detektionsblende den Flow-Sensing-Fluidströmungspfad. Die Regelvorrichtung wirkt hierbei derart mit diesem FS-Fluidströmungspfad zusammen, dass der Fluidstrom von der Hydropumpe hierdurch erhöht wird. Ist keiner der Verbraucher unterversorgt, so ist der FS-Fluidströmungspfad über die Detektionsblenden vollständig geöffnet und die Regelvorrichtung vermindert den Fluidstrom von der Hydropumpe.Disclosed is a hydraulic control arrangement for a plurality of consumers (38). For a respective consumer in this case a metering orifice (10) is provided for controlling a fluid flow. A respective metering orifice is assigned a detection diaphragm (12, 70). The detection apertures are arranged fluidly in series. A flow sensing (FS) fluid flow path (32) extends over the detection apertures. Upstream of the detection apertures, the fluid flow path is connected to a hydraulic pump (40) and downstream of the detection apertures to a control device (42) of the hydraulic pump. If a consumer is under-supplied with pressure medium, the corresponding detection panel closes the flow-sensing fluid flow path. In this case, the regulating device interacts with this FS fluid flow path in such a way that the fluid flow from the hydraulic pump is thereby increased. If none of the consumers are undersupplied, the FS fluid flow path is fully opened via the detection apertures and the control device reduces the fluid flow from the hydraulic pump.
Description
Die Erfindung geht aus von einer hydraulischen Steueranordnung gemäß dem Oberbegriff des Anspruchs 1.The invention is based on a hydraulic control arrangement according to the preamble of
Aus der
Bei dieser LS-Steuerung erfolgt eine Meldung eines höchsten Lastdrucks an eine Pumpenregelung der Verstellpumpe üblicherweise über LS-Meldeleitungen, die über eine Wechselventilkaskade miteinander verbunden sind. Dies verursacht einen erheblichen vorrichtungstechnischen Aufwand, hat einen hohen Bauraumbedarf und ist kostenintensiv. Damit bei diesen LS-Steuerungen ein ausreichendes Regeldruckgefälle an den Zumessblenden vorliegt, ist es erforderlich, an den Individualdruckwaagen durch die Verstellpumpe ein erhöhtes Regeldruckgefälle vorzusehen, um insbesondere Einflüsse auf den Fluidstrom aufgrund von Temperaturänderungen oder aufgrund von Durchflusswiderständen ausgleichen zu können. Durch das Regeldruckgefälle liegt in allen Betriebszuständen an den Zumessblenden eine ausreichende Druckdifferenz vor.In this LS control, a message of a highest load pressure to a pump control of the variable displacement pump usually via LS-reporting lines, which are connected to each other via a shuttle valve cascade. This causes a considerable device complexity, has a high space requirement and is costly. In order for these LS controls to have a sufficient control pressure gradient across the metering orifices, it is necessary to provide an increased regulating pressure gradient on the individual pressure compensators by means of the variable displacement pump in order to be able to compensate in particular for influences on the fluid flow due to temperature changes or due to flow resistances. Due to the control pressure gradient, there is a sufficient pressure difference in all operating states at the metering orifices.
Aus dem Datenblatt RD 66 134 der Firma Rexroth ist ein hydraulischer Schaltplan der vorstehend erläuterten LS-Steuerung aufgezeigt.From the
Die Druckschrift
In dem Datenblatt RD 64 125 der Firma Rexroth ist ein hydraulischer Schaltplan gattungsgemäßen LUDV-Steuerung offenbart.In the
Aus der
Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine hydraulische Steueranordnung zu schaffen, die insbesondere funktional etwa der LS-Steuerung und/oder der LUDV-Steuerung entspricht, die einfach ausgestaltet ist, einen geringen Bauraumbedarf hat, einen geringen Energiebedarf aufweist und kostengünstig ist.In contrast, the invention has for its object to provide a hydraulic control arrangement which corresponds in particular functionally about the LS control and / or the LUDV control, which is simple in design, has a low space requirement, has low energy requirements and is inexpensive.
Diese Aufgabe wird gelöst mit einer hydraulischen Steueranordnung gemäß den Merkmalen des Anspruchs 1.This object is achieved with a hydraulic control arrangement according to the features of
Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous developments of the invention are the subject of further subclaims.
Erfindungsgemäß ist eine hydraulische Steueranordnung für Verbraucher vorgesehen. Diese hat für einen jeweiligen Verbraucher eine Zumessblende zum Steuern einer Größe eines Fluidstroms von einer Hydropumpe zu dem jeweiligen Verbraucher. Eine jeweilige Zumessblende ist hierfür eingangsseitig mit der Hydropumpe, insbesondere direkt oder indirekt über zumindest ein weiteres Ventil, fluidisch verbunden. Ausgangsseitig einer jeweiligen Zumessblende ist ein jeweiliger Verbraucher vorgesehen. Vorteilhafterweise ist einer jeweiligen Zumessblende eine jeweilige Detektionsblende zugeordnet. Die Detektionsblenden sind hierbei fluidisch in Reihe angeordnet. Über die Detektionsblenden erstreckt sich ein Flow-Sensing (FS)-Fluidströmungspfad ausgehend von der Hydropumpe. Der FS-Fluidströmungspfad ist somit stromaufwärts der Detektionsblenden mit der Hydropumpe verbindbar. Der Fluidströmungspfad endet dann bei einer Regelvorrichtung, insbesondere stromabwärts der Detektionsblenden. Die Regelvorrichtung dient hierbei zur Regelung einer Größe eines Fluidstroms von der Hydropumpe zu den Zumessblenden. Eine jeweilige Detektionsblende ist derart ausgestaltet, dass sie bei Unterschreiten einer bestimmten Druckdifferenz über einer jeweiligen Zumessblende (Unterversorgung) den FS-Fluidströmungspfad sperrt oder zusteuert. Bei Erreichen oder Überschreiten der bestimmten Druckdifferenz (Normalversorgung) öffnet die der Zumessblende zugeordnete Detektionsblende den FS-Fluidströmungspfad oder steuert diesen auf. Mit dem FS-Fluidströmungspfad ist vorteilhafterweise die Regelvorrichtung der Hydropumpe zur Steuerung des Fluidstroms von der Hydropumpe zu den Verbrauchern bzw. zu den Zumessblenden beeinflussbar. Insbesondere kann mit dem FS-Fluidströmungspfad somit von der Regelvorrichtung erkannt werden, ob eine Unterversorgung vorliegt. Der FS- Fluidströmungspfad dient somit zur Übertragung eines FS-Signals.According to the invention, a hydraulic control arrangement for consumers is provided. This has a metering orifice for a respective consumer for controlling a quantity of fluid flow from a hydraulic pump to the respective consumer. A respective metering orifice is fluidly connected to the input side of the hydraulic pump, in particular directly or indirectly via at least one further valve. On the output side of a respective metering orifice a respective consumer is provided. Advantageously, a respective metering orifice is assigned a respective detection orifice. The detection apertures are arranged fluidly in series. Via the detection apertures, a flow-sensing (FS) fluid flow path extends from the hydraulic pump. The FS fluid flow path is thus connectable to the hydraulic pump upstream of the detection apertures. The fluid flow path then ends at a control device, in particular downstream of the detection apertures. The control device serves to control a size of a fluid flow from the hydraulic pump to the metering orifices. A respective detection orifice is designed in such a way that when it falls below a certain pressure difference above a respective metering orifice (undersupply), it blocks or controls the FS-fluid flow path. When the specified pressure difference (normal supply) is reached or exceeded, the detection diaphragm assigned to the metering orifice opens or controls the FS fluid flow path. With the FS fluid flow path, the control device of the hydraulic pump for controlling the fluid flow from the hydraulic pump to the consumers or to the metering orifices can advantageously be influenced. In particular, it can thus be recognized by the control device with the FS fluid flow path, whether there is an insufficient supply. The FS fluid flow path thus serves to transmit an FS signal.
Diese Lösung hat den Vorteil, dass die Regelvorrichtung der Hydropumpe zur Steuerung des Fluidstroms nicht mehr den höchsten Lastdruck, wie im eingangs erläuterten Stand der Technik, verwendet, sondern die Steuerung der Hydropumpe von dem FS-Fluidströmungspfad abhängig macht, also ob dieser geöffnet oder geschlossen ist. Ist er geöffnet, dass heißt alle fluidisch in Reihe angeordneten Detektionsblenden sind geöffnet, so liegt keine Unterversorgung einer Zumessblende bzw. eines Verbrauchers vor. Ist dagegen eine Detektionsblende geschlossen, so ist der FS-Fluidströmungspfad gesperrt und die Regelvorrichtung kann beispielsweise die Hydropumpe derart steuern, dass der Unterversorgung der Zumessblenden entgegengewirkt wird.This solution has the advantage that the control device of the hydraulic pump for controlling the fluid flow no longer uses the highest load pressure, as in the prior art described above, but makes the control of the hydraulic pump of the FS fluid flow path dependent, so whether it is open or closed is. If it is open, that is to say all detection apertures arranged fluidly in series are open, then there is no undersupply of an orifice or of a consumer. If, on the other hand, a detection orifice is closed, then the FS fluid flow path is blocked and the control device can, for example, control the hydraulic pump such that the undersupply of the metering orifices is counteracted.
Somit kann bei der erfindungsgemäßen hydraulischen Steueranordnung auf LS-Meldeleitungen und auf eine Wechselventilkaskade, wie sie bei der eingangs im Stand der Technik erläuterten Steueranordnungen vorgesehen ist, entfallen. Dies führt zu einer Verringerung eines vorrichtungstechnischen Aufwands und zu einer Verringerung eines Bauraumbedarfs. Hierdurch werden Kosten gesenkt. Des Weiteren weist die erfindungsgemäße hydraulische Steueranordnung vergleichsweise geringe Energieverluste auf.Thus, in the hydraulic control arrangement according to the invention on LS reporting lines and on a shuttle valve cascade, as provided in the initially described in the prior art control arrangements omitted. This leads to a reduction of a device-technical effort and to a reduction of space requirements. This will reduce costs. Furthermore, the hydraulic control arrangement according to the invention has comparatively low energy losses.
In weiterer Ausgestaltung der Erfindung beeinflusst der FS-Fluidströmungspfad derart die Regelvorrichtung, dass eine Sperrung oder Zusteuerung des FS-Fluidströmungspfads durch zumindest eine der Detektionsblenden zu einer Erhörung des Fluidstroms von der Hydropumpe zu den Verbrauchern führt. Eine Öffnung oder Aufsteuerung des FS-Fluidströmungspfads durch alle Detektionsblenden führt wiederum vorteilhafterweise zu einer Verringerung des Fluidstroms von der Hydropumpe zu den Verbrauchern.In a further embodiment of the invention, the FS fluid flow path influences the control device in such a way that blockage or injection of the FS fluid flow path through at least one of the detection diaphragms results in a hearing of the fluid flow from the hydraulic pump to the consumers. An opening or control of the FS fluid flow path through all the detection apertures, in turn, advantageously results in a reduction of the fluid flow from the hydraulic pump to the consumers.
Zum Öffnen und Schließen des FS-Fluidströmungspfads kann eine jeweilige Detektionsblende ein Ventilelement aufweisen. Das Ventilelement wird hierbei vorzugsweise in Öffnungsrichtung vom Druckmittel stromaufwärts der ihr zugeordneten Zumessblende und in Schließrichtung vom Druckmittel stromabwärts der ihr zugeordneten Zumessblende und zusätzlich von einer Federkraft einer, insbesondere einstellbaren, Detektionsfeder beaufschlagt. Somit kann auf vorrichtungstechnisch einfache Weise bei einer Unterversorgung der Zumessblende, also bei Unterschreiten einer bestimmten Druckdifferenz über die Zumessblende, der FS-Fluidströmungspfad gesperrt werden.For opening and closing the FS fluid flow path, a respective detection panel may have a valve element. The valve element is in this case preferably acted upon in the opening direction by the pressure medium upstream of its associated metering orifice and in the closing direction by the pressure medium downstream of its associated metering orifice and additionally by a spring force of a, in particular adjustable, detection spring. Thus can be locked on device technology simple manner in a supply of the metering orifice, ie falls below a certain pressure difference across the metering orifice, the FS fluid flow path.
Die Federkraft der Detektionsfeder der Detektionsblende gibt vorteilhafterweise die Druckdifferenz vor, bei der der Ventilschieber der Detektionsblende in Richtung der Schließstellung betätigt ist.The spring force of the detection spring of the detection aperture advantageously determines the pressure difference at which the valve slide of the detection aperture is actuated in the direction of the closed position.
Als Regelvorrichtung kann vorzugsweise eine Pumpenregelung zum Verstellen eines Fördervolumens der als Verstellpumpe ausgebildeten Hydropumpe vorgesehen sein. Alternativ ist denkbar, dass die Regelvorrichtung eine Eingangsdruckwaage der als Konstantpumpe ausgebildeten Hydropumpe ist.As a control device may preferably be provided a pump control for adjusting a delivery volume of the hydraulic pump designed as a variable displacement pump. Alternatively, it is conceivable that the control device is an inlet pressure compensator designed as a fixed displacement pump.
Die Pumpenregelung hat den Vorteil, dass die Verstellpumpe zurückgeschwenkt werden kann, wenn der FS-Fluidströmungspfad geöffnet ist, und somit keine Unterversorgung bei den Zumessblenden vorliegt. Ist dagegen der FS-Fluidströmungspfad gesperrt, so kann die Verstellpumpe durch die Pumpenregelung in Richtung einer Erhöhung des Fördervolumens verschwenkt werden. Es ist denkbar, dass aufgrund des FS-Fluidströmungspfads die Regelvorrichtung ohne einen Volumenstromregler ausgebildet werden kann.The pump control has the advantage that the variable displacement pump can be swung back when the FS fluid flow path is open, and thus there is no undersupply at the metering orifices. If, however, the FS fluid flow path is blocked, then the variable displacement pump can be pivoted by the pump control in the direction of increasing the delivery volume. It is conceivable that due to the FS fluid flow path, the control device may be formed without a volumetric flow regulator.
In weiterer Ausgestaltung der Erfindung kann eine jeweilige Zumessblende als stetig verstellbares Wegeventil ausgebildet sein. Diese kann in einer Neutralstellung eine Druckmittelverbindung zwischen dem ihr zugeordneten Verbraucher und der Hydropumpe sperren und in Schaltstellungen eine Druckmittelverbindung zwischen dem ihr zugeordneten Verbraucher und der Hydropumpe aufsteuern. Mit dem Wegeventil ist somit ein Öffnungsquerschnitt einstellbar.In a further embodiment of the invention, a respective metering orifice may be formed as a continuously adjustable directional control valve. This can lock in a neutral position, a pressure fluid connection between the associated consumer and the hydraulic pump and aufsteuern in switching positions a pressure medium connection between the associated consumer and the hydraulic pump. With the directional valve thus an opening cross-section is adjustable.
Bei einer bevorzugten Ausführungsform, die insbesondere auf einer LS-Steuerung mit Individualdruckwaagen basieren kann, ist einer jeweiligen Zumessblende eine Individualdruckwaage zugeordnet. Diese wird vorzugsweise zum Aufrechterhalten einer etwa konstanten Druckdifferenz über die Zumessblende eingesetzt. Somit ist neben einer jeweiligen Detektionsblende zusätzlich eine jeweilige Individualdruckwaage vorgesehen. Die Individualdruckwaage kann hierbei der Zumessblende vor- oder nachgeschaltet sein. Durch das Vorsehen einer Individualdruckwaage zusätzlich zur Detektionsblende ist im Unterschied um Stand der Technik kein Drucküberschuss mehr erforderlich.In a preferred embodiment, which may be based in particular on a LS control with individual pressure compensators, a respective metering orifice is associated with an individual pressure compensator. This is preferably used to maintain an approximately constant pressure difference across the metering orifice. Thus, in addition to a respective detection panel additionally a respective individual pressure compensator is provided. The individual pressure compensator can be upstream or downstream of the metering orifice. By providing an individual pressure compensator in addition to the detection aperture no pressure surplus is required in contrast to the prior art.
In weiterer Ausgestaltung der Erfindung ist zumindest eine Individualdruckwaage zusammen mit der zugeordneten Detektionsblende als ein Individualventil mit einem gemeinsamen Ventilelement ausgebildet. Vorzugsweise sind alle Individualdruckwaagen mit den diesen zugeordneten Detektionsblenden als Individualventile ausgebildet. Dies hat den Vorteil, dass vorrichtungstechnisch einfach und kostengünstig nur ein Ventil eingesetzt werden muss.In a further embodiment of the invention, at least one individual pressure compensator together with the associated detection aperture is designed as an individual valve with a common valve element. Preferably, all individual pressure compensators are formed with their associated detection apertures as individual valves. This has the advantage that device technology simple and inexpensive only one valve must be used.
Das Individualventil kann der Zumessblende vorteilhafterweise vor- oder nachgeschaltet sein.The individual valve may advantageously be upstream or downstream of the metering orifice.
Vorzugsweise ist das Ventilelement eines jeweiligen Individualventils als Ventilschieber ausgebildet. Dieser kann eine Grundstellung aufweisen und ausgehend von dieser in Richtung von ersten Schaltstellungen verschiebbar sein. Des Weiteren kann er in Richtung von zweiten Schaltstellungen verschiebbar sein, die sich an die ersten Schaltstellungen anschließen. In den unterschiedlichen Stellungen kann der Ventilschieber vorteilhafterweise die Funktionen der Detektionsblende und der Individualdruckwaage erfüllen. Somit kann in den ersten und zweiten Schaltstellungen der FS-Fluidströmungspfad geöffnet und in der Grundstellung gesperrt sein. In den zweiten Schaltstellungen kann des Weiteren eine Druckmittelverbindung zwischen der Hydropumpe und dem Verbraucher zugesteuert sein. In den ersten Schaltstellungen kann die Druckmittelverbindung zwischen der Hydropumpe und dem Verbraucher dann gedrosselt oder vollständig aufgesteuert sein. In der Grundstellung ist dann die Druckmittelverbindung zwischen der Hydropumpe und dem Verbraucher vorzugsweise vollständig aufgesteuert. Bei einer Normalversorgung der Zumessblende erfolgt die Regelung der Druckdifferenz über die Zumessblende durch das Individualventil in den ersten und zweiten Schaltstellungen, in denen der FS-Fluidströmungspfad vollständig geöffnet ist. Die Pumpenregelung kann hierbei die Verschwenkpumpe zurückschwenken. Bei einer Unterversorgung ist dagegen das Ventilelement des Individualventils in der Grundstellung, wobei der FS-Fluidströmungspfad gesperrt und die Druckmittelverbindung von der Hydropumpe zur Zumessblende bzw. zum Verbraucher vollständig geöffnet ist. Die Pumpenregelung kann die Verstellpumpe hierbei dann in Richtung eines erhöhten Fördervolumens verschwenken.Preferably, the valve element of a respective individual valve is designed as a valve slide. This can have a basic position and, starting from this, be displaceable in the direction of first switching positions. Furthermore, it can be displaceable in the direction of second switching positions which adjoin the first switching positions. In the different positions of the valve spool can advantageously fulfill the functions of the detection panel and the individual pressure compensator. Thus, in the first and second switch positions, the FS fluid flow path may be opened and locked in the home position. Furthermore, in the second switching positions, a pressure medium connection between the hydraulic pump and the consumer can be controlled. In the first switching positions, the pressure medium connection between the hydraulic pump and the consumer can then be throttled or completely open. In the basic position, the pressure medium connection between the hydraulic pump and the consumer is then preferably completely opened. In the case of a normal supply of the metering orifice, the pressure difference across the metering orifice is controlled by the individual valve in the first and second switching positions, in which the FS fluid flow path is completely open. The pump control can swing back the swivel pump. In the case of an undersupply, on the other hand, the valve element of the individual valve is in the basic position, wherein the FS fluid flow path is blocked and the pressure medium connection from the hydraulic pump to the metering orifice or to the consumer is completely opened. The pump control can in this case then pivot the variable displacement pump in the direction of an increased delivery volume.
Durch das Individualventil und den FS-Fluidströmungspfad kann der Ventilschieber des Individualventils des lasthöchsten Verbrauchers im eingeregelten Betrieb vorzugsweise im Bereich seiner ersten Schaltstellungen positioniert sein, da von der Hydropumpe, im Unterschied zum Stand der Technik, kein überschüssiger Druck zur Verfügung gestellt wird. Dies führt zu einer Energieeinsparung, da eine Regelreserve für sogenannte Extremsituationen nicht mehr erforderlich ist.Due to the individual valve and the FS fluid flow path, the valve slide of the individual valve of the highest-load consumer can preferably be positioned in the region of its first switching positions in the adjusted mode, since no excess pressure is provided by the hydraulic pump, in contrast to the prior art. This leads to an energy saving, since a control reserve for so-called extreme situations is no longer necessary.
In weiterer Ausgestaltung des Individualventils kann das Ventilelement in Richtung der Grundstellung von der Federkraft der Detektionsfeder und vom Druckmittel stromabwärts der zugeordneten Zumessblende beaufschlagt sein. In Richtung von den ersten und zweiten Schaltstellungen kann das Ventilelement vom Druckmittel stromaufwärts der ihr zugeordneten Zumessblende beaufschlagt sein.In a further embodiment of the individual valve, the valve element can be acted upon in the direction of the basic position by the spring force of the detection spring and the pressure medium downstream of the associated metering orifice. In the direction of the first and second switching positions, the valve element may be acted upon by the pressure medium upstream of the associated metering orifice.
Bei einer weiteren bevorzugten Ausführungsform, die insbesondere auf einer LUDV-Steuerung basiert, kann die erfindungsgemäße Steueranordnung mit einer der Zumessblende nachgeschalteten Individualdruckwaage ausgebildet sein. Somit kann bei einer Steueranordnung, die prinzipiell als LUDV-Steueranordnung ausgebildet ist, ebenfalls ein FS-Fluidströmungspfad vorgesehen werden.In a further preferred embodiment, which is based in particular on a LUDV control, the control arrangement according to the invention may be formed with an individual pressure compensator downstream of the metering orifice. Thus, in a control arrangement, which is in principle designed as LUDV control arrangement, also an FS fluid flow path can be provided.
Bei der weiteren bevorzugten Ausführungsform kann somit einer jeweiligen Zumessblende eine Individualdruckwaage mit einem Ventilschieber nachgeschaltet sein. Dieser kann in einer Grundstellung eine Druckmittelverbindung zwischen der Zumessblende und dem zugeordneten Verbraucher sperren und ausgehend von der Grundstellung in Richtung von ersten Schaltstellungen die Druckmittelverbindung zwischen der Zumessblende und dem zugeordneten Verbraucher gedrosselt aufsteuern. Ausgehend von den ersten Schaltstellungen kann der Ventilschalter weiter in Richtung von zweiten Schaltstellungen die Druckmittelverbindung zwischen der Zumessblende und dem zugeordneten Verbraucher vollständig aufsteuern.In the further preferred embodiment can thus be followed by a respective metering orifice an individual pressure compensator with a valve spool. This can lock in a basic position, a pressure medium connection between the metering orifice and the associated consumer and aufsteuern starting from the basic position in the direction of first switching positions the pressure medium connection between the metering orifice and the associated consumer throttled. Starting from the first switching positions, the valve switch can continue to control the pressure medium connection between the metering orifice and the associated consumer in the direction of second switching positions.
Der Ventilschieber einer jeweiligen Individualdruckwaage der weiteren Ausführungsform kann ferner in Richtung der ersten und zweiten Schaltstellungen vom Druckmittel stromabwärts der Zumessblende und in Richtung der Grundstellung vom höchsten Lastdruck der Verbraucher beaufschlagt sein.The valve spool of a respective individual pressure compensator of the further embodiment can also be acted upon in the direction of the first and second switching positions by the pressure medium downstream of the metering orifice and in the direction of the basic position of the highest load pressure of the consumer.
Des Weiteren können die Individualdruckwaagen der weiteren bevorzugten Ausführungsform an eine gemeinsame LS-Leitung angeschlossen sein. Der Ventilschieber einer jeweiligen Individualdruckwaage kann dann in den zweiten Schaltstellungen die LS-Leitung mit einer an den Verbraucher angeschlossenen Verbraucherleitung stromabwärts der Zumessblende gedrosselt verbinden. In den ersten Schaltstellungen und in der Grundstellung kann der Ventilschieber die Verbindung zwischen der LS-Leitung und der Verbraucherleitung sperren oder zusteuern. Ferner kann der Ventilschieber in Richtung der Grundstellung über die LS-Leitung vom höchsten Lastdruck der Verbraucher beaufschlagt sein.Furthermore, the individual pressure compensators of the further preferred embodiment can be connected to a common LS line. The valve spool of a respective individual pressure compensator can then connect the LS line throttled in the second switching positions with a consumer line connected to the consumer downstream of the metering orifice. In the first switching positions and in the basic position, the valve spool can block or control the connection between the LS line and the consumer line. Furthermore, the valve spool can be acted upon in the direction of the basic position via the LS line from the highest load pressure of the consumer.
In weiterer Ausgestaltung der Erfindung kann die Pumpenregelung vorzugsweise einen Verstellzylinder zum Verstellen des Fördervolumens der Verstellpumpe aufweisen. Der Verstellzylinder ist hierbei vorzugsweise über ein Regelventil geregelt.In a further embodiment of the invention, the pump control may preferably have an adjusting cylinder for adjusting the delivery volume of the variable. The adjusting cylinder is preferably regulated via a control valve.
Ein Kolben des Verstellzylinders kann ferner einen Zylinderraum begrenzen, der zur Verringerung des Fördervolumens der Verstellpumpe mit Druckmittel beschickbar ist. Um das Fördervolumen der Verstellpumpe zu erhöhen, kann aus dem Zylinderraum Druckmittel entlassen werden. Zum Druckmittelbeschicken ist der Zylinderraum insbesondere mit dem FS-Fluidströmungspfad direkt, insbesondere gedrosselt, verbunden.A piston of the adjusting cylinder can further limit a cylinder space which can be charged to reduce the delivery volume of the variable displacement pump with pressure medium. In order to increase the delivery volume of the variable displacement, pressure medium can be discharged from the cylinder space. For pressure medium charging the cylinder chamber is in particular directly connected to the FS fluid flow path, in particular throttled.
Das Regelventil kann einen Ventilschieber aufweisen, der über eine, insbesondere einstellbare, Ventilfeder mit einer Federkraft in Richtung einer Grundstellung beaufschlagt ist. In Richtung von Schaltstellungen kann er mit Druckmittel einer Ausgangsseite der Hydropumpe und somit mit einem Pumpendruck beaufschlagt sein. In der Grundstellung ist vorzugsweise eine Druckmittelverbindung zwischen dem FS-Fluidströmungspfad und dem Zylinderraum aufgesteuert und zwischen der Ausgangsseite der Hydropumpe und dem Zylinderraum zugesteuert. In den Schaltstellungen kann die Druckmittelverbindung zwischen dem FS-Fluidströmungspfad und dem Zylinderraum zugesteuert und zwischen der Ausgangsseite der Hydropumpe und dem Zylinderraum aufgesteuert sein.The control valve may have a valve slide, which is acted upon by a, in particular adjustable, valve spring with a spring force in the direction of a basic position. In the direction of switching positions, it can be acted upon with pressure medium of an output side of the hydraulic pump and thus with a pump pressure. In the basic position, a pressure medium connection between the FS fluid flow path and the cylinder space is preferably controlled and directed between the output side of the hydraulic pump and the cylinder chamber. In the switching positions, the pressure medium connection between the FS fluid flow path and the cylinder chamber can be controlled and controlled between the output side of the hydraulic pump and the cylinder chamber.
Mit Vorteil ist der FS- Fluidströmungspfad über eine Drossel mit einem Tank verbunden, womit im FS-Fluidströmungspfad selbst bei einer geschlossenen Detektionsblende ein definierter Druck vorherrscht.Advantageously, the FS fluid flow path is connected via a throttle to a tank, whereby a defined pressure prevails in the FS fluid flow path even with a closed detection orifice.
Die hydraulische Steueranordnung kann in einem Ventilblock vorgesehen sein. Es ist denkbar, dass der Ventilblock aus Ventilscheiben ausgebildet ist, wobei in einer jeweiligen Ventilscheibe die Ventile für einen jeweiligen Verbraucher vorgesehen sind.The hydraulic control arrangement may be provided in a valve block. It is conceivable that the valve block is formed from valve disks, wherein in a respective valve disk, the valves are provided for a respective consumer.
Im Folgenden werden bevorzugte Ausführungsformen anhand von Zeichnungen näher erläutert. Es zeigen:
-
einen hydraulischen Schaltplan einer erfindungsgemäßen Steueranordnung gemäß einem ersten Ausführungsbeispiel,Figur 1 -
einen weiteren hydraulischen Schaltplan der erfindungsgemäßen Steueranordnung,Figur 2 -
Figur 3 einen hydraulischen Schaltplan eines Abschnitts der Steueranordnung gemäß einem zweiten Ausführungsbeispiel, -
Figur 4 einen hydraulischen Schaltplan eines Abschnitts der Steueranordnung gemäß einem dritten Ausführungsbeispiels, -
Figur 5 einen hydraulischen Schaltplan eines Abschnitts der Steueranordnung gemäß einem vierten Ausführungsbeispiel und -
Figur 6 einen hydraulischen Schaltplan eines Abschnitts der Steueranordnung gemäß einem fünften Ausführungsbeispiel.
-
FIG. 1 a hydraulic circuit diagram of a control arrangement according to the invention according to a first embodiment, -
FIG. 2 a further hydraulic circuit diagram of the control arrangement according to the invention, -
FIG. 3 FIG. 2 shows a hydraulic circuit diagram of a section of the control arrangement according to a second exemplary embodiment, FIG. -
FIG. 4 FIG. 2 is a hydraulic circuit diagram of a portion of the control arrangement according to a third embodiment; FIG. -
FIG. 5 a hydraulic circuit diagram of a portion of the control arrangement according to a fourth embodiment and -
FIG. 6 a hydraulic circuit diagram of a portion of the control arrangement according to a fifth embodiment.
Gemäß
Die Ausgestaltung der Zumessblenden 10 wird anhand der Ventilscheibe 4 erläutert. Die Zumessblende 10 ist als stetig verstellbares 5/4-Wegeventil ausgestaltet. Ein Ventilschieber der Zumessblende 10 ist hierbei in einer Neutralstellung 0 federzentriert. Über einen hydraulischen Aktor 14 kann der Ventilschieber ausgehend von der Neutralstellung 0 in Richtung einer ersten Schaltstellung a oder entgegengesetzt ausgehend von der Neutralstellung 0 in Richtung von zweiten Schaltstellungen b verstellt werden. Wird der Ventilschieber ausgehend von den zweiten Schaltstellungen b weiter verschoben, so gelangt er in Freigang- oder Schwimm-Stellungen c. In den ersten Schaltstellungen a ist eine Druckmittelverbindung zwischen einer Zulaufleitung 16, die sich von einer in
Das Individualventil 12 wird ebenfalls anhand der Ventilscheibe 4 näher erläutert. Es ist als stetig verstellbares 4/3-Wegeventil ausgestaltet. Über eine Detektionsfeder 30 ist ein Ventilschieber in Richtung einer Grundstellung 0 mit einer Federkraft beaufschlagt. Ausgehend von der Grundstellung 0 ist er in Richtung von ersten Schaltstellungen a verschiebbar. Im Anschluss an die Schaltstellungen a ist er in Richtung von zweiten Schaltstellungen b verschiebbar. Über die Individualventile 10 der Ventilscheiben 4 bis 8 erstreckt sich ein Flow-Sensing (FS)-Fluidströmungspfad 32. Hinsichtlich dieses FS-Fluidströmungspfads 32 sind die Individualventile 12 in Reihe angeordnet. In der Grundstellung 0 des Individualventils 12 ist hierbei der FS-Fluidströmungspfad 32 gesperrt und in den ersten und zweiten Schaltstellungen a, b geöffnet. Somit ist der FS-Fluidströmungspfad 32 nur dann geöffnet, wenn alle Ventilschieber der Individualventile 12 nicht in ihrer Neutralstellung 0 sind. Ist dagegen einer der Ventilschieber oder sind mehrere der Ventilschieber der Individualventile 12 in der Grundstellung 0, so ist der FS-Fluidströmungspfad 32 gesperrt. Der FS-Fluidströmungspfad 32 ist stromaufwärts der Individualventile 12 gesehen an die Zulaufleitung 16 angeschlossen und erstreckt sich über das Individualventil 12 der Ventilscheibe 8 weiter zum Individualventil 12 der Ventilscheibe 6 und von hier aus zum Individualventil 12 der Ventilscheibe 4. Stromabwärts des letzten Individualventils 12 der Ventilscheibe 4 ist der FS-Fluidströmungspfad 32 dann an eine nicht dargestellte Pumpenregelung einer als Verstellpumpe ausgebildeten Hydropumpe angeschlossen.The
Der Ventilschieber eines jeweiligen Individualventils 12 ist, wie vorstehend bereits erläutert, von der Federkraft der Detektionsfeder 30 in Richtung der Grundstellung 0 beaufschlagt. Zusätzlich ist der in Richtung der Grundstellung 0 vom Druckmittel in der Zweigleitung 24 beaufschlagt und somit vom Druck stromab der Zumessblende 10. In entgegengesetzter Richtung, also in Richtung der ersten und zweiten Schaltstellungen a, b, ist der Ventilschieber über eine Steuerleitung 34 vom Druckmittel der Zulaufleitung 16 stromab des Individualventils 12 und stromauf der Zumessblende 10 beaufschlagt. In der Grundstellung 0 ist der FS-Fluidströmungspfad 32 gesperrt und die Zulaufleitung 16 zur Zumessblende 10 vollständig geöffnet. In den ersten Schaltstellungen a ist dagegen der FS-Fluidströmungspfad 32 geöffnet und die Zulaufleitung 16 zur Zumessblende ist ebenfalls vollständig geöffnet. In den zweiten Schaltstellungen b ist dann der FS-Fluidströmungspfad 32 wiederum geöffnet und die Zulaufleitung 16 zur Zumessblende 10 gesperrt.The valve spool of a respective
Die erfindungsgemäße hydraulische Steueranordnung nach
Bei der Erläuterung der Funktionsweise der Steueranordnung 1 aus
Als nächstes wird angenommen, dass die Zumessblende 10 der Ventilscheibe 8 sich in ihrer zweiten Schaltstellung b befindet, womit ein an den Arbeitsanschlüssen A, B der Ventilscheibe 8 angeschlossener Verbraucher mit Druckmittel über die Zulaufleitung 16 versorgt ist. Die Individualventile 12 der Ventilscheiben 4 und 6 sind in der zweiten Schaltstellung b. Ist der an die Ventilscheibe 8 angeschlossene Verbraucher nun in Unterversorgung, dass heißt die Druckdifferenz über die Zumessblende 10 ist unterhalb einer vorbestimmten Druckdifferenz, so wird der Ventilschieber des Individualventils 12 der Ventilscheibe 8 in die Grundstellung 0 verschoben. Der FS-Fluidströmungspfad 32 ist demnach durch das Individualventil 12 der Ventilscheibe 8 gesperrt. Es gelangt somit kein Druckmittel von der Zulaufleitung 16 über den FS-Fluidströmungspfad 32 zur Pumpenregelung. Der FS-Fluidströmungspfad 32 wirkt dabei derart mit der Pumpenregelung zusammen, dass in diesem Fall die Verstellpumpe in Richtung einer Erhöhung des Fördervolumens verschwenkt wird. Das Individualventil 12 der Ventilscheibe 8 ist in diesem Fall hinsichtlich der Zulaufleitung 16 zur Zumessblende 10 vollständig bzw. fast vollständig geöffnet, weswegen es minimale hydraulische Verluste aufweist, im Unterschied zu einer herkömmlichen LS-Steueranordnung aus dem Stand der Technik.Next, it is assumed that the
Liegt keine Unterversorgung des an der Ventilscheibe 8 angeschlossenen Verbrauchers mehr vor, so wird der Ventilschieber des Individualventils 12 der Ventilscheibe 8 in seine erste Schaltstellung a bewegt. Der FS-Fluidströmungspfad 32 ist somit wieder geöffnet und gleichzeitig ist die Zulaufleitung 16 zur Zumessblende 10 der Ventilscheibe 8 vollständig oder fast vollständig geöffnet, was wiederum zu minimalen hydraulischen Verlusten führt. Durch den geöffneten FS-Fluidströmungspfad 32 wird die Verschwenkpumpe wieder zurückgeschwenkt.If there is no undersupply of the consumer connected to the valve disk 8, the valve spool of the
Nun wird angenommen, dass die an den Ventilscheiben 6 und 8 angeschlossenen hydraulischen Verbraucher parallel betrieben sind. Hierzu befindet sich sowohl der Ventilschieber der Zumessblende 10 der Ventilscheibe 6 als auch der Ventilschieber der Zumessblende 10 der Ventilscheibe 8 beispielsweise in den zweiten Schaltstellungen b. Die Druckdifferenz der Zumessblenden 10 der Ventilscheiben 6 und 8 sind hierbei über die Individualventile 12 eingeregelt. Der an die Ventilscheibe 6 angeschlossene Verbraucher soll der lasthöchste Verbraucher sein, weswegen das Individualventil 12 der Ventilscheibe 6 den FS-Fluidströmungspfad 32 regelt. Hierzu befindet sich sein Ventilschieber in der Grundstellung 0 oder in der ersten Schaltstellung a. Die Verstellpumpe wird dabei mit der Pumpenregelung so geregelt, dass die benötigte Druckdifferenz an den Zumessblenden 10 anliegt. Die Verbindung in der ersten Ventilscheibe 6 zwischen der Zulaufleitung 16 und der Zumessblende 10 ist somit vollständig geöffnet, was zu minimalen hydraulischen Verlusten führt. Das andere Individualventil 12 der Ventilscheibe 8 mit dem lastdruckniederen Verbraucher regelt dann die Druckdifferenz über die Zumessblende 10 der Ventilscheibe 8 auf herkömmliche Weise, indem sein Ventilschieber in den Schaltstellungen a oder b ist. Der FS-Fluidströmungspfad 32 ist somit über das Individualventil 12 der Ventilscheibe 8 vollständig geöffnet.It is now assumed that the hydraulic consumers connected to the valve disks 6 and 8 are operated in parallel. For this purpose, both the valve spool of the
Durch die erfindungsgemäße hydraulische Steueranordnung 1 gemäß
Gemäß
In
Des Weiteren in der
Gemäß
Von der Verbindungsleitung 66 zweigt die Zweigleitung 24 für das Individualventil 12 ab. Der Ventilschieber des Individualventils 12 wird somit in Richtung seiner Grundstellung 0 weiterhin vom Druckmittel stromabwärts der Zumessblende 10 beaufschlagt. In entgegen gesetzter Richtung wird er von der Steuerleitung 34 vom Druckmittel zwischen dem Individualventil 12 und der Zumessblende 10 beaufschlagt. In Unterschied zur
Eine Funktionsweise des Abschnitts 36 der Steueranordnung 1 gemäß
Bei der Funktionsbeschreibung der hydraulischen Steueranordnung gemäß den
Befindet sich der Ventilschieber einer Zumessblende 10 in der Neutralstellung 0, so wird der Ventilschieber des zugeordneten Individualventils 12 in seine zweite Schaltstellung b verschoben. In dieser ist der FS-Fluidströmungspfad 32 hinsichtlich dieses Individualventils 12 geöffnet. Sind alle Zumessblenden 10 in der Neutralstellung 0, so wird ein Fördervolumen der Verstellpumpe 40 auf den geringst möglichen Wert verstellt, so dass Energieverluste bei einem Stillstand der Verbraucher 38 möglichst gering sind.The valve spool of a
Eine Funktionsweise der Steueranordnung gemäß
In
Die Detektionsblende 70 ist als 2/2-Wegeventil ausgestaltet. Ein Ventilschieber der Detektionsblende 70 ist in Richtung einer Grundstellung 0 von der Federkraft der Detektionsfeder 30 beaufschlagt. Ausgehend von der Grundstellung 0 kann er entgegen der Federkraft in Richtung einer Schaltstellung a verstellt werden. Zusätzlich zur Federkraft ist der Ventilschieber in Richtung seiner Grundstellung 0 über eine Steuerleitung 78 vom Druckmittel der Verbindungsleitung 66 zwischen der Zumessblende 10 und der Individualdruckwaage 68 beaufschlagt. In entgegengesetzter Richtung, also in Richtung der Schaltstellung a, ist der Ventilschieber über eine Steuerleitung 80 vom Druckmittel der Zulaufleitung 16 stromauf der Zumessblende 10 beaufschlagbar. In der Grundstellung 0 sperrt die Detektionsblende 70 den FS-Fluidströmungspfad 32. Dagegen ist der Schaltstellung a der FS-Fluidströmungspfad 32 geöffnet.The
Liegt keine Unterversorgung vor, so ist die Steueranordnung gemäß
Eine weitere Ausführungsform einer Steueranordnung 1 zeigt der Abschnitt 36 gemäß
Wird die Druckdifferenz über die Zumessblende 10 gemäß
Offenbart ist eine hydraulische Steueranordnung für eine Mehrzahl von Verbrauchern. Für einen jeweiligen Verbraucher ist hierbei eine Zumessblende zum Steuern eines Fluidstroms vorgesehen. Einer jeweiligen Zumessblende ist eine Detektionsblende zugeordnet. Die Detektionsblenden sind dabei fluidisch in Reihe angeordnet. Ein Flow-Sensing (FS)- Fluidströmungspfad erstreckt sich hierbei über die Detektionsblenden. Stromaufwärts der Detektionsblenden ist der Fluidströmungspfad mit einer Hydropumpe und stromabwärts der Detektionsblenden mit einer Regelvorrichtung der Hydropumpe verbunden. Ist ein Verbraucher mit Druckmittel unterversorgt, so schließt die entsprechende Detektionsblende den Flow-Sensing-Fluidströmungspfad. Die Regelvorrichtung wirkt hierbei derart mit diesem FS-Fluidströmungspfad zusammen, dass der Fluidstrom von der Hydropumpe hierdurch erhöht wird. Ist keiner der Verbraucher unterversorgt, so ist der FS-Fluidströmungspfad über die Detektionsblenden vollständig geöffnet und die Regelvorrichtung vermindert den Fluidstrom von der Hydropumpe.Disclosed is a hydraulic control arrangement for a plurality of consumers. For a respective consumer in this case a metering orifice for controlling a fluid flow is provided. A respective metering orifice is assigned a detection aperture. The detection apertures are arranged fluidly in series. A flow-sensing (FS) fluid flow path extends over the detection apertures. Upstream of the detection apertures, the fluid flow path is connected to a hydraulic pump and downstream of the detection apertures to a control device of the hydraulic pump. If a consumer is under-supplied with pressure medium, the corresponding detection panel closes the flow-sensing fluid flow path. In this case, the regulating device interacts with this FS fluid flow path in such a way that the fluid flow from the hydraulic pump is thereby increased. If none of the consumers are undersupplied, then the FS fluid flow path is Fully opened via the detection panels and the control device reduces the fluid flow from the hydraulic pump.
- 11
- Steueranordnungcontrol arrangement
- 22
- Ventilblockmanifold
- 44
- Ventilscheibevalve disc
- 66
- Ventilscheibevalve disc
- 88th
- Ventilscheibevalve disc
- 1010
- Zumessblendemetering orifice
- 1212
- Individualventilindividual valve
- 1414
- Aktoractuator
- 1616
- Zulaufleitungsupply line
- 1818
- Arbeitsleitungworking line
- 2020
- Arbeitsleitungworking line
- 2222
- Ablaufleitungdrain line
- 2424
- Zweigleitungbranch line
- 2626
- Steuerleitungcontrol line
- 2828
- Steuerleitungcontrol line
- 3030
- Detektionsfederdetection pen
- 3232
- FS-FluidströmungspfadFS-fluid flow path
- 3434
- Steuerleitungcontrol line
- 3636
- Abschnittsection
- 3838
- Verbraucherconsumer
- 4040
- Verstellpumpevariable
- 4242
- Pumpenregelungpump control
- 4444
- Verstellzylinderadjusting cylinder
- 4646
- Kolbenpiston
- 4848
- Zylinderraumcylinder space
- 5050
- Federfeather
- 5252
- Regelventilcontrol valve
- 5454
- Ventilfedervalve spring
- 5656
- Steuerleitungcontrol line
- 5858
- Zweigleitungbranch line
- 6060
- Drosselthrottle
- 6262
- Drosselthrottle
- 6464
- Tanktank
- 6666
- Verbindungsleitungconnecting line
- 6868
- IndividualdruckwaageIndividual pressure compensator
- 7070
- Detektionsblendedetection aperture
- 7272
- LastdruckmeldeleitungLoad pressure signaling line
- 7474
- Steuerleitungcontrol line
- 7676
- Steuerleitungcontrol line
- 7878
- Steuerleitungcontrol line
- 8080
- Steuerleitungcontrol line
- 8282
- Steuerleitungcontrol line
- 8484
- Steuerleitungcontrol line
- A, BA, B
- Arbeitsanschlussworking port
- 0 ^0 ^
- Neutralstellung, GrundstellungNeutral position, basic position
- aa
- erste Schaltstellungfirst switching position
- bb
- zweite Schaltstellungsecond switch position
- cc
- Freigang-StellungFree gear position
Claims (15)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013223288.8A DE102013223288A1 (en) | 2013-11-15 | 2013-11-15 | Hydraulic control arrangement |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2881594A1 true EP2881594A1 (en) | 2015-06-10 |
EP2881594B1 EP2881594B1 (en) | 2016-07-20 |
Family
ID=51845302
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14190832.7A Active EP2881594B1 (en) | 2013-11-15 | 2014-10-29 | Hydraulic control assembly |
Country Status (4)
Country | Link |
---|---|
US (1) | US9726203B2 (en) |
EP (1) | EP2881594B1 (en) |
CN (1) | CN104653530B (en) |
DE (1) | DE102013223288A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014226182A1 (en) * | 2014-12-17 | 2016-06-23 | Robert Bosch Gmbh | Control valve assembly and hydraulic drive system with it |
DE102015218832A1 (en) * | 2015-09-30 | 2017-03-30 | Robert Bosch Gmbh | Pump-controller combination with power limitation |
DE102018202148B3 (en) * | 2018-02-12 | 2019-03-07 | Hawe Hydraulik Se | Hydraulic valve assembly with forced switching and mobile hydraulic system |
DE102018212077A1 (en) * | 2018-07-19 | 2020-01-23 | Deere & Company | Method for operating a hydraulic consumer on an electrically actuated control valve |
WO2020132934A1 (en) * | 2018-12-26 | 2020-07-02 | 潍柴动力股份有限公司 | Hydraulic variable pump set and excavator |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5081839A (en) * | 1990-01-29 | 1992-01-21 | Caterpillar Inc. | Pressure compensated hydraulic system |
US5305789A (en) | 1992-04-06 | 1994-04-26 | Rexroth-Sigma | Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves |
DE102007045803A1 (en) | 2007-08-22 | 2009-02-26 | Robert Bosch Gmbh | Hydraulic control arrangement |
EP2078868A2 (en) * | 2008-01-09 | 2009-07-15 | Husco International, Inc. | Hydraulic control valve system with isolated pressure compensation |
DE102009017506A1 (en) * | 2008-04-25 | 2009-12-03 | Husco International Inc., Waukesha | Pressure compensated hydraulic control valve with load-dependent pressure limitation |
DE102009034616A1 (en) | 2009-07-27 | 2011-02-03 | Robert Bosch Gmbh | Way valve arrangement |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5937645A (en) * | 1996-01-08 | 1999-08-17 | Nachi-Fujikoshi Corp. | Hydraulic device |
FR2744497B1 (en) * | 1996-02-07 | 1998-04-03 | Rexroth Sigma | MULTIPLE HYDRAULIC DISTRIBUTION DEVICE |
DE10255738A1 (en) * | 2002-11-07 | 2004-05-27 | Bosch Rexroth Ag | Double-circuit hydraulic system for controlling consumers of mobile equipment such as track equipment comprises two circuits interconnected by an interconnecting valve arrangement having two valve devices |
DE102004048684A1 (en) * | 2004-10-06 | 2006-04-13 | Bosch Rexroth Ag | Hydraulic control arrangement |
DE102006053897A1 (en) * | 2006-11-15 | 2008-05-21 | Robert Bosch Gmbh | Two-circuit hydraulic system and interconnecting valve arrangement |
-
2013
- 2013-11-15 DE DE102013223288.8A patent/DE102013223288A1/en not_active Withdrawn
-
2014
- 2014-10-29 EP EP14190832.7A patent/EP2881594B1/en active Active
- 2014-11-11 US US14/538,122 patent/US9726203B2/en active Active
- 2014-11-14 CN CN201410643590.XA patent/CN104653530B/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5081839A (en) * | 1990-01-29 | 1992-01-21 | Caterpillar Inc. | Pressure compensated hydraulic system |
US5305789A (en) | 1992-04-06 | 1994-04-26 | Rexroth-Sigma | Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves |
DE102007045803A1 (en) | 2007-08-22 | 2009-02-26 | Robert Bosch Gmbh | Hydraulic control arrangement |
EP2078868A2 (en) * | 2008-01-09 | 2009-07-15 | Husco International, Inc. | Hydraulic control valve system with isolated pressure compensation |
DE102009017506A1 (en) * | 2008-04-25 | 2009-12-03 | Husco International Inc., Waukesha | Pressure compensated hydraulic control valve with load-dependent pressure limitation |
DE102009034616A1 (en) | 2009-07-27 | 2011-02-03 | Robert Bosch Gmbh | Way valve arrangement |
Also Published As
Publication number | Publication date |
---|---|
DE102013223288A1 (en) | 2015-05-21 |
CN104653530A (en) | 2015-05-27 |
US20150136251A1 (en) | 2015-05-21 |
EP2881594B1 (en) | 2016-07-20 |
CN104653530B (en) | 2018-02-13 |
US9726203B2 (en) | 2017-08-08 |
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