EP2441966B1 - Dispositif de commande pour consommateurs hydrauliques - Google Patents

Dispositif de commande pour consommateurs hydrauliques Download PDF

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Publication number
EP2441966B1
EP2441966B1 EP20110010098 EP11010098A EP2441966B1 EP 2441966 B1 EP2441966 B1 EP 2441966B1 EP 20110010098 EP20110010098 EP 20110010098 EP 11010098 A EP11010098 A EP 11010098A EP 2441966 B1 EP2441966 B1 EP 2441966B1
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EP
European Patent Office
Prior art keywords
valve
control valve
control
line
reg
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.)
Not-in-force
Application number
EP20110010098
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German (de)
English (en)
Other versions
EP2441966A1 (fr
Inventor
Winfried RÜB
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Hydac Filtertechnik GmbH
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Hydac Filtertechnik GmbH
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Publication of EP2441966A1 publication Critical patent/EP2441966A1/fr
Application granted granted Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/047—Preventing foaming, churning or cavitation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/565—Control of a downstream pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2544—Supply and exhaust type
    • Y10T137/2554—Reversing or 4-way valve systems
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/263—Plural sensors for single bypass or relief valve
    • Y10T137/2632—Sensors interconnected by timing or restrictive orifice
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/265—Plural outflows
    • Y10T137/2657—Flow rate responsive
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/265—Plural outflows
    • Y10T137/2668—Alternately or successively substituted outflow
    • Y10T137/2678—Four port reversing valve
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2708—Plural sensors
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves

Definitions

  • the invention relates to a control device for hydraulic consumers with at least one control valve for controlling a feed line for the respective hydraulic consumer and with a tank return according to the feature configuration of the preamble of claim 1.
  • fluidic pressure medium can then escape via the after-suction valve to the tank without any great resistance, and in the braking phase the after-suction valve is automatically biased to a higher opening pressure so that an extreme feed into the hydrostatic drive system can be dispensed with due to the increased suction pressure level.
  • an additional pump system in the manner of an auxiliary pump to maintain a certain inlet-side pressure levels;
  • the known solution with a control valve in two-piston design consuming and therefore expensive to manufacture.
  • DE 42 43 578 A1 is a commercial vehicle hydraulics known, in particular for a refuse vehicle, with at least one hydraulic circuit to which various actuators for performing various functions, such as opening the rear part, lifting and tilting a refuse container, etc., are connected. Furthermore, the known solution on one of a motor or coupled to this power take-off of the commercial vehicle pump for pumping hydraulic oil into the hydraulic circuit. The pump is constructed such that its delivery rate is at least partially controllable independently of the speed of the engine. With the known solution, it is possible using a control device to determine the power requirements of the actuators connected to the hydraulic circuit and always adjust the flow rate of the pump so that the speed of the engine of the commercial vehicle remains as low as possible and only raised at higher power requirements, which helps avoid energy losses.
  • a generic control device for hydraulic consumers with at least one control valve for driving a feed line for the respective hydraulic consumer and with a tank return, wherein the control valve is connected to an additional feed line and designed as a priority valve, that the feed line the preference of a fluid supply to the Tank return receives.
  • the known control device is designed as a hydraulic system with a plurality of pumps having a constant delivery volume, wherein a pump is associated with a preferred consumer (primary circuit). For both pumps, of which the first pump is mainly associated with the preferred consumer, the other a secondary circuit, a single flow control valve is assigned.
  • the present invention seeks to further improve the known solutions to the effect that in any case, damaging cavitations are reliably prevented in functionally reliable, energy-saving and cost-effective manner.
  • This object is achieved by a drive device having the features of patent claim 1 in its entirety.
  • the control valve for the control device according to the invention is constructed in the manner of a priority valve, the so-called.
  • Tank Vorspannventil addressed feed line gives preference to the free tank return.
  • control valve has a second feed line, which is influenced by a second throttle and that a control edge of the valve piston of the control valve influences the free flow of this second feed line.
  • the other second feed line can serve for additional and direct supply of the feed line.
  • the fact that the other supply line in the control valve via the control edge of the valve piston can be influenced, can be shut off by the control stroke of a control spring of the control valve such that there is an interruption of the connection in the supply line.
  • the further second feed line begins in a channel of the pressure supply and is determined via a defined throttle point in their flow behavior.
  • a non-return valve arranged between the feed line and the feed line, which opens in the direction of the feed line, prevents unwanted return flow from the feed line into the feed line.
  • Fig.1 is reproduced the control device for hydraulic consumers in the manner of a circuit diagram.
  • the relevant circuit diagram is only an example; Other design options are conceivable.
  • the working cylinder 10 is connected fluidly with its piston chamber to a Nutzanschluß A 1 and with its rod side to a Nutzanschluß B 1st
  • the hydraulic motor is connected to useful terminals A 2 , B 2 , wherein all user terminals A 1 , B 1 , A 2 , B 2 form respective output of a designated as a whole by 14 control block.
  • the illustrated working cylinder 10 may, for example, be part of a working machine in the form of a wheel loader or the like for the purpose of lifting and lowering a working tool in the form of a customary lifting mechanism Shovel.
  • the hydraulic motor 12 drives, for example, a mechanical slewing gear 16, which is based on an inertia J.
  • hydraulic motors 12 for example, hydraulic lifts can be actuated, running gears of working machines, such as forklifts, driven and the like more.
  • the possibilities of use both for hydraulic power cylinders and for hydraulic motors are almost unlimited.
  • both the working movement of the piston rod unit of the working cylinder 10 and the respective direction of rotation for the hydraulic motor 12 is reversible. It applies to the hydraulic motor 12 that when driving the slewing gear 16 in one direction he experiences a pressing load during acceleration, whereas a pulling load occurs during braking, because the inertial mass (moment of inertia J) of the rotating mechanism 16 continues.
  • the situation on the working cylinder 10 is comparable if a load has to be pressed in one direction and pulled in the other opposite direction for a retraction movement.
  • control device has a control valve 18, which serves, among other things, to control a feed line T Reg for the respective hydraulic consumer 10, 12. Diametrically opposite to the output-side feed line T Reg is connected to the control valve 18 of a further tank return T RO on the input side. Another output of the control valve 18 is connected to an additional supply line T R. and the control valve 18 is formed as a priority valve, that the feed line T Reg receives the benefit of a fluid supply to the tank return T RO .
  • the pressure supply p is in turn connected via a throttle D 1 to the input side of the control valve 18 and in a side branch 20, the pressure supply p opens on the input side of two other control valves 22,24, wherein the one control valve 22 on the output side with its fluid connections each with the Nutzanêtn A. 1 , B 1 of the hydraulic cylinder 10 is in communication and the second further control valve 24 is connected to the useful ports A 2 , B 2 of the hydraulic motor 12 accordingly.
  • the respective valve 22,24 is also the input side in fluid-carrying connection with the feed line T R and the two leading to the respective Nutzanêtn A 1 , B 1 , A 2 , B 2 outputs are each connected via a fluid line to the feed line T Reg .
  • check valves 26,28 In the pertinent fluid lines two check valves 26,28 are connected, wherein the check valve 28 which leads respectively to the Nutzanschluß B 1 , B 2 , should be provided with a pressure limiting function. Furthermore, all the check valves 26, 28 open in the direction of their respectively assignable useful connections A 1 , B 1 , A 2 , B 2 .
  • the other second control valves 22,24 are formed in the type of 4/3-way valves and shown in their middle unactuated position, in which the respective input side is separated from the output side.
  • the respective 4/3-way valve can be controlled hydraulically or electro-hydraulically in the usual way via opposite control terminals a 1 , b 1 and a 2 , b 2 .
  • the pertinent 4/3-way valves can be optionally replace with other valve designs and in addition to the shown working cylinder 10 and the hydraulic motor 12 can occur more consumers of the same kind or different types.
  • the control block 14 only serve to control a hydraulic consumer 10 or 12.
  • a check valve RV is connected, which opens in the direction of the feed line T Reg .
  • the control valve 18 further comprises an internally extending second feed line 30, which is influenced by a second throttle D2. The details are still on the basis of the sectional images after the Fig. 2 ff will be explained.
  • the valve piston 32 of the control valve 18 is supported against a control spring 34 in the form of a compression spring ab.Wie further from the Fig.1 shows, between the tank return T RO and the feed line T Reg a permanently throttled discharge line 36 is connected, which preferably has a further defined throttle point D2 '.
  • the relief line 36 further opens to the control side 38 of the control valve 18, which acts opposite to the control spring 34 on the valve piston 32.
  • another branch line 40 opens from the free tank return T RO on the other control side 42 of the control valve 18.
  • the drive device is designed in the manner of a sensor circuit that "feels" if there is a need for feed for the respective consumer 10,12. Only when the demand is "felt", the free tank return T RO is accumulated to the required pressure level.
  • the control valve 18 thus forms a kind of tank biasing valve and is designed as a priority valve such that it gives preference to the feed line T Reg from the fluid supply before the free tank return T RO .
  • the addressed sensor circuit relieves the tank return T RO , as long as no input requirement is reported. Otherwise, the tank return T RO is throttled to a constructively predetermined height, which is essentially predetermined by the spring force of the control spring 34. As long as no outflow of water takes place in the feed line T Reg , the fluid is conducted unthrottled into the tank return line T RO . On the other hand, when a feed current flows, the control valve 18 continues to regulate the constructively set pressure in the feed line T Reg by throttling the outflow cross section to the free tank return T RO , thereby simultaneously raising the pressure in T R above those in the feed line T Reg and Fluid medium now must flow through the check valve RV in the feed line T Reg .
  • the respective effective pressure surface on the valve piston 32 of the control valve designed as a pressure compensator 18 is used.
  • the control valve 18 is preferably formed as a 4/3-way proportional valve to form the pressure compensator.
  • the control valve is shown in more detail in the following figures with reference to various working positions.
  • the representation corresponds to the Fig.2 the switching representation of the valve after the Figure 6 , ie in the direction of the Fig.2 and 6 Seen inside the valve housing 44 guided control or valve piston 32 in its leftmost switching position, in which he abuts the left side of a wall of the valve housing 44.
  • a plurality of widened in the circumferential annular spaces 46,48,50,52 and 54 are present.
  • the last-mentioned annular space 54 accommodates the control spring 34 designed as a compression spring.
  • the pressure supply p is connected to the throttle point D1.
  • the feed line T R opens and to the subsequent fourth annulus 52, the free tank return T RO is connected.
  • the individual annular spaces 46, 48, 50, 52 and 54 are essentially fluid-tightly separated from one another via piston segments 56, 58, 60 and 62.
  • the pertinent piston segments 56, 58, 60 and 62 are widened in diameter relative to the other diameter profile of the valve piston 32 with the formation of effective annular piston surfaces.
  • left cover position for the valve piston 32 are individual with a, b, c designated overlaps of the valve piston 32 in the valve housing 44 reproduced, in the pertinent working position applies a ⁇ b ⁇ c and in view of the said left stop position is the free travel x for
  • the valve piston 32 is penetrated along its longitudinal axis 66 by a longitudinal bore 68 which opens outward on both sides of the valve piston 32 to the outside, ie into the first annular space 46 and into the fifth Annular space 54.
  • first transverse bore 70 between the first piston segment 56 and the second piston segment 58 which in the shown Working position after the Fig.2 opens into the second annular space 48 and in the other fluid-carrying communicates with the longitudinal bore 68 in the form of a longitudinal channel in connection.
  • a second transverse bore 72 of larger diameter emerges as part of the longitudinal bore 68 in the direction of the valve housing 44 from the second piston segment 58.
  • a third transverse bore 74 is provided which opens into the fourth annular space 52 between the piston segments 60 and 62. If transverse boring is mentioned here, each transverse bore 70, 72, 74 can also comprise several, in particular four, mutually perpendicular channel sections.
  • transverse drilling arrangements successive in the longitudinal planes can be arranged adjacent to one another by 90 ° offset from each other.
  • the valve piston 32 is at its, in the direction of the Fig.2 seen, right end formed running in steps.
  • the outer diameter of all piston segments is the same; however, the effective piston surfaces 64 are different in diameter from each other; however, the mutually adjacent piston surfaces 64 of two piston segments 56, 58, 58, 60 and 60 and 62 have the same effective piston surface 64.
  • the Fig.2 and 6 concern basically the so-called. Feeding position as a possible working position of the drive device according to the invention.
  • the throttles D1 and D2 should be closed in the sense of an intellectual assumption.
  • the pressureless state then presses the valve spring 34, the control piston 32 against the mechanical stop in the form of an inner housing wall of the valve housing 44.
  • the fluid-conducting connection between T R and T RO is shut off.
  • the hydraulic pump is turned on and fluid pressure p is present in the second annulus 48, no hydraulic resistance is present in the feed channel T Reg with the result that the flowing in the return working fluid via the valve RV depressurized via the feed valves 26,28 to the hydraulic consumers 10,12 arrives.
  • This working condition prevails when pulling loads. If there are no more pulling loads, then the feed valves 26,28 close and no volume flow flows anymore.
  • the pressure in T Reg and T R increases.
  • the throttle D1 should now be opened.
  • the T Reg fluid-carrying channel as a feed line is then supplied not only via the valve RV from the side T R , but also via the throttle D1, starting from a high pressure level, for example in the form of the pump supply pressure p. If now no pulling loads occur, then the valve piston 32 again moves in the direction of the figures to the right against the spring 34 and it comes within the valve to a fluid-carrying connection of T R to the non-return T RO . The consequence of this is that the pressure in T R decreases.
  • the valve RV closes because the feed line T Reg is additionally fed via the throttle D1 and no volume flow flows. Therefore, the pressure in the feed line T Reg remains at a level corresponding to the amount of the control spring 34.
  • control or valve piston 32 can then run completely against the control spring 34, without feed pressure is taken from T R. Therefore, at fully open connection T R to T RO, the pressure at T R drops to the level of T RO . If the valve piston 32 ran against the spring 34 until the mechanical stop, then the pressure in the feed line T Reg would have run up to the level of the inlet pressure in the second feed line 30.
  • the respective feed valves 26, 28 would then optionally open and feed undesirably into consumer connections A 1 , B 1 , A 2 , B 2 .
  • the amount of control oil consumption is determined by the magnitude of the force of the control spring 34 and the throttling action of D2.
  • Typical design values vary between a compressive preload of 10 bar, combined with D2 equal to 0.8 mm and a compressive preload of 7 bar, combined obtained from two series-connected restrictors of 0.6 mm as D2. This can be varied by interpretation, the control oil consumption of 1 l / min to 0.34 l / min easily.
  • the associated energy losses are then dependent on the current pump pressure p, which supplies the second feed line 30 with. At a mean pump pressure of 200 bar then occur losses of 0.3 KW and 0.1 KW.
  • the tank biasing valve can be in Form of the control valve 18 its stroke so far lead to a connection feed line T Reg to feed line T R opens, wherein supply line T R is already unthrottled connected to the free tank return T RO .
  • the working capacity of the hydraulic consumers 10, 12 can be increased with the control device described, as long as no feed state is present.
  • An increase in pressure by 7 to 10 bar is readily possible, so that so far energy saved by this enabled dynamic pressure.
  • the working capacity of the hydraulic consumers is, for example, increased by 7 to 10 bar when there is no feed state. Energy is then saved in the scope of the released dynamic pressure of 7 to 10 bar.
  • a typical example is a small excavator with a mean volume flow of 50 l / min and 7 bar back pressure in the feed channel.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Transmission Device (AREA)
  • Means For Warming Up And Starting Carburetors (AREA)

Claims (9)

  1. Dispositif de commande pour des consommateurs (10, 12) hydrauliques, comprenant au moins une vanne (18) de commande pour la commande d'un conduit (TReg) d'alimentation du consommateur (10, 12) respectif et un retour (TR0) de cuve, la vanne (18) de commande étant raccordée à un conduit (TR) d'alimentation supplémentaire et étant constituée en vanne prioritaire, de manière à ce que le conduit (TReg) d'alimentation reçoive la préférence d'une alimentation en fluide par rapport au retour (TRO) de cuve, caractérisé en ce que la vanne (18) de commande a un deuxième conduit (30) d'alimentation, qui est influencé par un deuxième étranglement (D2), et en ce qu'un bord (76) de commande du piston (32) de commande de la vanne (18) de commande influe sur la liberté de passage dans ce deuxième conduit (30) d'alimentation.
  2. Dispositif de commande suivant la revendication 1, caractérisé en ce que, entre le conduit (TReg) d'alimentation et le conduit (TR) d'alimentation, est monté un clapet antiretour (RV), qui s'ouvre dans la direction du conduit (TReg) d'alimentation.
  3. Dispositif de commande suivant la revendication 1 ou 2, caractérisé en ce que la vanne (18) de commande est raccordée à une alimentation (p) en pression servant d'alimentation en fluide, qui est influencée par un étranglement (D1).
  4. Dispositif de commande suivant l'une des revendications 1 à 3, caractérisé en ce que le piston (32) de la vanne (18) de commande s'appuie sur un ressort (34) de réglage, en ce que le piston (32) de la vanne a une conduite intérieure de fluide ayant le deuxième étranglement (D2) et des surfaces (64) de piston à distance l'une de l'autre, qui débouchent dans des espaces (46, 48, 50, 52, 54) annulaires dans le corps (44) de la vanne (18) de commande, auquel respectivement l'alimentation (p) en pression, le retour (TRO) de cuve, le conduit (TReg) d'alimentation ainsi que le premier conduit (TR) d'alimentation sont raccordés fluidiquement.
  5. Dispositif de commande suivant l'une des revendications 1 à 4, caractérisé en ce qu'un conduit (D2') de décharge étranglé en permanence est monté entre le retour (TRO) de cuve et le conduit (TReg) d'alimentation.
  6. Dispositif de commande suivant la revendication 4 ou 5, caractérisé en ce que le piston (32) de la vanne (18) de commande exécute, par rapport au ressort (34) de réglage, une course de réglage pour la limitation de la pression, pour relier ainsi le conduit (TReg) d'alimentation au conduit (TR) d'alimentation, dès qu'une hauteur de pression pouvant être prescrite est dépassée.
  7. Dispositif de commande suivant l'une des revendications 1 à 6, caractérisé en ce que, dans le conduit (TReg) d'alimentation, sont montées respectivement deux vannes (26, 28) d'alimentation, qui commandent respectivement un raccord (A1, B1, A2, B2) utile du consommateur (10, 12) hydraulique, et en ce qu'il est monté, dans les conduits d'alimentation du côté de la sortie, une autre vanne de commande, qui est raccordée sur son côté d'entrée respectivement à l'alimentation en fluide ainsi qu'aux conduits (TR) d'alimentation.
  8. Dispositif de commende suivant l'une des revendications 1 à 7, caractérisé en ce que la une vanne (18) de commande est constituée sous la forme d'une bascule manométrique.
  9. Dispositif de commande suivant la revendication 7 ou 8, caractérisé en ce que la une vanne (18) de commande est, en tant que bascule manométrique, une vanne proportionnelle à 4/3 voies et la respectivement deuxième vanne (22, 24) de commande est une vanne à 4/3 voies.
EP20110010098 2006-12-22 2007-10-26 Dispositif de commande pour consommateurs hydrauliques Not-in-force EP2441966B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006061305A DE102006061305B3 (de) 2006-12-22 2006-12-22 Ansteuereinrichtung für hydraulische Verbraucher
EP20070819343 EP2126370B1 (fr) 2006-12-22 2007-10-26 Dispositif de commande pour des consommateurs hydrauliques

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP07819343.0 Division 2007-10-26

Publications (2)

Publication Number Publication Date
EP2441966A1 EP2441966A1 (fr) 2012-04-18
EP2441966B1 true EP2441966B1 (fr) 2013-02-13

Family

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Family Applications (3)

Application Number Title Priority Date Filing Date
EP20110010098 Not-in-force EP2441966B1 (fr) 2006-12-22 2007-10-26 Dispositif de commande pour consommateurs hydrauliques
EP20070819343 Not-in-force EP2126370B1 (fr) 2006-12-22 2007-10-26 Dispositif de commande pour des consommateurs hydrauliques
EP20110010099 Not-in-force EP2441967B1 (fr) 2006-12-22 2007-10-26 Dispositif de commande pour consommateurs hydrauliques

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP20070819343 Not-in-force EP2126370B1 (fr) 2006-12-22 2007-10-26 Dispositif de commande pour des consommateurs hydrauliques
EP20110010099 Not-in-force EP2441967B1 (fr) 2006-12-22 2007-10-26 Dispositif de commande pour consommateurs hydrauliques

Country Status (6)

Country Link
US (1) US8443827B2 (fr)
EP (3) EP2441966B1 (fr)
AT (1) ATE550552T1 (fr)
DE (1) DE102006061305B3 (fr)
DK (3) DK2441966T3 (fr)
WO (1) WO2008083772A1 (fr)

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US11540942B2 (en) * 2018-07-26 2023-01-03 Alcon Inc. Redundant pneumatic circuit for reliability enhancement of vitrectomy instruments
JP7304807B2 (ja) * 2019-12-26 2023-07-07 株式会社クボタ バルブユニット
EP3956740A4 (fr) 2020-06-16 2023-01-11 Berry Metal Company Brûleur à oxygène à entrée unique pour fabriquer du métal
JP7223213B2 (ja) * 2020-09-04 2023-02-15 パーシバン・バラダラジャン 油圧システム内で圧力制限を制御する動的論理素子

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Also Published As

Publication number Publication date
DK2441966T3 (da) 2013-03-11
EP2126370B1 (fr) 2012-03-21
ATE550552T1 (de) 2012-04-15
EP2126370A1 (fr) 2009-12-02
US20100065135A1 (en) 2010-03-18
WO2008083772A1 (fr) 2008-07-17
DK2441967T3 (da) 2013-03-11
EP2441966A1 (fr) 2012-04-18
US8443827B2 (en) 2013-05-21
DE102006061305B3 (de) 2008-07-10
EP2441967A1 (fr) 2012-04-18
DK2126370T3 (da) 2012-04-30
EP2441967B1 (fr) 2013-02-20

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