EP0924427A1 - Leistungsregelventil - Google Patents
Leistungsregelventil Download PDFInfo
- Publication number
- EP0924427A1 EP0924427A1 EP98121603A EP98121603A EP0924427A1 EP 0924427 A1 EP0924427 A1 EP 0924427A1 EP 98121603 A EP98121603 A EP 98121603A EP 98121603 A EP98121603 A EP 98121603A EP 0924427 A1 EP0924427 A1 EP 0924427A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- throttle valve
- power control
- control device
- valve body
- 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
Links
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1203—Power on the axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1204—Position of a rotating inclined plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/08—Pressure difference over a throttle
Definitions
- the invention relates at least to a power control valve for limiting the power one connected to the power control valve by means of an adjustment device adjustable hydraulic pump.
- a power control device is such. B. from the DE 196 26 793 C1 known.
- a hydraulic Control device described each for two hydraulic pumps operating in parallel Power control device according to the preamble of claim 1 comprises.
- the two Power control devices are provided by a pressure control device common to the hydraulic pumps controlled.
- the known power control devices each include a so-called Hyperbolic regulator, which acts via a swivel lever on a valve that acts as a power control valve Proportional valve.
- the swivel lever is by means of a swivel piston trained attack elements with the adjusting piston of the adjusting device each associated hydraulic pump connected.
- the engagement element is from the adjusting piston of the adjusting device carried along, so that the lever arm over which the engagement element on the Swinging lever attacks with increasing delivery volume of the assigned hydraulic pump extended.
- the adjusting piston of the adjusting device is on the one hand with the working pressure the working line of the assigned hydraulic pump and on the other hand with a back pressure acted upon, which is set by the proportional valve.
- the one from that Proportional valve set back pressure depends on the reaction via the Swivel angle from. This reaction is on the one hand from the pressure in the work management the associated hydraulic pump and on the other hand depending on the lever arm with which engages the engagement element on the pivot lever. Because of this constellation there is a hyperbolic control characteristic, d. H. when the specified one is reached
- the power control device regulates the hydraulic pump to a constant maximum output Performance, i.e. on a constant product of work pressure in the work management and Delivery volume of the hydraulic pump.
- the known power control device is therefore variable for drive systems Drive speed cannot be used.
- Another disadvantage with the known Power control device can be seen in the fact that the known power control device must be connected to the adjusting piston of the adjusting device, d. H. at the Adjustment device of the hydraulic pump must be installed. The corresponding Connection between the pivot lever and the actuating piston requires an additional one constructive effort.
- the same constructive solution cannot be found for everyone Realize types of hydraulic pumps to be used in the same way and it is for each type of hydraulic pump requires a special design.
- a power control valve is known from DE-OS 24 61 897, which by the Drive speed of the hydraulic pump is independent.
- This power control valve uses but not of a hyperbola controller that has a swivel lever on one Proportional valve. Instead, this is indicated in the management of the Hydropump provided power control valve on a valve body, the front side from which pressure fluid flows. The resulting pressure causes a shift the valve body against a return spring. With increasing displacement of the A control slit is closed in the valve body.
- the control slot is geometrically like this shaped that the change in the throttle cross-section as a function of the displacement of the valve body is not linear but is determined so that the product is Working pressure and throttle cross section is at least approximately constant. To this In this way, a power regulation is achieved at least approximately.
- a disadvantage of the power control valve known from DE-OS 24 61 897 is, however, that its control characteristic is too imprecise for many applications.
- the dynamic pressure at the front of the valve piston is a relatively imprecise control variable and is from the Pressure drop at the control slot is affected.
- the throttle cross section of the control slot therefore acts back on the displacement of the valve body, so that there is a relative imprecise control characteristic results.
- the dynamic pressure also depends on the viscosity and thus the temperature of the pressure fluid.
- This capacity control valve failed therefore not compared to power control valves with an exact hyperbola controller push through.
- Another disadvantage is that to change the control power of the control slot must be changed. At high powers there are very high spring forces, which are very require large feathers.
- the object is in connection with the characterizing features of claim 1 solved with the generic features.
- the invention is based on the concept of the hyperbolic regulator with the swivel lever in to integrate a unit that is structurally separate from the hydraulic pump.
- the swivel lever is not over the attack element with the adjusting piston of the adjusting device Hydraulic pump connected. Instead, a throttle valve is provided, the valve body carries the attack element.
- the throttle valve throttles the flow in the Hydraulic pump assigned working line.
- the pressure drop at the throttle valves can can be used to control the adjusting device of the hydraulic pump.
- the power control device according to the invention is rather against the Flow-regulated hydraulic pumps are the usual fixed throttles in the working line the hydraulic pump. In this way, those already in operation can Hydraulic pumps also retrofitted with a power control device according to the invention become.
- the power control device is completely independent of the drive speed the assigned hydraulic pump. Furthermore, the invention Power control device universal for various types of hydraulic pumps be used because a mechanical connection between the pivot lever and the Adjusting piston of the adjusting device does not have to be created. It is enough that to loop power control device according to the invention into the working line. Yet the power control device according to the invention works on the basis of the hyperbola controller extremely precise.
- the throttle valve body of the throttle valve can according to claim 2 of the Pressure difference between two throttle valve chambers are applied, the first throttle valve chamber with the working line and the second throttle valve chamber is connected to a control output of the proportional valve.
- the throttle valve body can advantageously be designed as a hollow piston, one of the two throttle valve chambers according to claim 4 inside the throttle valve body can be integrated.
- the corresponding throttle valve chamber be closed with a volumetric flask located on a housing part of the Power control device repels.
- an annular groove can be in the jacket region of the throttle valve body be formed on which with a throttle valve body surrounding the throttle valve body cooperating control edge is designed according to claim 5.
- the throttle cross-section depends on the inlet and outlet of the throttle valve thereby from the position of the throttle valve body.
- the engagement element can according to claim 6 in the throttle valve body be slidably mounted and protrude into the hollow bore of the throttle valve body, so that it is acted upon by the working line pressure against the swivel lever.
- the Direction of movement of the engagement element preferably perpendicular according to claim 7 directed to the direction of movement of the throttle valve body, so that the position of the Throttle valve body the lever arm and the working pressure on the lever arm determines the force exerted.
- an adjustable stop element for the throttle valve body be provided to vary the maximum flow rate of the hydraulic pump to be determined.
- the proportional valve can according to claim 9 with the working line connected first input port, one connected to a pressure medium tank second input connection and a control output connected to the throttle valve exhibit.
- the pressure at the control outlet is on the one hand related to the working pressure the input connection connected to the working line and, on the other hand, the one via the Reaction on the reaction force acting on the proportional valve proportional.
- the pivot lever engages according to claim 10 on the proportional valve body Proportional valve preferably so that the proportional valve body with increasing application of force to the swivel lever by the engagement element Control output increasingly connects to the first input connection.
- a proportional, linear control of the proportional valve can be achieved in that the Swing lever the proportional valve body according to claim 11 against one Return spring applied.
- the bias of the return spring is preferably corresponding via an adjusting element Claim 12 adjustable so that the limiting power to which the power control device according to the invention limits the connected hydraulic pump, is adjustable.
- the setting can either be done manually e.g. B. with an adjusting screw take place or via a hydraulic or electrical control accordingly Claim 13.
- a proportional electromagnet is preferably provided for this purpose which the preload of the return spring is variably adjustable.
- the Power control device 1 has four connections, namely a working line input P, a working line outlet A, one with a pressure medium tank 2 connected tank connection T and a message connection X.
- the working line input P is via the working line 3 with the working line connection B of the hydraulic pump 4th connected.
- the message port X is connected via a message line 5 the load-sensing connection X of the valve control unit 6 to be described in more detail below Hydraulic pump 4 connected.
- the signaling connection X and the working line output A are in the housing 7 of the power control device 1 in the illustrated embodiment connected with each other.
- the message output X and the working line output A can However, it can also be combined to form a common output, so that the signal line 5 from the working line 3 downstream of the working line output A, preferably z. B. branches directly to the connected consumer.
- the power control device 1 is essentially divided into one Throttle valve 8 and a proportional valve 9, which in the illustrated embodiment too a common valve unit are structurally combined in a common housing 7.
- the throttle valve 8 consists of a throttle valve body 10 which is in a the throttle valve body 10 surrounding throttle cylinder body 11 is movable in the longitudinal direction.
- the throttle valve body 10 is in the illustrated embodiment as a hollow piston formed and has a hollow bore 12 designed as a blind bore.
- the Hollow bore 12 is via a transverse bore 13 with a on the outer surface of the throttle valve body 10 formed annular groove 14 connected.
- On the throttle cylinder body 11 is an inlet 15 connected to the working line input P and one to the Working line output A connected drain 16, z. B. in the form of radial slots, educated.
- the throttle valve body 10 is in its position with the maximum in FIG Throttle cross section shown.
- the throttle cross-section of the throttle valve 8 decreases increasingly as the Control edge 17 at the upper end in FIG. 1 of the annular groove 14 with the displacement of the Throttle valve body 10 also moves down and connects to the drain 16 constricts.
- the position of the throttle valve body 10 shown in FIG. 1 with maximum throttle cross section and thus maximum delivery volume of the connected hydraulic pump 4 can be adjusted by the adjustable stop element 18th set variably.
- the adjustable stop element 18 is shown in the Embodiment designed as a threaded bolt and can be in the connecting piece Screw in 19 and fix using the nut 20 and the lock nut 21.
- the position of the throttle valve body 10 is determined by the pressure difference between one Inside the throttle valve body 10 formed first throttle valve chamber 22 and a second in the exemplary embodiment on the connecting piece 19 on the in Fig. 1st Upper end face of the throttle valve body 10 formed second throttle valve chamber 23 controlled.
- the first throttle valve chamber 22 is shown in the Embodiment part of the hollow bore 12 and is thus via the working line input P connected to the working line 3.
- the first throttle valve chamber 22 is by a measuring piston 24, which is supported on the closure cap 25 of the housing 7, locked.
- the second throttle valve chamber 23 is via a in the connecting piece 19th by a closure body 26 closed end control line 27 with a Control output A 'of the proportional valve 9 connected.
- Pivot axis 30 pivotable pivot lever 31 is arranged, on which one in a Radial bore 32 of the throttle valve body 10 arranged, piston-like Attacking element 35 attacks via a slide shoe 33.
- the end face 34 of the In the exemplary embodiment, engagement elements 35 are located within the hollow bore 12 and is thus against the prevailing working pressure in the work line 3 Swing lever 31 acted upon.
- the direction of movement of the engagement element 35 runs thereby perpendicular to the direction of movement of the throttle valve piston 10.
- Working pressure in the working line 3 determines the force with which the engagement element 35 acts on the pivot lever 31, the lever arm with which the engagement element 35 engages the pivot lever 31 by the position of the throttle valve body 10 fixed.
- the reaction force imparted via the pivot lever 31 acts on the plunger 40 Proportional valve piston 41 of the proportional valve 9 and shifts the Proportional valve body 41 against that applied by the return spring 42 Restoring force in Fig. 1 down.
- the proportional valve body 41 is in one Proportional cylinder body 43 movable, which surrounds the proportional valve body 41 and a first input connection P 'connected to the working line 3, one with the pressure medium tank 2 connected second input port T 'and one over the Control line 27 has control output A 'connected to throttle valve 8.
- a hydraulic proportional valve of any known type can be used as the proportional valve 9 Find use.
- the bias of the return spring 42 is preferably over a Adjustment element which engages the spring plate 46 of the return spring 42, adjustable.
- a Another spring plate 47 of the return spring 42 lies on the proportional valve body 41 of the proportional valve 9. In this way, the limiting power to which the power control device according to the invention limited, adjustable.
- the adjusting element is designed as a threaded bolt 45 and fixable by means of a nut 47 and a lock nut 48.
- the return spring 42 is in the illustrated embodiment from two interlocking return springs 42a and 42b put together.
- Fig. 1 is an example of the external wiring of the invention Power control device using the example of a flow-controlled hydraulic pump 4 shown.
- the use of the power control device 1 according to the invention is but not limited to this application.
- the power control device 1 is looped into the working line 3 and provides at the same time the throttle element, which is the flow rate in the flow control specifies for the consumer connected to the working line output A.
- a Flow control valve 50 detects the pressure drop across the throttle valve 8 and controls in Dependence thereon on the two actuating cylinders 51 and 52 in the exemplary embodiment two adjusting pistons 53 and 54 having adjusting device the delivery volume of Hydraulic pump 4.
- a pressure relief valve 55 is provided, which Working pressure in the working line 3 limited to a permissible maximum value.
- the Flow control valve 50 and the pressure relief valve 55 are shown in the Embodiment designed as a 3/2-way valve and each by a return spring 56 or 57 applied to their basic position.
- the flow control valve 50 and the pressure relief valve 55 are via a Connecting line 60 with the working line 3 and via a connecting line 61 connected to the pressure medium tank 2.
- the pressure relief valve 55 is in the illustrated embodiment in the connecting line 62 between the Flow control valve 50 and the pressure chamber 63 of the actuating cylinder 51 Increasing the pressure drop across the throttle valve 8 increases the flow control valve 50 the pressure in line 62 and thus in the control chamber 63, so that the hydraulic pump 4th is pivoted back and thus the pressure drop across the throttle valve 8 drops. On an equilibrium state is achieved in this way. Conversely, the pressure drop decreases, the flow control valve 50 reduces the pressure in the control chamber 63 and Hydraulic pump 4 is pivoted out further until equilibrium is reached. Increased when the maximum permissible working pressure in the working line 3 is exceeded the pressure relief valve 55 the pressure in the actuating chamber 63 and pivots the Hydraulic pump 4 back so far that the working pressure in the working line 3 on the permissible maximum pressure is limited.
- FIG. 3 shows a pQ diagram, where p symbolizes the working pressure in the working line 3 and Q the delivery volume emitted by the hydraulic pump 4.
- p symbolizes the working pressure in the working line 3
- Q the delivery volume emitted by the hydraulic pump 4.
- the power control device 1 controls the delivery flow control valve 50, the delivery of the hydraulic pump 4 in the control area 60 in Fig. 3 to a constant flow volume Q max, a, which is given consumer adjusted by the adjustable stop member 18.
- the power control device 1 regulates the product of the working pressure p and the delivery volume Q to a constant value along the hyperbola 61, so that overloading of the hydraulic pump 4 is avoided.
- the pressure limiting valve 55 regulates the hydraulic pump 4 back in order to avoid a pressure overload of the system.
- the maximum power to which the power control device 1 adjusts can be set by the adjusting element 45.
- An essential advantage of the power control device 1 according to the invention over the adjustment device of the hydraulic pump 4 attacking power control devices in that the power control of the speed of the hydraulic pump 4 driving Drive shaft 58 is independent.
- Known power control devices regulate the product from working pressure and swivel angle of the hydraulic pump 4 also with a Rocker arm mechanism to a constant value. The funding volume of the However, the hydraulic pump is only proportional to the swivel angle if the Drive speed is constant. This is not guaranteed with some drive concepts and a known power control device cannot be used there.
- a Another significant advantage is that the known power control device as the hydraulic pump 4 is designed as a separate valve unit. A mechanical one Connection to the adjusting device 51 to 54 of the hydraulic pump 4 is not necessary.
- the power control device 1 according to the invention is only in the working line 3 looped in and is therefore perfect of the type of hydraulic pump 4 used independently. As a result, the invention can be used universally Power control device 1 given.
- FIG. 2 shows a slightly modified from the embodiment of FIG. 1 second embodiment. Elements already described are the same Provide reference numerals, so that a repetitive description is unnecessary.
- the Bias of the return spring 42 is not rigidly adjustable by means of the threaded bolt 45 is, but by means of a tappet 70 engaging on the spring plate 46, in individual proportional electromagnets not shown depending on one of the connecting lines 72 and 73 of the proportional magnet 41 can be supplied electrical control signal is variably adjustable. That way it is Limiting power of the power control device 1 according to the invention is variable definable. For example, on a hydraulic pump 4, several consumers can each have one separate power control device 1 may be connected. The benefit allocation for the individual consumer then depends on z. B. depends on how many other consumers are switched on. This can be done by a corresponding on the proportional magnet 71st acting control signal are taken into account. Hyperboles of other control services are 3 with the reference numerals 63 and 64.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Servomotors (AREA)
Abstract
Description
- Fig. 1
- ein erstes Ausführungsbeispiel einer erfindungsgemäßen Leistungsregeleinrichtung in einer teilweise geschnittenen Darstellung mit einem Schaltbeispiel für die hydraulische Beschaltung; und
- Fig. 2
- ein zweites Ausführungsbeispiel einer erfindungsgemäßen Leistungsregeleinrichtung, wobei der Unterschied zu dem Ausführungsbeispiel gemäß Fig. 1 besteht darin, daß die Vorspannung der Rückstellfeder des Proportionalventils über einen Proportional-Elektromagneten einstellbar ist; und
- Fig. 3
- die Regel-Kennlinie der in Fig. 1 und Fig. 2 gezeigten Ventile in einem P-Q-Diagramm.
Claims (13)
- Leistungsregeleinrichtung (1) zum Begrenzen der Leistung zumindest einer an der Leistungsregeleinrichtung (1) angeschlossenen, mittels einer Verstellvorrichtung (51-54) verstellbaren und in eine Arbeitsleitung (3) fördernden Hydropumpe (4)
mit einem Hyperbelregler, der über einen Schwenkhebel (31) auf ein Proportionalventil (9) zurückwirkt und einem Angriffselement (35), das auf dem Schwenkhebel (31) so verschiebbar ist, daß der Hebelarm, mit welchem das Angriffselement (35) an dem Schwenkhebel (31) angreift, veränderbar ist,
dadurch gekennzeichnet,daß die Leistungsregeleinrichtung (1) als eine von der Verstellvorrichtung (51-54) baulich getrennte Ventileinheit ausgebildet ist, unddaß das Angriffselement (35) von einem bewegbaren Drossel-Ventilkörper (10) eines in der Arbeitsleitung (3) angeordneten Drosselventils (8) mitgeführt wird, wobei die Stellung des Drossel-Ventilkörpers (10) von einem Differenzdruck gesteuert ist, der die Differenz zwischen dem in der Arbeitsleitung (3) herrschenden Arbeitsdruck der Hydropumpe (4) und einem Steuerdruck ist, der durch das Proportionalventil (9) in Abhängigkeit von der durch den Schwenkhebel (31) vermittelten Rückwirkung geregelt wird. - Leistungsregeleinrichtung nach Anspruch 1,
dadurch gekennzeichnet,daß der Drossel-Ventilkörper (10) von der Druckdifferenz zwischen einer ersten (22) und zweiten (23) Drosselventil-Kammer beaufschlagt ist, wobei die erste Drosselventil-Kammer (22) mit der Arbeitsleitung (3) und die zweite Drosselventil-Kammer (23) über eine Steuerleitung (27) mit einem Steuerausgang (A') des Proportionalventils (9) verbunden ist. - Leistungsregeleinrichtung nach Anspruch 2,
dadurch gekennzeichnet,daß der Drossel-Ventilkörper (10) als Hohlkolben ausgebildet ist und der Drossel-Ventilkörper (10) eine Hohlbohrung (12) aufweist, die mit der Arbeitsleitung (3) in Verbindung steht. - Leistungsregeleinrichtung nach Anspruch 3,
dadurch gekennzeichnet,daß die erste Drosselventil-Kammer (22) im Inneren des Drossel-Ventilkörpers (10) ausgebildet ist und mit einem Meßkolben (24) verschlossen ist, des sich an einem Gehäuseteil (25) der Leistungsregeleinrichtung (1) abstützt. - Leistungsregeleinrichtung nach Anspruch 3 oder 4,
dadurch gekennzeichnet,daß die Hohlbohrung (12) mit einer im Mantelbereich des Drossel-Ventilkörpers (10) vorgesehenen Ringnut (14) verbunden ist, die einen in einem den Drossel-Ventilkörper (10) umgebenden Drossel-Zylinderkörper (11) ausgebildeten Zulauf (15) mit einem in dem Drossel-Zylinderkörper (11) ausgebildeten Ablauf (16) über einen Drosselquerschnitt verbindet, der von der Stellung des Drossel-Ventilkörpers (10) abhängt. - Leistungsregeleinrichtung nach einem der Ansprüche 3 bis 5,
dadurch gekennzeichnet,daß das Angriffselement (35) in dem Drossel-Ventilkörper (10) verschiebbar gelagert ist und von dem Arbeitsdruck in der Arbeitsleitung (3) gegen den Schwenkhebel (31) beaufschlagt ist, indem eine Stirnfläche (34) des Angriffselements (35) in die Hohlbohrung (12) des Drossel-Ventilkörpers (10) ragt. - Leistungsregeleinrichtung nach Anspruch 6,
dadurch gekennzeichnet,daß die Bewegungsrichtung des Angriffselements (35) senkrecht zu der Bewegungsrichtung des Drossel-Ventilkörpers (10) gerichtet ist. - Leistungsregeleinrichtung nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet,daß ein justierbares Anschlagelement (18) vorgesehen ist, an welchem der Drossel-Ventilkörper (10) bei Erreichen des durch das Anschlagelement (18) einstellbaren maximalen Förderstroms der Hydropumpe (4) anschlägt. - Leistungsregeleinrichtung nach einem der Ansprüche 1 bis 8,
dadurch gekennzeichnet,daß das Proportionalventil (9) einen mit der Arbeitsleitung (3) verbundenen ersten Eingangsanschluß (P'), einen mit einem Druckmedium-Tank (2) verbundenen zweiten Eingangsanschluß (T') und einen über eine Steuerleitung (27) mit dem Drosselventil (8) verbundenen Steuerausgang (A') aufweist. - Leistungsregeleinrichtung nach Anspruch 9,
dadurch gekennzeichnet,daß das Proportionalventil (9) einen Proportional-Ventilkörper (41) aufweist, an welchem der Schwenkhebel (31) so angreift, daß der Proportional-Ventilkörper (41) mit zunehmender Kraftbeaufschlagung des Schwenkhebels (31) durch das Angriffselement (35) den Steuerausgang (A') zunehmend mit dem ersten Eingangsanschluß (P') verbindet. - Leistungsregeleinrichtung nach Anspruch 9 oder 10,
dadurch gekennzeichnet,daß der Schwenkhebel (31) den Proportional-Ventilkörper (41) gegen eine Rückstellfeder (42) beaufschlagt. - Leistungsregeleinrichtung nach Anspruch 11,
dadurch gekennzeichnet,daß die Vorspannung der Rückstellfeder (42) über ein Justierelement (45; 70, 71) einstellbar ist. - Leistungsregeleinrichtung nach Anspruch 12,
dadurch gekennzeichnet,daß die Vorspannung der Rückstellfeder (42) hydraulisch oder elektrisch, insbesondere mittels eines Proportional-Elektromagneten (71), zur Vorgabe der Begrenzungsleistung der Leistungsregeleinrichtung (1) veränderbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19756600A DE19756600C1 (de) | 1997-12-18 | 1997-12-18 | Leistungsregelventil |
DE19756600 | 1997-12-18 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0924427A1 true EP0924427A1 (de) | 1999-06-23 |
EP0924427B1 EP0924427B1 (de) | 2003-07-02 |
Family
ID=7852566
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98121603A Expired - Lifetime EP0924427B1 (de) | 1997-12-18 | 1998-11-12 | Leistungsregeleinrichtung |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0924427B1 (de) |
DE (2) | DE19756600C1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0939225A3 (de) * | 1998-02-26 | 2000-06-14 | Brueninghaus Hydromatik Gmbh | Leistungsregeleinrichtung für mehrere verstellbare Hydropumpen |
EP1304482A2 (de) * | 2001-10-18 | 2003-04-23 | Brueninghaus Hydromatik Gmbh | Summenleistungsregler und Druckmittler |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017000761A1 (de) | 2017-01-27 | 2018-08-02 | Hydac Drive Center Gmbh | Versorgungsvorrichtung |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE2461897A1 (de) | 1974-12-31 | 1976-07-08 | Bosch Gmbh Robert | Regeleinrichtung fuer eine pumpe |
DE3034115A1 (de) * | 1980-09-11 | 1982-05-19 | Mannesmann Rexroth GmbH, 8770 Lohr | Leistungsregler |
US4535966A (en) * | 1981-09-26 | 1985-08-20 | Barmag Barmer Maschinenfabrik Aktiengesellschaft | Throttle valve |
DE4329164A1 (de) * | 1993-08-30 | 1995-03-09 | Brueninghaus Hydraulik Gmbh | Verwendung eines hydraulischen Steuerventilblocks mit einem Sitzventil anstelle eines Kolbenventils |
DE19626793C1 (de) | 1996-07-03 | 1997-06-26 | Brueninghaus Hydromatik Gmbh | Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen |
EP0781923A1 (de) * | 1994-09-14 | 1997-07-02 | Komatsu Ltd. | Kapauitätsregelung für hydraulische pumpe mit veränderlicher fördermenge |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3129440A1 (de) * | 1981-07-25 | 1983-02-10 | Mannesmann Rexroth GmbH, 8770 Lohr | Regeleinrichtung fuer eine verstellpumpe |
DE3919175A1 (de) * | 1989-06-12 | 1990-12-13 | Hydromatik Gmbh | Regeleinrichtung fuer eine verstellbare pumpe |
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1997
- 1997-12-18 DE DE19756600A patent/DE19756600C1/de not_active Expired - Fee Related
-
1998
- 1998-11-12 DE DE59808896T patent/DE59808896D1/de not_active Expired - Fee Related
- 1998-11-12 EP EP98121603A patent/EP0924427B1/de not_active Expired - Lifetime
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DE3034115A1 (de) * | 1980-09-11 | 1982-05-19 | Mannesmann Rexroth GmbH, 8770 Lohr | Leistungsregler |
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EP0781923A1 (de) * | 1994-09-14 | 1997-07-02 | Komatsu Ltd. | Kapauitätsregelung für hydraulische pumpe mit veränderlicher fördermenge |
DE19626793C1 (de) | 1996-07-03 | 1997-06-26 | Brueninghaus Hydromatik Gmbh | Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0939225A3 (de) * | 1998-02-26 | 2000-06-14 | Brueninghaus Hydromatik Gmbh | Leistungsregeleinrichtung für mehrere verstellbare Hydropumpen |
EP1304482A2 (de) * | 2001-10-18 | 2003-04-23 | Brueninghaus Hydromatik Gmbh | Summenleistungsregler und Druckmittler |
EP1304482A3 (de) * | 2001-10-18 | 2005-09-07 | Brueninghaus Hydromatik Gmbh | Summenleistungsregler und Druckmittler |
Also Published As
Publication number | Publication date |
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DE59808896D1 (de) | 2003-08-07 |
EP0924427B1 (de) | 2003-07-02 |
DE19756600C1 (de) | 1999-08-26 |
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