EP0924427B1 - Power control mechanism - Google Patents

Power control mechanism Download PDF

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Publication number
EP0924427B1
EP0924427B1 EP98121603A EP98121603A EP0924427B1 EP 0924427 B1 EP0924427 B1 EP 0924427B1 EP 98121603 A EP98121603 A EP 98121603A EP 98121603 A EP98121603 A EP 98121603A EP 0924427 B1 EP0924427 B1 EP 0924427B1
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EP
European Patent Office
Prior art keywords
valve body
regulating device
capacity regulating
restrictor
restrictor valve
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.)
Expired - Lifetime
Application number
EP98121603A
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German (de)
French (fr)
Other versions
EP0924427A1 (en
Inventor
Dieter Dittmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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Publication of EP0924427A1 publication Critical patent/EP0924427A1/en
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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 adjusting 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 working in parallel Power control device according to the preamble of claim 1 comprises.
  • the two Power control devices are operated by a pressure control device common to the hydraulic pumps driven.
  • the known power control devices each include a so-called Hyperbolic regulator, which acts via a swivel lever 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 in 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 however, not of a hyperbolic regulator 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 results in inaccurate control characteristics.
  • 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 needs to 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 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 the 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 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 between the inlet and the outlet of the throttle valve depends 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 set.
  • 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 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 port.
  • 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 connection 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 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 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 established.
  • 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.
  • Another spring plate 47 of the return spring 42 lies on the proportional valve body 41 of the proportional valve 9.
  • 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 nested 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-regulated 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 represents the throttle element, which is the delivery volume in the flow control specifies for the consumer connected to the working line output A.
  • On 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, the displacement volume of the Hydraulic pump 4.
  • a pressure relief valve 55 is provided, which Working pressure in the working line 3 is 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 thus achieved. 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.
  • 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 adjusted by the adjusting element 45.
  • a major 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.
  • 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.
  • Limiting power of the power control device 1 according to the invention is variable predetermined. 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.

Description

Die Erfindung betrifft ein Leistungsregelventil zum Begrenzen der Leistung zumindest einer an dem Leistungsregelventil angeschlossenen, mittels einer Verstellvorrichtung verstellbaren Hydropumpe.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 adjusting device adjustable hydraulic pump.

Eine Leistungsregeleinrichtung nach dem Oberbegriff des Anspruchs 1 ist z. B. aus der DE 196 26 793 C1 bekannt. In dieser Druckschrift wird eine hydraulische Regeleinrichtung beschrieben, die für zwei parallel arbeitende Hydropumpen jeweils ein Leistungsregeleinrichtung nach dem Oberbegriff des Anspruchs 1 umfaßt. Die beiden Leistungsregeleinrichtungen werden von einer den Hydropumpen gemeinsamen DruckRegeleinrichtung angesteuert.A power control device according to the preamble of claim 1 is such. B. from the DE 196 26 793 C1 known. In this publication a hydraulic Control device described, each for two hydraulic pumps working in parallel Power control device according to the preamble of claim 1 comprises. The two Power control devices are operated by a pressure control device common to the hydraulic pumps driven.

Die bekannten Leistungsregeleinrichtungen umfassen jeweils einen sogenannten Hyperbelregler, der über einen Schwenkhebel auf ein als Leistungsregelventil wirkendes Proportionalventil zurückwirkt. Der Schwenkhebel ist mittels eines als Schwenkkolben ausgebildeten Angriffselements mit dem Stellkolben der Verstellvorrichtung der jeweils zugeordneten Hydropumpe verbunden. In dem Stellkolben ist für das Angriffselement eine Druckkammer geschaffen, die mit der Arbeitsleitung der zugeordneten Hydropumpe in Verbindung steht. Das Angriffselement wird von dem Stellkolben der Verstellvorrichtung mitgeführt, so daß sich der Hebelarm, über welchen das Angriffselement an dem Schwenkhebel angreift mit zunehmendem Fördervolumen der zugeordneten Hydropumpe verlängert. Der Stellkolben der Verstellvorrichtung ist einerseits mit dem Arbeitsdruck in der Arbeitsleitung der zugeordneten Hydropumpe und andererseits mit einem Gegendruck beaufschlagt, der durch das Proportionalventil eingestellt wird. Der von dem Proportionalventil eingestellte Gegendruck hängt von der Rückwirkung über den Schwenkwinkel ab. Diese Rückwirkung ist einerseits von dem Druck in der Arbeitsleitung der zugeordneten Hydropumpe und andererseits von dem Hebelarm abhängig, mit welchem das Angriffselement an dem Schwenkhebel angreift. Durch diese Konstellation ergibt sich eine hyperbolische Regelkennlinie, d. h. bei Erreichen der vorgegebenen Maximalleistung regelt die Leistungsregeleinrichtung die Hydropumpe auf eine konstante Leistung, also auf ein konstantes Produkt aus Arbeitsdruck in der Arbeitsleitung und Fördervolumen der Hydropumpe ein.The known power control devices each include a so-called Hyperbolic regulator, which acts via a swivel lever 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. There is one in the actuating piston for the engagement element Pressure chamber created that with the working line of the associated hydraulic pump in Connection is established. 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 in 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.

Dabei wird jedoch davon ausgegangen, daß das Fördervolumen der Hydropumpe ausschließlich von der durch den Stellkolben der Verstellvorrichtung vorgegebenen Ausschwenkung abhängt. Diese Voraussetzung trifft jedoch nur dann zu, wenn die Hydropumpe durch den Antriebsmotor mit einer konstanten Drehzahl angetrieben wird. However, it is assumed that the delivery volume of the hydraulic pump exclusively from that specified by the adjusting piston of the adjusting device Pivoting depends. However, this requirement only applies if the Hydraulic pump is driven by the drive motor at a constant speed.

Die bekannte Leistungsregeleinrichtung ist daher für Antriebssysteme mit variabler Antriebsdrehzahl nicht einsetzbar. Ein weiterer Nachteil bei der bekannten Leistungsregeleinrichtung ist darin zu sehen, daß die bekannte Leistungsregeleinrichtung mit dem Stellkolben der Verstellvorrichtung verbunden werden muß, d. h. an der Verstellvorrichtung der Hydropumpe montiert werden muß. Die entsprechende Verbindung zwischen dem Schwenkhebel und dem Stellkolben erfordert einen zusätzlichen konstruktiven Aufwand. Zudem läßt sich die gleiche konstruktive Lösung nicht bei allen Typen der zu verwendenden Hydropumpen in gleicher Weise verwirklichen und es ist für jede Type der Hydropumpe eine Sonderkonstruktion erforderlich.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. In addition, 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.

Zwar ist aus der DE-OS 24 61 897 ein Leistungsregelventil bekannt, das von der Antriebsdrehzahl der Hydropumpe unabhängig ist. Dieses Leistungsregelventil bedient sich jedoch nicht eines Hyperbelreglers, der über einen Schwenkhebel auf ein Proportionalventil zurückwirkt. Statt dessen weist dieses in der Arbeitsleitung der Hydropumpe vorgesehene Leistungsregelventil einen Ventilkörper auf, dessen Stirnseite von dem Druckfluid angeströmt wird. Der entstehende Druck bewirkt eine Verschiebung des Ventilkörpers gegen eine Rückstellfeder. Mit zunehmender Verschiebung des Ventilkörpers wird ein Regelschlitz geschlossen. Der Regelschlitz ist geometrisch so ausgeformt, daß die Veränderung des Drosselquerschnitts als Funktion des Verschiebewegs des Ventilkörpers nicht linear ist sondern so bestimmt ist, daß das Produkt aus Arbeitsdruck und Drosselquerschnitt zumindest näherungsweise konstant ist. Auf diese Weise wird zumindest annähernd eine Leistungsregelung erreicht.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 however, not of a hyperbolic regulator 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.

Nachteilig bei dem aus der DE-OS 24 61 897 bekannten Leistungsregelventil ist jedoch, daß dessen Regelcharakteristik für viele Anwendungsfälle zu ungenau ist. Der Staudruck an der Stirnseite des Ventilkolbens ist eine relativ ungenaue Regelgröße und wird von dem Druckabfall an dem Regelschlitz beeinflußt. Der Drosselquerschnitt des Regelschlitzes wirkt daher auf den Verschiebeweg des Ventilkörpers zurück, so daß sich eine relativ ungenaue Regelcharakteristik ergibt. Zudem hängt der Staudruck auch von der Viskosität und somit der Temperatur des Druckfluids ab. Dieses Leistungsregelventil konnte sich daher gegenüber Leistungsregelventilen mit einem exakten Hyperbelregler nicht durchsetzen. Ferner ist nachteilig, daß zum Verändern der Regelleistung der Regelschlitz verändert werden muß. Bei hohen Leistungen ergeben sich sehr hohe Federkräfte, die sehr große Federn erfordern.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 results in inaccurate control characteristics. 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 needs to be changed. At high powers there are very high spring forces, which are very require large feathers.

Es ist daher die Aufgabe der vorliegenden Erfindung, eine Leistungsregeleinrichtung mit einem einen Schwenkhebel aufweisenden Hyperbelregler zu schaffen, die auch zur Ansteuerung von Hydropumpen geeignet ist, die nicht mit konstanter Drehzahl angetrieben werden.It is therefore the object of the present invention to provide a power control device to create a swivel lever hyperbola regulator, which also for Control of hydraulic pumps is suitable, which is not driven at constant speed become.

Die Aufgabe wird durch die kennzeichnenden Merkmale des Anspruchs 1 in Verbindung mit den gattungsbildenden Merkmalen gelöst.The object is in connection with the characterizing features of claim 1 solved with the generic features.

Der Erfindung liegt das Konzept zugrunde, den Hyperbelregler mit dem Schwenkhebel in einer von der Hydropumpe baulich losgelösten Einheit zu integrieren. Der Schwenkhebel wird über das Angriffselement nicht mit dem Stellkolben der Verstellvorrichtung der Hydropumpe verbunden. Statt dessen ist ein Drosselventil vorgesehen, dessen Ventilkörper das Angriffselement mitführt. Das Drosselventil drosselt die Strömung in der der Hydropumpe zugeordneten Arbeitsleitung. Der Druckabfall an den Drosselventilen kann zur Ansteuerung der Verstellvorrichtung der Hydropumpe herangezogen werden. Da eine derartige Steuerung z. B. bei förderstromgeregelten Hydropumpen ohnehin vorhanden und üblich ist, ergibt sich für die Ansteuerung der Hydropumpe kein zusätzlicher konstruktiver Aufwand. Die erfindungsgemäße Leistungsregeleinrichtung ist vielmehr gegen die bei förderstromgeregelten Hydropumpen übliche festverstellbare Drossel in der Arbeitsleitung der Hydropumpe auszutauschen. Auf diese Weise können bereits im Betrieb befindliche Hydropumpen auch mit einer erfindungsgemäßen Leistungsregeleinrichtung nachgerüstet werden.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. There one such control z. B. already available in flow-controlled hydraulic pumps and Is usual, there is no additional constructive for the control of the hydraulic pump Expenditure. The power control device according to the invention is rather against 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.

Die Leistungsregeleinrichtung ist dabei vollkommen unabhängig von der Antriebsdrehzahl der zugeordneten Hydropumpe. Ferner kann die erfindungsgemäße Leistungsregeleinrichtung universell für verschiedenste Typen von Hydropumpen eingesetzt werden, da eine mechanische Verbindung zwischen dem Schwenkhebel und dem Stellkolben der Verstellvorrichtung nicht geschaffen werden muß. Es genügt, die erfindungsgemäße Leistungsregeleinrichtung in die Arbeitsleitung einzuschleifen. Dennoch arbeitet die erfindungsgemäße Leistungsregeleinrichtung aufgrund des Hyperbelreglers äußerst exakt.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 the 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.

Die Ansprüche 2 bis 13 beinhalten vorteilhafte Weiterbildungen der Erfindung.Claims 2 to 13 contain advantageous developments of the invention.

Der Drossel-Ventilkörper des Drosselventils kann entsprechend Anspruch 2 von der Druckdifferenz zwischen zwei Drosselventil-Kammern beaufschlagt werden, wobei die erste Drosselventil-Kammer mit der Arbeitsleitung und die zweite Drosselventil-Kammer mit einem Steuerausgang des Proportionalventils verbunden ist. Entsprechend Anspruch 3 kann der Drossel-Ventilkörper vorteilhaft als Hohlkolben ausgebildet sein, wobei eine der beiden Drosselventil-Kammern entsprechend Anspruch 4 im Inneren des Drossel-Ventilkörpers integriert sein kann. Dabei kann die entsprechende Drosselventil-Kammer mit einem Meßkolben verschlossen sein, der sich an einem Gehäuseteil der Leistungsregeleinrichtung abstößt.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. According to claim 3 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.

Entsprechend Anspruch 5 kann im Mantelbereich des Drossel-Ventilkörpers eine Ringnut ausgebildet sein, an der die mit einem den Drossel-Ventilkörper umgebenden Drossel-Zylinderkörper zusammenwirkende Steuerkante entsprechend Anspruch 5 ausgebildet ist. Der Drosselquerschnitt zwischen dem Zulauf und dem Ablauf des Drosselventils hängt dabei von der Stellung des Drossel-Ventilkörpers ab.According to claim 5, an annular groove 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 between the inlet and the outlet of the throttle valve depends thereby from the position of the throttle valve body.

Das Angriffselement kann entsprechend Anspruch 6 in dem Drossel-Ventilkörper verschiebbar gelagert sein und bis in die Hohlbohrung des Drossel-Ventilkörpers ragen, so daß es vom Arbeitsdruck der Arbeitsleitung gegen den Schwenkhebel beaufschlagt wird. Auf diese Weise ergibt sich eine besonders kompakte Bauweise. Dabei ist die Bewegungsrichtung des Angriffselements vorzugsweise entsprechend Anspruch 7 senkrecht zur Bewegungsrichtung des Drossel-Ventilkörpers gerichtet, so daß die Stellung des Drossel-Ventilkörpers den Hebelarm und der Arbeitsdruck die auf den Hebelarm ausgeübte Kraft festlegt.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. This results in a particularly compact design. Here is 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.

Entsprechend Anspruch 8 kann ein justierbares Anschlagelement für den Drossel-Ventilkörper vorgesehen sein, um den maximalen Förderstrom der Hydropumpe variabel festzulegen.According to claim 8, an adjustable stop element for the throttle valve body be provided to vary the maximum flow rate of the hydraulic pump set.

Das Proportionalventil kann entsprechend Anspruch 9 einen mit der Arbeitsleitung verbundenen ersten Eingangsanschluß, einen mit einem Druckmedium-Tank verbundenen zweiten Eingangsanschluß und einem mit dem Drosselventil verbundenen Steuerausgang aufweisen. Der Druck an dem Steuerausgang ist dabei einerseits zu dem Arbeitsdruck an dem mit der Arbeitsleitung verbundenen Eingangsanschluß und andererseits der über die Rückwirkung auf das Proportionalventil einwirkenden Rückwirkungskraft proportional. Der Schwenkhebel greift entsprechend Anspruch 10 an dem Proportional-Ventilkörper des Proportionalventils vorzugsweise so an, daß der Proportional-Ventilkörper mit zunehmender Kraftbeaufschlagung des Schwenkhebels durch das Angriffselement den Steuerausgang zunehmend mit dem ersten Eingangsanschluß verbindet. Eine proportionale, lineare Ansteuerung des Proportionalventils kann dadurch erreicht werden, daß der Schwenkhebel den Proportional-Ventilkörper entsprechend Anspruch 11 gegen eine Rückstellfeder beaufschlagt. 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 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 port. 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.

Vorzugsweise ist die Vorspannung der Rückstellfeder über ein Justierelement entsprechend Anspruch 12 einstellbar, so daß die Begrenzungsleistung, auf welche die erfindungsgemäße Leistungsregeleinrichtung die angeschlossenen Hydropumpe begrenzt, einstellbar ist. Die Einstellung kann entweder manuell z. B. mit einer Einstellschraube erfolgen oder aber über eine hydraulische oder elektrische Ansteuerung entsprechend Anspruch 13. Vorzugsweise ist dazu ein Proportional-Elektromagnet vorgesehen, über welchen die Vorspannung der Rückstellfeder variabel einstellbar ist.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.

Die Erfindung wird nachfolgend unter Bezugnahme auf die Zeichnung näher beschrieben. In der Zeichnung zeigen:

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.
The invention is described below with reference to the drawing. The drawing shows:
Fig. 1
a first embodiment of a power control device according to the invention in a partially sectioned illustration with a switching example for the hydraulic circuit; and
Fig. 2
a second embodiment of a power control device according to the invention, the difference from the embodiment of FIG. 1 is that the bias of the return spring of the proportional valve is adjustable via a proportional solenoid; and
Fig. 3
the control characteristic of the valves shown in Fig. 1 and Fig. 2 in a PQ diagram.

Bei dem in Fig. 1 dargestellten Ausführungsbeispiel ist die erfindungsgemäße Leistungsregeleinrichtung allgemein mit dem Bezugszeichen 1 versehen. Die Leistungsregeleinrichtung 1 weist vier Anschlüsse auf, nämlich einen Arbeitsleitungs-Eingang P, einen Arbeitsleitungs-Ausgang A, einen mit einem Druckmedium-Tank 2 verbundenen Tankanschluß T und einen Melde-Anschluß X. Der Arbeitsleitungs-Eingang P ist über die Arbeitsleitung 3 mit dem Arbeitsleitungs-Anschluß B der Hydropumpe 4 verbunden. An dem Arbeitsleitungs-Ausgang A ist bzw. sind ein oder mehrere Verbraucher angeschlossen. Der Melde-Anschluß X ist über eine Melde-Leitung 5 mit dem Load-Sensing Anschluß X der noch näher zu beschreibenden Ventilsteuereinheit 6 der Hydropumpe 4 verbunden. Der Melde-Anschluß X und der Arbeitsleitungs-Ausgang A sind im Gehäuse 7 der Leistungsregeleinrichtung 1 im dargestellten Ausführungsbeispiel miteinander verbunden. Der Melde-Ausgang X und der Arbeitsleitungs-Ausgang A können jedoch auch zu einem gemeinsamen Ausgang vereinigt sein, so daß die Melde-Leitung 5 von der Arbeitsleitung 3 stromabwärts des Arbeitsleitungs-Ausgangs A, vorzugsweise z. B. unmittelbar an dem angeschlossenen Verbraucher, abzweigt.In the embodiment shown in Fig. 1 is the invention Power control device generally provided with the reference number 1. 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. There is one or more at the working line exit A Consumers connected. The message connection 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.

Die erfindungsgemäße Leistungsregeleinrichtung 1 gliedert sich im wesentlichen in ein Drosselventil 8 und ein Proportionalventil 9, die im dargestellten Ausführungsbeispiel zu einer gemeinsamen Ventileinheit in einem gemeinsamen Gehäuse 7 baulich vereinigt sind.The power control device 1 according to the invention 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.

Das Drosselventil 8 besteht aus einem Drossel-Ventilkörper 10, der in einem den Drossel-Ventilkörper 10 umgebenen Drossel-Zylinderkörper 11 in Längsrichtung bewegbar ist. Der Drossel-Ventilkörper 10 ist im dargestellten Ausführungsbeispiel als Hohlkolben ausgebildet und weist eine als Sackbohrung ausgeführte Hohlbohrung 12 auf. Die Hohlbohrung 12 ist über eine Querbohrung 13 mit einer an der Mantelfläche des Drossel-Ventilkörpers 10 ausgebildete Ringnut 14 verbunden. An dem Drossel-Zylinderkörper 11 ist ein mit dem Arbeitsleitungs-Eingang P verbundener Zulauf 15 und ein mit dem Arbeitsleitungs-Ausgang A verbundener Ablauf 16, z. B. in Form von Radialschlitzen, ausgebildet.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.

Der Drossel-Ventilkörper 10 ist in Fig. 1 in seiner Stellung mit maximalem Drosselquerschnitt dargestellt. Wenn sich der Drossel-Ventilkörper 10 in Fig. 1 nach unten bewegt, verringert sich der Drosselquerschnitt des Drosselventil 8 zunehmend, da sich die Steuerkante 17 am in Fig. 1 oberen Ende der Ringnut 14 mit der Verschiebung des Drossel-Ventilkörpers 10 ebenfalls nach unten bewegt und die Verbindung zu dem Ablauf 16 einengt. Die in Fig. 1 dargestellte Stellung des Drossel-Ventilkörpers 10 mit maximalem Drossel-Querschnitt und somit maximalem Fördervolumen der angeschlossenen Hydropumpe 4 läßt sich durch das justierbare Anschlagelement 18 variabel einstellen. Das justierbare Anschlagelement 18 ist in dem dargestellten Ausführungsbeispiel als Gewindebolzen ausgebildet und läßt sich in den Anschlußstutzen 19 einschrauben und mittels der Mutter 20 und der Kontermutter 21 fixieren.The throttle valve body 10 is in its position with the maximum in FIG Throttle cross section shown. When the throttle valve body 10 in Fig. 1 is down moves, 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 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.

Die Stellung des Drossel-Ventilkörpers 10 ist durch die Druckdifferenz zwischen einer im Inneren des Drossel-Ventilkörpers 10 ausgebildeten ersten Drosselventil-Kammer 22 und einer zweiten im Ausführungsbeispiel an dem Anschlußstutzen 19 an der in Fig. 1 oberseitigen Stirnseite des Drossel-Ventilkörpers 10 ausgebildeten zweiten Drosselventil-Kammer 23 angesteuert. Die erste Drosselventil-Kammer 22 ist im dargestellten Ausführungsbeispiel Teil der Hohlbohrung 12 und ist somit über den Arbeitsleitungs-Eingang P mit der Arbeitsleitung 3 verbunden. Die erste Drosselventil-Kammer 22 ist durch einen Meßkolben 24, der sich an der Verschlußkappe 25 des Gehäuses 7 abstützt, verschlossen. Bei Druckerhöhung in der ersten Drosselventil-Kammer 22 bewegt sich der Drossel-Ventilkörper 10 daher in Fig. 1 nach oben, während sich der Drossel-Ventilkörper 10 bei einer Druckerhöhung in der zweiten Drosselventil-Kammer 23 in Fig. 1 nach unten bewegt. Die zweite Drosselventil-Kammer 23 ist über eine in dem Anschlußstutzen 19 durch einen Verschlußkörper 26 endseitig verschlossene Steuerleitung 27 mit einem Steuerausgang A' des Proportionalventils 9 verbunden.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. When the pressure in the first throttle valve chamber 22 increases, the pressure moves Throttle valve body 10 therefore upward in FIG. 1 while the throttle valve body 10 with a pressure increase in the second throttle valve chamber 23 in Fig. 1 down emotional. The second throttle valve chamber 23 is via a in the connecting piece 19th by a closure body 26 closed control line 27 with a Control output A 'of the proportional valve 9 connected.

In dem Gehäuse 7 der erfindungsgemäßen Leistungsregeleinrichtung 1 ist ein um eine Schwenkachse 30 schwenkbarer Schwenkhebel 31 angeordnet, an welchem ein in einer Radialbohrung 32 des Drossel-Ventilkörpers 10 angeordnetes, kolbenartiges Angriffselement 35 über einen Gleitschuh 33 angreift. Die Stirnfläche 34 des Angriffselements 35 befindet sich im Ausführungsbeispiel innerhalb der Hohlbohrung 12 und wird somit von dem in der Arbeitsleitung 3 herrschenden Arbeitsdruck gegen den Schwenkhebel 31 beaufschlagt. Die Bewegungsrichtung des Angriffselements 35 verläuft dabei senkrecht zu der Bewegungsrichtung des Drossel-Ventilkolbens 10. Während der Arbeitsdruck in der Arbeitsleitung 3 die Kraft festlegt, mit welcher das Angriffselement 35 auf den Schwenkhebel 31 einwirkt, wird der Hebelarm mit welchem das Angriffselement 35 an dem Schwenkhebel 31 angreift durch die Stellung des Drossel-Ventilkörpers 10 festgelegt. Beim Verschieben des Drossel-Ventilkörpers 10 in Fig. 1 nach unten gleitet der Gleitschuh 33 auf der Oberfläche des Schwenkhebels 31 nach unten, so daß sich der Hebelarm verkürzt. Insgesamt wirkt daher über den Schwenkhebel 31 ein Drehmoment auf das Proportionalventil 9 zurück, das dem Produkt aus dem Arbeitsdruck in der Arbeitsleitung 3 und dem Drosselquerschnitt des Drosselventils 8, also der von dem Drosselventil 8 festgelegten hydraulischen Leistung proportional ist.In the housing 7 of the power control device 1 according to the invention is one by one 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. During the 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 established. When moving the throttle valve body 10 in Fig. 1 down the Slide 33 on the surface of the pivot lever 31 downward, so that the Lever arm shortened. Overall, therefore, a torque acts on the pivot lever 31 the proportional valve 9 back, the product of the working pressure in the Working line 3 and the throttle cross section of the throttle valve 8, that of the Throttle valve 8 is proportional hydraulic power.

Die über den Schwenkhebel 31 vermittelte Rückwirkkraft wirkt über den Stößel 40 auf den Proportional-Ventilkolben 41 des Proportionalventils 9 ein und verschiebt den Proportional-Ventilkörper 41 gegen die von der Rückstellfeder 42 aufgebrachte Rückstellkraft in Fig. 1 nach unten. Der Proportional-Ventilkörper 41 ist in einem Proportional-Zylinderkörper 43 bewegbar, der den Proportional-Ventilkörper 41 umgibt und einen mit der Arbeitsleitung 3 verbundenen ersten Eingangsanschluß P', einen mit dem Druckmedium-Tank 2 verbundenen zweiten Eingangsanschluß T' und einem über die Steuerleitung 27 mit dem Drosselventil 8 verbundenen Steuerausgang A' aufweist.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.

In der in Fig. 1 dargestellten Grundstellung ist der Druckmedium-Tank 2 mit dem Steueranschluß A' verbunden und somit die zweite Drosselventil-Kammer 23 zum Druckmedium-Tank T hin belüftet. Das Drosselventil 8 arbeitet mit dem durch das justierbare Anschlagelement 18 vorgegebenen Maximalöffnungsquerschnitt. Bei Ansprechen der Leistungsbegrenzung wird jedoch der Proportional-Ventilkörper 41 in Fig. 1 nach unten bewegt, so daß die Trennwand 44 des Proportional-Ventilkörpers 41 zunehmend die Verbindung zwischen dem mit der Arbeitsleitung 3 verbundenen Eingangsanschluß P' und dem Steuerausgang A' freigibt. Dadurch wird die zweite Drosselventil-Kammer 23 mit Steuerdruck beaufschlagt und der Drossel-Ventilkörper 10 in Fig. 1 nach unten bewegt, so daß sich der Drosselquerschnitt des Drosselventils 8 verringert. Dadurch verkürzt sich der Hebelarm, mit welchem das Angriffselement 35 auf den Schwenkhebel 31 einwirkt, so daß ein Gleichgewichtsszustand gefunden wird. Wie beschrieben wird das Produkt aus Arbeitsdruck in der Arbeitsleitung 3 und variablem Drosselquerschnitt des Drosselventils 8 und somit die hydraulische Leistung auf einen konstanten Wert eingeregelt.In the basic position shown in Fig. 1, the pressure medium tank 2 with the Control connection A 'connected and thus the second throttle valve chamber 23 to Pressurized medium tank T vented. The throttle valve 8 works with that by adjustable stop element 18 predetermined maximum opening cross-section. at However, the proportional valve body 41 in FIG. 1 moves downward so that the partition 44 of the proportional valve body 41st increasingly the connection between that connected to the working line 3 Input terminal P 'and the control output A' releases. This will make the second Throttle valve chamber 23 is charged with control pressure and the throttle valve body 10 in 1 moves downward, so that the throttle cross section of the throttle valve 8 reduced. This shortens the lever arm with which the engagement element 35 opens the pivot lever 31 acts so that a state of equilibrium is found. How the product of working pressure in the working line 3 and variable is described Throttle cross section of the throttle valve 8 and thus the hydraulic power to one constant value adjusted.

Da der Steuerdruck in der Drosselventil-Kammer 23 neben der Ventilstellung des Proportionalventils 9 auch von dem am Eingangsanschluß P' des Proportionalventils 9 anstehenden Arbeitsdruck abhängt muß bezüglich des Arbeitsdrucks eine Kompensation erfolgen. Dies geschieht beim dargestellten Ausführungsbeispiel durch die Drosselventil-Kammer 22 und den Meßkolben 24.Since the control pressure in the throttle valve chamber 23 in addition to the valve position of the Proportional valve 9 also from that at the input port P 'of the proportional valve 9 current working pressure must compensate for the working pressure respectively. In the exemplary embodiment shown, this is done by the throttle valve chamber 22 and the volumetric flask 24.

Als Proportionalventil 9 kann ein hydraulisches Proportionalventil jeder bekannten Bauart Verwendung finden. Die Vorspannung der Rückstellfeder 42 ist vorzugsweise über ein Justierelement, das an dem Federteller 46 der Rückstellfeder 42 angreift, einstellbar. Ein weiterer Federteller 47 der Rückstellfeder 42 liegt an dem Proportional-Ventilkörper 41 des Proportionalventils 9 an. Auf diese Weise ist die Begrenzungsleistung, auf welche die erfindungsgemäße Leistungsregeleinrichtung begrenzt, einstellbar. Im in Fig. 1 dargestellten Ausführungsbeispiel ist das Justierelement als Gewindebolzen 45 ausgebildet und mittels einer Mutter 47 und einer Kontermutter 48 fixierbar. Die Rückstellfeder 42 ist im dargestellten Ausführungsbeispiel aus zwei ineinander angeordneten Rückstellfedern 42a und 42b zusammengesetzt.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. On 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. In Fig. 1 In the illustrated embodiment, 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 nested return springs 42a and 42b put together.

In Fig. 1 ist als Beispiel die äußere Beschaltung der erfindungsgemäßen Leistungsregeleinrichtung am Beispiel einer förderstromgeregelten Hydropumpe 4 dargestellt. Die Verwendung der erfindungsgemäßen Leistungsregeleinrichtung 1 ist jedoch nicht auf diesen Anwendungsfall beschränkt.In Fig. 1 is an example of the external wiring of the invention Power control device using the example of a flow-regulated hydraulic pump 4 shown. The use of the power control device 1 according to the invention is but not limited to this application.

Die Leistungregeleinrichtung 1 ist in die Arbeitsleitung 3 eingeschleift und stellt gleichzeitig das Drosselelement dar, das bei der Förderstromregelung das Fördervolumen für den an dem Arbeitsleitungs-Ausgang A angeschlossenen Verbraucher vorgibt. Ein Förderstromregelventil 50 erfaßt den Druckabfall über dem Drosselventil 8 und regelt in Abhängigkeit davon über die im Ausführungsbeispiel zwei Stellzylinder 51 und 52 und zwei Stellkolben 53 und 54 aufweisende Verstellvorrichtung das Fördervolumen der Hydropumpe 4. Ferner ist ein Druckbegrenzungsventil 55 vorgesehen, das den Arbeitsdruck in der Arbeitsleitung 3 auf einen zulässigen Maximalwert begrenzt. Das Förderstromregelventil 50 und das Druckbegrenzungsventil 55 sind im dargestellten Ausführungsbeispiel als 3/2-Wegeventile ausgebildet und jeweils durch eine Rückstellfeder 56 bzw. 57 in ihre Grundstellung beaufschlagt.The power control device 1 is looped into the working line 3 and provides at the same time represents the throttle element, which is the delivery volume in the flow control specifies for the consumer connected to the working line output A. On 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, the displacement volume of the Hydraulic pump 4. Furthermore, a pressure relief valve 55 is provided, which Working pressure in the working line 3 is 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.

Das Förderstromregelventil 50 und das Druckbegrenzungsventil 55 sind über eine Verbindungsleitung 60 mit der Arbeitsleitung 3 und über eine Verbindungsleitung 61 mit dem Druckmedium-Tank 2 verbunden. Das Druckbegrenzungsventil 55 befindet sich im dargestellten Ausführungsbeispiel in der Verbindungsleitung 62 zwischen dem Förderstromregelventil 50 und der Druckkammer 63 des Stellzylinders 51. Bei einer Erhöhung des Druckabfalls über dem Drosselventil 8 erhöht das Förderstromregelventil 50 den Druck in der Leitung 62 und somit in der Stellkammer 63, so daß die Hydropumpe 4 zurückgeschwenkt wird und somit der Druckabfall über dem Drosselventil 8 sinkt. Auf diese Weise wird ein Gleichgewichtszustand erreicht. Wenn umgekehrt der Druckabfall sinkt verringert das Förderstromregelventil 50 den Druck in der Stellkammer 63 und die Hydropumpe 4 wird bis zum Erreichen des Gleichgewichtszustands weiter ausgeschwenkt. Beim Überschreiten des maximal zulässigen Arbeitsdrucks in der Arbeitsleitung 3 erhöht das Druckbegrenzungsventil 55 den Druck in der Stellkammer 63 und schwenkt die Hydropumpe 4 soweit zurück, daß der Arbeitsdruck in der Arbeitsleitung 3 auf den zulässigen Maximaldruck begrenzt wird.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 thus achieved. 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.

Das Zusammenwirken der erfindungsgemäßen Leistungsregeleinrichtung 1, des Förderstromregelventils 50 und des Druckbegrenzungsventils 55 wird nachfolgend anhand von Fig. 3 beschrieben.The interaction of the power control device 1 according to the invention Flow control valve 50 and the pressure relief valve 55 is subsequently based described by Fig. 3.

Fig. 3 zeigt ein p-Q-Diagramm, wobei p den Arbeitsdruck in der Arbeitsleitung 3 und Q das von der Hydropumpe 4 abgegebene Fördervolumen symbolisieren. Solange die von der erfindungsgemäßen Leistungsregeleinrichtung 1 vorgegebene Maximalleistung noch nicht erreicht ist, regelt das Förderstromregelventil 50 das Fördervolumen der Hydropumpe 4 im Regelbereich 60 in Fig. 3 auf ein konstantes Fördervolumen Qmax ein, das durch das justierbare Anschlagelement 18 verbraucherangepaßt vorgegeben wird. Sobald die zulässige Maximalleistung der Hydropumpe 4 erreicht wird, regelt die erfindungsgemäße Leistungsregeleinrichtung 1 entlang der Hyperbel 61 das Produkt aus Arbeitsdruck p und Fördervolumen Q auf einen konstanten Wert ein, so daß eine Überlastung der Hydropumpe 4 vermieden wird. Wenn jedoch in der Arbeitsleitung 3 der maximal zulässige Arbeitsdruck Pmax überschritten wird, regelt das Druckbegrenzungsventil 55 die Hydropumpe 4 zurück, um eine Drucküberlastung des Systems zu vermeiden. Die Maximalleistung, auf welche die erfindungsgemäße Leistungsregeleinrichtung 1 einregelt, ist durch das Justierelement 45 einstellbar.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. As long as the preset of the inventive power control device 1, maximum power is not yet reached, 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. As soon as the permissible maximum output of the hydraulic pump 4 is reached, the power control device 1 according to the invention 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. However, if the maximum permissible working pressure P max is exceeded in the working line 3, 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 adjusted by the adjusting element 45.

Ein wesentlicher Vorteil der erfindungsgemäßen Leistungsregeleinrichtung 1 gegenüber an der Verstellvorrichtung der Hydropumpe 4 angreifenden Leistungsregeleinrichtungen liegt darin, daß die Leistungsregelung von der Drehzahl der die Hydropumpe 4 antreibenden Antriebswelle 58 unabhängig ist. Bekannte Leistungsregeleinrichtungen regeln das Produkt aus Arbeitsdruck und Schwenkwinkel der Hydropumpe 4 ebenfalls mit einem Schwenkhebelmechanismus auf einen konstanten Wert ein. Das Fördervolumen der Hydropumpe ist jedoch nur dann dem Schwenkwinkel proportional, wenn die Antriebsdrehzahl konstant ist. Bei einigen Antriebskonzepten ist dies nicht sichergestellt und dort kann eine bekannte Leistungsregeleinrichtung nicht zum Einsatz kommen. Ein weiterer erheblicher Vorteil liegt darin, daß die bekannte Leistungsregeleinrichtung als von der Hydropumpe 4 getrennte separate Ventileinheit ausgebildet ist. Eine mechanische Verbindung mit der Verstellvorrichtung 51 bis 54 der Hydropumpe 4 ist nicht erforderlich. Die erfindungsgemäße Leistungsregeleinrichtung 1 wird lediglich in die Arbeitsleitung 3 eingeschleift und ist daher vom verwendeten Typ der Hydropumpe 4 vollkommen unabhängig. Dadurch ist eine hohe universelle Einsetzbarkeit der erfindungsgemäßen Leistungsregeleinrichtung 1 gegeben.A major 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. On 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 zeigt ein gegenüber dem Ausführungsbeispiel nach Fig. 1 leicht abgewandeltes zweites Ausführungsbeispiel. Bereits beschriebene Elemente sind mit übereinstimmenden Bezugszeichen versehen, so daß sich insoweit eine wiederholende Beschreibung erübrigt.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.

Der Unterschied zu dem in Fig. 1 dargestellten Ausführungsbeispiel besteht darin, daß die Vorspannung der Rückstellfeder 42 nicht mittels des Gewindebolzens 45 starr einstellbar ist, sondern mittels eines über einen Stößel 70 an dem Federteller 46 angreifenden, im einzelnen nicht weiter dargestellten Proportional-Elektromagneten in Abhängigkeit von einem den Anschlußleitungen 72 und 73 des Proportional-Magneten 41 zuführbaren elektrischen Steuersignals variabel einstellbar ist. Auf diese Weise ist die Begrenzungsleistung der erfindungsgemäßen Leistungsregeleinrichtung 1 variabel vorgebbar. Z. B. können an einer Hydropumpe 4 mehrere Verbraucher jeweils über eine separate Leistungsregeleinrichtung 1 angeschlossen sein. Die Leistungszuweisung für die einzelnen Verbraucher hängt dann z. B. davon ab, wieviele andere Verbraucher zugeschaltet sind. Dies kann durch eine entsprechendes auf den Proportional-Magneten 71 einwirkendes Steuersignal berücksichtigt werden. Hyperbeln anderer Regelleistungen sind in Fig. 3 mit den Bezugszeichen 63 und 64 versehen.The difference from the embodiment shown in Fig. 1 is that 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. In this way it is Limiting power of the power control device 1 according to the invention is variable predetermined. 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.

Claims (13)

  1. A capacity regulating device (1) for limiting the capacity of at least one hydraulic pump (4), which is connected to the capacity regulating device (1), is adjustable by means of an adjusting device (51-54) and delivers to an operating line (3), having a hyperbolic regulator, which reacts on a proportional valve (9) by way of a pivot lever (31), and a working element (35) which is displaceable on the pivot lever (31) so that it is possible to alter the lever arm by means of which the working element (35) works on the pivot lever (31),
    characterised in that
    the capacity regulating device (1) is constructed as a valve unit which is structurally separate from the adjusting device (51-54), and in that
    the working element (35) is carried by a movable restrictor valve body (10) of a restrictor valve (8) arranged in the operating line (3), the position of the restrictor valve body (10) being controlled by a differential pressure which is the difference between the operating pressure of the hydraulic pump (4) in the operating line (3) and a control pressure which is regulated by the proportional valve (9) in dependence on the reaction relayed by the pivot lever (31).
  2. A capacity regulating device according to Claim 1,
    characterised in that
    the restrictor valve body (10) is acted upon by the pressure difference between a first (22) and a second (23) restrictor valve chamber, the first restrictor valve chamber (22) being connected to the operating line (3) and
    the second restrictor valve chamber (23) being connected to a control output (A') of the proportional valve (9) by way of a control line (27).
  3. A capacity regulating device according to Claim 2,
    characterised in that
    the restrictor valve body (10) is constructed as a hollow piston and the restrictor valve body (10) has a hollow bore (12) which is in communication with the operating line (3).
  4. A capacity regulating device according to Claim 3,
    characterised in that
    the first restrictor valve chamber (22) is constructed inside the restrictor valve body (10) and is closed by a measuring piston (24) which is supported on a housing part (25) of the capacity regulating device (1).
  5. A capacity regulating device according to Claim 3 or 4,
    characterised in that
    the hollow bore (12) is connected to an annular groove (14) provided in the casing region of the restrictor valve body (10), said groove connecting an inlet (15) constructed in a restrictor cylinder body (11) surrounding the restrictor valve body (10) to an outlet (16) constructed in the restrictor cylinder body (11) by way of a restrictor cross-section, which depends on the position of the restrictor valve body (10).
  6. A capacity regulating device according to one of Claims 3 to 5,
    characterised in that
    the working element (35) is displaceably mounted in the restrictor valve body (10) and is acted upon in opposition to the pivot lever (31) by the operating pressure in the operating line (3) in that an end face (34) of the working element (35) projects into the hollow bore (12) of the restrictor valve body (10).
  7. A capacity regulating device according to Claim 6,
    characterised in that
    the movement direction of the working element (35) is perpendicular to the movement direction of the restrictor valve body (10).
  8. A capacity regulating device according to one of Claims 1 to 7,
    characterised in that
    an adjustable stop element (18) is provided, against which the restrictor valve body (10) strikes when the maximum delivery rate of the hydraulic pump (4) is reached, said delivery rate being adjustable by means of the stop element (18).
  9. A capacity regulating device according to one of Claims 1 to 8,
    characterised in that
    the proportional valve (9) has a first input connection (P') connected to the operating line (3), a second input connection (T') connected to a pressure-medium tank (2), and a control output (A') connected to the restrictor valve (8) by way of a control line (27).
  10. A capacity regulating device according to Claim 9,
    characterised in that
    the proportional valve (9) has a proportional valve body (41) on which the pivot lever (31) works such that, with an increase in the force acting on the pivot lever (31) as a result of the working element (35), the proportional valve body (41) connects the control output (A') increasingly to the first input connection (P').
  11. A capacity regulating device according to Claim 9 or 10,
    characterised in that
    the pivot lever (31) acts on the proportional valve body (41) in opposition to a resetting spring (42).
  12. A capacity regulating device according to Claim 11,
    characterised in that
    the pre-tension of the resetting spring (42) is adjustable by way of an adjusting element (45; 70, 71).
  13. A capacity regulating device according to Claim 12,
    characterised in that
    the pre-tension of the resetting spring (42) is hydraulically or electrically alterable, particularly by means of a proportional electromagnet (71), for the purpose of specifying the limit capacity of the capacity regulating device (1).
EP98121603A 1997-12-18 1998-11-12 Power control mechanism Expired - Lifetime EP0924427B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19756600A DE19756600C1 (en) 1997-12-18 1997-12-18 Capacity control valve
DE19756600 1997-12-18

Publications (2)

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EP0924427A1 EP0924427A1 (en) 1999-06-23
EP0924427B1 true EP0924427B1 (en) 2003-07-02

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EP (1) EP0924427B1 (en)
DE (2) DE19756600C1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19808127C2 (en) * 1998-02-26 1999-12-09 Brueninghaus Hydromatik Gmbh Power control device
DE10151401A1 (en) * 2001-10-18 2003-05-08 Brueninghaus Hydromatik Gmbh Total power regulator and diaphragm seal
DE102017000761A1 (en) 2017-01-27 2018-08-02 Hydac Drive Center Gmbh supply device

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DE2461897A1 (en) * 1974-12-31 1976-07-08 Bosch Gmbh Robert CONTROL DEVICE FOR A PUMP
DE3034115A1 (en) * 1980-09-11 1982-05-19 Mannesmann Rexroth GmbH, 8770 Lohr PERFORMANCE CONTROLLER
DE3129440A1 (en) * 1981-07-25 1983-02-10 Mannesmann Rexroth GmbH, 8770 Lohr Control device for a variable-delivery pump
US4535966A (en) * 1981-09-26 1985-08-20 Barmag Barmer Maschinenfabrik Aktiengesellschaft Throttle valve
DE3919175A1 (en) * 1989-06-12 1990-12-13 Hydromatik Gmbh CONTROL DEVICE FOR AN ADJUSTABLE PUMP
DE4329164C2 (en) * 1993-08-30 1998-02-19 Brueninghaus Hydromatik Gmbh Hydraulic control valve block
JP3562657B2 (en) * 1994-09-14 2004-09-08 株式会社小松製作所 Capacity control device for variable displacement hydraulic pump

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DE19626793C1 (en) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulic equipment for parallel regulation of hydrostatic displacement pumps

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DE19756600C1 (en) 1999-08-26
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