EP0561153B1 - Capacity regulating device for at least two hydrostatic variable displacement pumps - Google Patents
Capacity regulating device for at least two hydrostatic variable displacement pumps Download PDFInfo
- Publication number
- EP0561153B1 EP0561153B1 EP93102076A EP93102076A EP0561153B1 EP 0561153 B1 EP0561153 B1 EP 0561153B1 EP 93102076 A EP93102076 A EP 93102076A EP 93102076 A EP93102076 A EP 93102076A EP 0561153 B1 EP0561153 B1 EP 0561153B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- piston
- lever arm
- control
- spring
- 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
Links
Images
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
- F04B49/002—Hydraulic systems to change the pump delivery
-
- 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
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0208—Power
-
- 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
- F04B2205/18—Pressure in a control cylinder/piston unit
Definitions
- the invention relates to a device for regulating the power of at least two hydrostatic variable displacement pumps according to the preamble of claim 1.
- the power control of this known device is a total power control, which distributes the total drive power made available by the drive motor as needed between the two variable pumps. Like any power control, it is based on the principle of adjusting the delivery volume of the variable pumps depending on the first control pressure along a hyperbolic characteristic, so that the maximum drive torque or, at constant drive speed, the maximum power consumption of the variable pumps remains essentially constant over the entire working range.
- the spring arrangements assigned to the power control valves of the known device each consist of a compression spring, the setting value of which determines the counterpressure and thus the maximum power consumption of the respective variable pump.
- the back pressure is selected so that each variable pump is set to 100% total drive power. This power can be transmitted by each variable pump as long as the pressure difference acting on the assigned power control valve is equal to the set back pressure, i.e. there is no second control pressure because the other variable pump does not require any power.
- variable pumps each transfer 50% of the total drive power, their power consumption is limited to this value.
- a corresponding power limitation in the form of throttle and valve devices is provided, which prevents a reduction in the power setting of the other variable pump.
- the power restriction includes the first compression springs, the design effort of which is negligible, since they are used for the power control valves instead of the return springs usual in the prior art.
- the function of the power limitation results from the setting values and the arrangement of the first and second, preferably adjustable compression springs in cooperation with the respective second control pressure.
- the back pressure determining the maximum power consumption (100% of the total drive power) of each variable pump is divided into a first back pressure, ie the setting value of the first compression spring, and a second back pressure, ie the setting value of the second compression spring.
- the pressure difference between the back pressure and the second control pressure is divided into a first pressure difference and a second pressure difference. Since the second control pressure only acts against the second, but not against the first pressure spring, the first pressure difference remains the same as the set value of the first pressure spring.
- the second pressure difference between the second control pressure and the second pressure spring acting on the power control valve of each variable pump changes inversely proportional to the power consumption of the other variable displacement pump and is equal to zero if this variable displacement pump consumes the power corresponding to the setting value of the second compression spring.
- the first control pressure is only opposed by the first pressure difference, ie the counter pressure of the first compression spring, so that the power consumption of the variable pump cannot exceed the value set with this counter pressure, ie is limited to this.
- Both first compression springs thus determine the power settings to which both variable pumps are limited if the difference between the maximum power they take up is a minimum, for example zero when the power is limited to 50% for each variable pump.
- a two-armed swivel lever with a first lever arm and a second lever arm is assigned to each power control valve and lies on the side opposite the first compression spring with the first lever arm, the second lever arm between a first and a second piston, which is in contact with it, the first piston is mounted displaceably in the actuating piston of the actuating device designed as an actuating cylinder perpendicular to its direction of movement and is acted upon by the first control pressure in the direction of the second lever arm, and the second piston by the second compression spring against the second control pressure is applied in the direction of the second lever arm.
- the figure shows two hydrostatic variable displacement pumps 1 and 2, such as, for example, axial piston pumps in a swashplate design, which are connected mechanically via a gear (not shown) to a drive motor (also not shown) with constant drive speed.
- the components or devices assigned to the variable displacement pumps 1, 2 are identified below by the addition .1 or .2 to the reference symbol, if necessary.
- Each variable pump 1, 2 is via a suction line 3 and a drain line 4 connected to a tank 5 and via a working line 6.1 or 6.2 to one or more consumers, not shown.
- the adjusting pumps 1, 2 are each assigned an adjusting device in the form of a hydraulic adjusting cylinder 7.1 or 7.2 for adjusting their delivery volumes.
- An actuating piston 8 is arranged displaceably in each actuating cylinder 7 and is connected via a piston rod 9 to an actuating part 10 coupled to the swash plate of the respective variable displacement pump 1 or 2.
- Each actuating piston 8 delimits a left cylinder chamber 11 in the respective actuating cylinder 7.1 or 7.2 with its (smaller) piston ring surface and a right cylinder chamber 12 with its (larger) piston surface Cylinder chamber 12 and thus in the sense of pivoting the respective variable pump 1 or 2 to a larger delivery volume.
- Each piston rod 9 comprises a piston rod section of smaller diameter and a piston rod section of larger diameter.
- the latter is designated by the reference number 14 and molded onto the respective actuating piston 8. Its end region connected to the piston rod section of smaller diameter protrudes from the respective actuating cylinder 7.1 or 7.2 and is provided with a blind bore running perpendicular to its direction of movement, in which a piston 15.1 or 15.2, hereinafter referred to as the first piston, is slidably mounted.
- Each first piston 15.1, 15.2 can be acted upon by a control pressure corresponding to the working pressure in the working line 6.1 or 6.2 of the respective variable pump 1 or 2, hereinafter referred to as the first control pressure.
- a first control pressure line 16.1, 17.1 or 16.2, 17.2 is provided, each consisting of a first line section 16.1 or 16.2 and a second line section 17.1 or 17.2.
- the first line section 16.1 or 16.2 connects the working line 6.1 or 6.2 to the left cylinder space 11 of the respective actuating cylinder 7.1 or 7.2.
- the respective left cylinder chamber 11.1 or 11.2 is connected to the respective blind bore via the second line section 17.1 or 17.2 running in the respective piston rod section 14.1 or 14.2.
- Each first line section 16.1, 16.2 feeds the working pressure in the respective working line 6.1 or 6.2 to the left cylinder space 11 of the respective actuating cylinder 7.1 or 7.2 as the signal pressure and thus serves as the signal pressure line.
- the right cylinder spaces 12 can also be acted upon with the working pressure as a control pressure via a connection.
- Each variable pump 1, 2 is assigned a power control valve 18.1 or 18.2 in the form of a throttling 3/2-way valve, each with a slide 19 for regulating the actuating pressure applied to the respective actuating cylinder 7.1 or 7.2.
- Each power control valve 18.1, 18.2 is provided with a tank connection and a connection to a third line section 20.1 or 20.2 and a fourth line section 21.1 or 21.2, both of which serve as signal pressure lines.
- Each third line section 20 leads to the left cylinder chamber 11 and every fourth line section 21 to the signal pressure connection of the right cylinder chamber 12 of the respective actuating cylinder 7.1 or 7.2.
- each power control valve 18.1 or 18.2 is acted upon on the left side in the figure by an adjustable first compression spring 22 in the direction of the starting position shown, in which the tank connection is open and the connection to the third line section 20 is closed.
- each output control valve 18.1 or 18.2 opposite the first compression spring 22 Arranged on the side of each output control valve 18.1 or 18.2 opposite the first compression spring 22 is a two-armed pivot lever with a first lever arm 23.1 or 23.2 and a second lever arm 24.1 or 24.2 which can be pivoted about a pivot bearing 32.1 or 32.2.
- the first lever arm 23 bears against the slide 19 of the respective power control valve 18.1 or 18.2.
- the second lever arm 24 is arranged between the first piston 15 and the piston rod 25 of a second piston 26, both of which bear against it. Therefore, the arrangement of the pistons 15, 26 relative to the second lever arm 24 is such that the first control pressure acts against the pressure of the first and second compression springs 22 and 30.
- Each second piston 26.1, 26.2 is slidably mounted in a cylinder 27.1 or 27.2 and delimits a control chamber 28 and with its (smaller) piston ring surface its (larger) piston surface has a spring chamber 29 in which an adjustable second compression spring 30 is arranged.
- the control rooms 28.1, 28.2 of the cylinders 27.1 and 27.2 assigned to the two variable pumps 1, 2 are each connected via a second control pressure line 31.2 and 31.1, so to speak, so to speak, with the working line 6.2 and 6.1 of the other variable pumps 2 and 1, respectively.
- the second piston 26.1 assigned to the power control valve 18.1 of the variable pump 1 can be acted upon with the working pressure in the working line 6.2 of the variable pump 2 as the second control pressure.
- variable pumps 1, 2 in the ratio of 60/40.
- the compression springs 22.1 and 30.2 are at 60% and the compression springs 22.2 and 30.1 at 40% of the total drive power provided by the drive motor, i.e. to a value corresponding to the quotient of 100% total drive power and max. Delivery volume of the respective variable pump.
- the power control valves 18.1, 18.2 are in their starting position, so that both variable pumps 1, 2 are set to the maximum delivery volume.
- variable pumps are driven by the drive motor at the same and constant speed. If the variable displacement pump 2 does not take up any power, for example, and the second control pressure accordingly has the value zero, the second pressure difference at the second piston 26.1 is equal to the set value of the second pressure spring 30.1, so that the power control valve 18.1 and thus the variable displacement pump 1 are set to 100% power is.
- variable pump 1 now takes up this set power and, with a corresponding load from the connected consumer, the hydraulic force of the working pressure in the working line 6.1, and thus the first control pressure, the adjusting force of the working pressure 6.1 via the first piston 15.1 and the pivoting lever 23.1, 24.1 exceeds two compression springs 28.1 and 30.1, the slide 19.1 of the power control valve 18.1 is moved to the left into the control position in which the two cylinder spaces 11.1 and 12.1 of the actuating cylinder 7.1 are connected to one another are connected.
- the working pressure in the working line 6.1 now acts as the actuating pressure on the larger piston surface of the actuating piston 8.1 and moves it to the left while pivoting the variable displacement pump 1 until there is a force equilibrium at the power control valve 18.1.
- the lever length of the second lever arm 24.1 is shortened, so that the working pressure in the working line 6.1 can increase in the same ratio as the delivery volume of the variable pump 1 decreases.
- the product of the working pressure and delivery volume is kept constant in this way, ie the variable pump 1 is regulated along a hyperbolic characteristic.
- the working pressure in the working line 6.1 acts via the second control pressure line 31.1 as a second control pressure on the second piston 26.2 and reduces the pressure difference against the first control pressure compared to the second pressure spring 30.2 to the value zero.
- the power control valve 18.2 and thus the variable pump 2 is now set to 40% of the total drive power in accordance with the setting value of the first compression spring 22.2.
- variable pump 2 now consumes this power of 40%, its delivery volume is reduced in the manner already described above with the variable pump 1 and regulated along a hyperbolic characteristic curve when the hydraulic force of the working pressure in the working line 6.2 with a corresponding load by the connected consumer the setting force of the first compression spring exceeds 22.2.
- the working pressure in the working line 6.2 acts via the second control pressure line 31.2 as the second control pressure on the second piston 26.1 and reduces the pressure difference acting against the first control pressure compared to the second pressure spring 30.1 to the value zero.
- the power control valve 18.1 and thus the variable pump 1 is now set to 60% of the total drive power in accordance with the setting value of the first compression spring 22.1.
- variable pumps 1, 2 transmit these set power values of 60% or 40% of the total drive power, they are limited to these values, since the power setting of each variable pump also exceeds the set value of the assigned second compression spring 30 is not reduced by the second control pressure corresponding to the power consumption of the respective other variable displacement pump; in such a case, the piston rod 25 of the second piston 26 acted upon by the second control pressure lifts off from the second lever arm 24, so that the power setting of the respective variable pump can no longer be influenced by the power consumption of the other variable pump.
- a higher power consumption by one of the two variable pumps is only possible if the power consumption of the other variable pump falls below the set value of the first compression spring 22 assigned to it.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Reciprocating Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
Die Erfindung betrifft eine Vorrichtung zur Leistungsregelung von wenigstens zwei hydrostatischen Verstellpumpen nach dem Oberbegriff des Anspruches 1.The invention relates to a device for regulating the power of at least two hydrostatic variable displacement pumps according to the preamble of claim 1.
Derartige Vorrichtungen sind in der Praxis bekannt und beispielsweise auf Seite 9 des Technischen Merkblattes RD93010/03.87 der Firma Hydromatik GmbH unter der Bezeichnung Cross-Sensing dargestellt. Die Leistungsregelung dieser bekannten Vorrichtung ist eine Summenleistungsregelung, die die vom Antriebsmotor zur Verfügung gestellte Gesamtantriebsleistung bedarfsorientiert zwischen den beiden Verstellpumpen verteilt. Sie beruht wie jede Leistungsregelung auf dem Prinzip der Verstellung des Fördervolumens der Verstellpumpen in Abhängigkeit vom ersten Steuerdruck entlang einer hyperbolisch verlaufenden Kennlinie, so daß das maximale Antriebsmoment bzw. bei konstanter Antriebsdrehzahl die maximale Leistungsaufnahme der Verstellpumpen über den gesamten Arbeitsbereich im wesentlichen konstant bleibt.Such devices are known in practice and are shown, for example, on page 9 of Technical Data Sheet RD93010 / 03.87 by Hydromatik GmbH under the name Cross-Sensing. The power control of this known device is a total power control, which distributes the total drive power made available by the drive motor as needed between the two variable pumps. Like any power control, it is based on the principle of adjusting the delivery volume of the variable pumps depending on the first control pressure along a hyperbolic characteristic, so that the maximum drive torque or, at constant drive speed, the maximum power consumption of the variable pumps remains essentially constant over the entire working range.
Die den Leistungsregelventilen der bekannten Vorrichtung zugeordneten Federanordnungen bestehen aus je einer Druckfeder, deren Einstellwert den Gegendruck und damit die maximale Leistungsaufnahme der jeweiligen Verstellpumpe bestimmt. Der Gegendruck ist so gewählt, daß jede Verstellpumpe auf 100 % Gesamtantriebsleistung eingestellt ist. Diese Leistung kann von jeder Verstellpumpe solange übertragen werden, wie die am zugeordneten Leistungsregelventil wirkende Druckdifferenz gleich dem eingestellten Gegendruck ist, d.h. kein zweiter Steuerdruck ansteht, da die jeweils andere Verstellpumpe keine Leistung beansprucht.The spring arrangements assigned to the power control valves of the known device each consist of a compression spring, the setting value of which determines the counterpressure and thus the maximum power consumption of the respective variable pump. The back pressure is selected so that each variable pump is set to 100% total drive power. This power can be transmitted by each variable pump as long as the pressure difference acting on the assigned power control valve is equal to the set back pressure, i.e. there is no second control pressure because the other variable pump does not require any power.
Mit zunehmender Leistungsaufnahme der letzteren Verstellpumpe verringert sich infolge des entsprechend steigenden zweiten Steuerdrucks die Druckdifferenz am Leistungsregelventil der ersteren Verstellpumpe und damit dessen Leistungseinstellung.As the power consumption of the latter variable pump increases, the pressure difference at the power control valve of the first variable pump and thus its power setting decrease due to the correspondingly increasing second control pressure.
Sobald jedoch beide Verstellpumpen je 50 % der Gesamtantriebsleistung übertragen, wird ihre Leistungsaufnahme auf diesen Wert beschränkt. Zu diesem Zweck ist eine entsprechende Leistungsbeschränkung in Form von Drossel- und Ventileinrichtungen vorgesehen, die eine Reduzierung der Leistungseinstellung der jeweils anderen Verstellpumpe verhindert. Diese Einrichtungen sind konstruktiv vergleichsweise aufwendig und nicht Lieferbestandteil der bekannten Vorrichtung. Sie werden vom Kunden nachträglich bei der Installation der Leistungsregelungsvorrichtung und der Verstellpumpen in Fahrzeuge etc. mit eingebaut.However, as soon as both variable pumps each transfer 50% of the total drive power, their power consumption is limited to this value. To For this purpose, a corresponding power limitation in the form of throttle and valve devices is provided, which prevents a reduction in the power setting of the other variable pump. These devices are structurally comparatively complex and not part of the delivery of the known device. They are subsequently installed by the customer when installing the power control device and variable pumps in vehicles etc.
Es ist Aufgabe der Erfindung, eine Vorrichtung der eingangs genannten Art so weiterzubilden, daß sie die Leistungsbeschränkung in konstruktiv vereinfachter Ausführung bereits ab Werk als integralen Bestandteil enthält.It is an object of the invention to develop a device of the type mentioned at the outset in such a way that it contains the power limitation in a structurally simplified embodiment as an integral part from the factory.
Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruches 1 gelöst.This object is achieved by the characterizing features of claim 1.
In konstruktiver Hinsicht umfaßt die Leistungsbeschränkung die ersten Druckfedern, deren konstruktiver Aufwand vernachlässigbar ist, da sie anstelle der im Stand der Technik üblichen Rückstellfedern für die Leistungsregelventile verwendet werden.From a design point of view, the power restriction includes the first compression springs, the design effort of which is negligible, since they are used for the power control valves instead of the return springs usual in the prior art.
Die Funktion der Leistungsbeschränkung ergibt sich aus den Einstellwerten und der Anordnung der ersten und zweiten, vorzugsweise verstellbar ausgebildeten Druckfedern im Zusammenwirken mit dem jeweiligen zweiten Steuerdruck. Der die maximale Leistungsaufnahme (100 % der Gesamtantriebsleistung) jeder Verstellpumpe bestimmende Gegendruck ist erfindungsgemäß in einen ersten Gegendruck, d.h. den Einstellwert der ersten Druckfeder, und einen zweiten Gegendruck, d.h. den Einstellwert der zweiten Druckfeder, aufgeteilt. Dementsprechend ist auch die Druckdifferenz zwischen dem Gegendruck und dem zweiten Steuerdruck in eine erste Druckdifferenz und eine zweite Druckdifferenz aufgeteilt. Da der zweite Steuerdruck nur gegen die zweite, nicht jedoch gegen die erste Druckfeder wirkt, bleibt die erste Druckdifferenz unverändert gleich dem Einstellwert der ersten Druckfeder. Die am Leistungsregelventil jeder Verstellpumpe wirkende zweite Druckdifferenz zwischen dem zweiten Steuerdruck und der zweiten Druckfeder ändert sich umgekehrt proportional zur Leistungsaufnahme der jeweils anderen Verstellpumpe und ist gleich Null, wenn diese Verstellpumpe die dem Einstellwert der zweiten Druckfeder entsprechende Leistung aufnimmt. In diesem Fall steht dem ersten Steuerdruck lediglich die erste Druckdifferenz, d.h. der Gegendruck der ersten Druckfeder entgegen, so daß die Leistungsaufnahme der Verstellpumpe den mit diesem Gegendruck eingestellten Wert nicht überschreiten kann, d.h. auf diesen beschrankt ist. Beide erste Druckfedern bestimmen somit die Leistungseinstellungen, auf welche beide Verstellpumpen beschränkt werden, wenn der Unterschied zwischen den von ihnen maximal aufgenommenen Leistungen ein Minimum ist, beispielsweise gleich Null bei einer Leistungsbeschränkung auf 50 % für jede Verstellpumpe.The function of the power limitation results from the setting values and the arrangement of the first and second, preferably adjustable compression springs in cooperation with the respective second control pressure. According to the invention, the back pressure determining the maximum power consumption (100% of the total drive power) of each variable pump is divided into a first back pressure, ie the setting value of the first compression spring, and a second back pressure, ie the setting value of the second compression spring. Accordingly, the pressure difference between the back pressure and the second control pressure is divided into a first pressure difference and a second pressure difference. Since the second control pressure only acts against the second, but not against the first pressure spring, the first pressure difference remains the same as the set value of the first pressure spring. The second pressure difference between the second control pressure and the second pressure spring acting on the power control valve of each variable pump changes inversely proportional to the power consumption of the other variable displacement pump and is equal to zero if this variable displacement pump consumes the power corresponding to the setting value of the second compression spring. In this case, the first control pressure is only opposed by the first pressure difference, ie the counter pressure of the first compression spring, so that the power consumption of the variable pump cannot exceed the value set with this counter pressure, ie is limited to this. Both first compression springs thus determine the power settings to which both variable pumps are limited if the difference between the maximum power they take up is a minimum, for example zero when the power is limited to 50% for each variable pump.
Gemäß einer Weiterbildung der Erfindung und zur Erzielung der hyperbolischen Regelkurve ist je ein zweiarmiger Schwenkhebel mit einem ersten Hebelarm und einem zweiten Hebelarm jedem Leistungsregelventil zugeordnet und liegt an dessen der ersten Druckfeder gegenüberliegenden Seite mit dem ersten Hebelarm an, wobei der zweite Hebelarm zwischen einem ersten und einem zweiten, ihm jeweils anliegenden Kolben angeordnet ist, der erste Kolben im Stellkolben der als Stellzylinder ausgebildeten Stelleinrichtung senkrecht zu dessen Bewegungsrichtung verschiebbar gelagert und vom ersten Steuerdruck in Richtung des zweiten Hebelarmes beaufschlagt ist, und der zweite Kolben von der zweiten Druckfeder entgegen dem zweiten Steuerdruck in Richtung des zweiten Hebelarmes beaufschlagt ist.According to a development of the invention and to achieve the hyperbolic control curve, a two-armed swivel lever with a first lever arm and a second lever arm is assigned to each power control valve and lies on the side opposite the first compression spring with the first lever arm, the second lever arm between a first and a second piston, which is in contact with it, the first piston is mounted displaceably in the actuating piston of the actuating device designed as an actuating cylinder perpendicular to its direction of movement and is acted upon by the first control pressure in the direction of the second lever arm, and the second piston by the second compression spring against the second control pressure is applied in the direction of the second lever arm.
Nachstehend ist die Erfindung anhand eines bevorzugten Ausführungsbeispiels unter Bezugnahme auf den Schaltplan gemäß der einzigen Figur näher beschrieben.The invention is described in more detail below on the basis of a preferred exemplary embodiment with reference to the circuit diagram in accordance with the single figure.
Die Figur zeigt zwei hydrostatische Verstellpumpen 1 und 2, wie z.B. Axialkolbenpumpen in Schrägscheibenbauweise, die über ein nicht gezeigtes Getriebe mit einem ebenfalls nicht gezeigten Antriebsmotor konstanter Antriebsdrehzahl in mechanischer Antriebsverbindung stehen. Nachstehend sind die den Verstellpumpen 1, 2 zugeordneten Bauteile bzw. Einrichtungen bei Bedarf durch den Zusatz .1 bzw. .2 zum Bezugszeichen gekennzeichnet. Jede Verstellpumpe 1, 2 ist über je eine Saugleitung 3 und je eine Leckölleitung 4 an einen Tank 5 sowie über je eine Arbeitsleitung 6.1 bzw. 6.2 an einen oder mehrere nicht gezeigte Verbraucher angeschlossen.The figure shows two hydrostatic variable displacement pumps 1 and 2, such as, for example, axial piston pumps in a swashplate design, which are connected mechanically via a gear (not shown) to a drive motor (also not shown) with constant drive speed. The components or devices assigned to the variable displacement pumps 1, 2 are identified below by the addition .1 or .2 to the reference symbol, if necessary. Each variable pump 1, 2 is via a suction line 3 and a drain line 4 connected to a
Den Verstellpumpen 1, 2 ist je eine Stelleinrichtung in Form eines hydraulischen Stellzylinders 7.1 bzw. 7.2 zur Verstellung ihrer Fördervolumina zugeordnet. In jedem Stellzylinder 7 ist ein Stellkolben 8 verschiebbar angeordnet und über eine Kolbenstange 9 mit einem mit der Schrägscheibe der jeweiligen Verstellpumpe 1 bzw. 2 gekoppelten Stellteil 10 verbunden. Jeder Stellkolben 8 begrenzt im jeweiligen Stellzylinder 7.1 bzw. 7.2 mit seiner (kleineren) Kolbenringfläche einen linken Zylinderraum 11 und mit seiner (größeren) Kolbenfläche einen rechten Zylinderraum 12. Eine Vorspannfeder 13 im linken Zylinderraum 11 beaufschlagt den Stellkolben 8 im Sinne einer Verkleinerung des rechten Zylinderraums 12 und damit im Sinne eines Ausschwenkens der jeweiligen Verstellpumpe 1 bzw. 2 auf größeres Fördervolumen.The adjusting pumps 1, 2 are each assigned an adjusting device in the form of a hydraulic adjusting cylinder 7.1 or 7.2 for adjusting their delivery volumes. An actuating piston 8 is arranged displaceably in each actuating cylinder 7 and is connected via a piston rod 9 to an actuating
Jede Kolbenstange 9 umfaßt einen Kolbenstangenabschnitt kleineren und einen Kolbenstangenabschnitt größeren Durchmessers. Letzterer ist mit dem Bezugszeichen 14 bezeichnet und an den jeweiligen Stellkolben 8 angeformt. Sein mit dem Kolbenstangenabschnitt kleineren Durchmessers verbundener Endbereich ragt aus dem jeweiligen Stellzylinder 7.1 bzw. 7.2 heraus und ist mit einer senkrecht zu seiner Bewegungsrichtung verlaufenden Sackbohrung versehen, in der ein Kolben 15.1 bzw. 15.2, nachstehend als erster Kolben bezeichnet, verschiebbar gelagert ist.Each piston rod 9 comprises a piston rod section of smaller diameter and a piston rod section of larger diameter. The latter is designated by the reference number 14 and molded onto the respective actuating piston 8. Its end region connected to the piston rod section of smaller diameter protrudes from the respective actuating cylinder 7.1 or 7.2 and is provided with a blind bore running perpendicular to its direction of movement, in which a piston 15.1 or 15.2, hereinafter referred to as the first piston, is slidably mounted.
Jeder erste Kolben 15.1, 15.2 ist von einem dem Arbeitsdruck in der Arbeitsleitung 6.1 bzw. 6.2 der jeweiligen Verstellpumpe 1 bzw. 2 entsprechenden Steuerdruck, nachstehend als erster Steuerdruck bezeichnet, beaufschlagbar. Zu diesem Zweck ist je eine erste Steuerdruckleitung 16.1, 17.1 bzw. 16.2, 17.2 bestehend aus je einem ersten Leitungsabschnitt 16.1 bzw. 16.2 und je einem zweiten Leitungsabschnitt 17.1 bzw. 17.2 vorgesehen. Der erste Leitungsabschnitt 16.1 bzw. 16.2 verbindet die Arbeitsleitung 6.1 bzw. 6.2 mit dem linken Zylinderraum 11 des jeweiligen Stellzylinders 7.1 bzw. 7.2. Über den zweiten, im jeweiligen Kolbenstangenabschnitt 14.1 bzw. 14.2 verlaufenden Leitungsabschnitt 17.1 bzw. 17.2 ist der jeweilige linke Zylinderraum 11.1 bzw. 11.2 an die jeweilige Sackbohrung angeschlossen.Each first piston 15.1, 15.2 can be acted upon by a control pressure corresponding to the working pressure in the working line 6.1 or 6.2 of the respective variable pump 1 or 2, hereinafter referred to as the first control pressure. For this purpose, a first control pressure line 16.1, 17.1 or 16.2, 17.2 is provided, each consisting of a first line section 16.1 or 16.2 and a second line section 17.1 or 17.2. The first line section 16.1 or 16.2 connects the working line 6.1 or 6.2 to the left cylinder space 11 of the respective actuating cylinder 7.1 or 7.2. The respective left cylinder chamber 11.1 or 11.2 is connected to the respective blind bore via the second line section 17.1 or 17.2 running in the respective piston rod section 14.1 or 14.2.
Jeder erste Leitungsabschnitt 16.1, 16.2 führt den Arbeitsdruck in der jeweiligen Arbeitsleitung 6.1 bzw. 6.2 als Stelldruck dem linken Zylinderraum 11 des jeweiligen Stellzylinders 7.1 bzw. 7.2 zu und dient somit als Stelldruckleitung. Die rechten Zylinderräume 12 sind über je einen Anschluß ebenfalls mit dem Arbeitsdruck als Stelldruck beaufschlagbar.Each first line section 16.1, 16.2 feeds the working pressure in the respective working line 6.1 or 6.2 to the left cylinder space 11 of the respective actuating cylinder 7.1 or 7.2 as the signal pressure and thus serves as the signal pressure line. The right cylinder spaces 12 can also be acted upon with the working pressure as a control pressure via a connection.
Jeder Verstellpumpe 1, 2 ist je ein Leistungsregelventil 18.1 bzw. 18.2 in Form eines drosselnden 3/2-Wegeventils mit je einem Schieber 19 zur Regelung der Stelldruckbeaufschlagung des jeweiligen Stellzylinders 7.1 bzw. 7.2 zugeordnet. Jedes Leistungsregelventil 18.1, 18.2 ist mit einem Tankanschluß sowie je einem Anschluß an einen dritten Leitungsabschnitt 20.1 bzw. 20.2 und einen vierten Leitungsabschnitt 21.1 bzw. 21.2, die beide als Stelldruckleitungen dienen, versehen. Jeder dritte Leitungsabschnitt 20 führt zum linken Zylinderraum 11 und jeder vierte Leitungsabschnitt 21 zum Stelldruckanschluß des rechten Zylinderraums 12 des jeweiligen Stellzylinders 7.1 bzw. 7.2.Each variable pump 1, 2 is assigned a power control valve 18.1 or 18.2 in the form of a throttling 3/2-way valve, each with a slide 19 for regulating the actuating pressure applied to the respective actuating cylinder 7.1 or 7.2. Each power control valve 18.1, 18.2 is provided with a tank connection and a connection to a third line section 20.1 or 20.2 and a fourth line section 21.1 or 21.2, both of which serve as signal pressure lines. Each third line section 20 leads to the left cylinder chamber 11 and every fourth line section 21 to the signal pressure connection of the right cylinder chamber 12 of the respective actuating cylinder 7.1 or 7.2.
Der Schieber 19 jedes Leistungsregelventils 18.1 bzw. 18.2 ist auf der in der Figur linken Seite von einer einstellbaren ersten Druckfeder 22 in Richtung der gezeigten Ausgangsstellung beaufschlagt, in der der Tankanschluß geöffnet und der Anschluß an den dritten Leitungsabschnitt 20 geschlossen ist.The slide 19 of each power control valve 18.1 or 18.2 is acted upon on the left side in the figure by an adjustable first compression spring 22 in the direction of the starting position shown, in which the tank connection is open and the connection to the third line section 20 is closed.
Auf der der ersten Druckfeder 22 gegenüberliegenden Seite jedes Leistungsregelventils 18.1 bzw. 18.2 ist je ein zweiarmiger, um je ein Schwenklager 32.1 bzw. 32.2 schwenkbarer Schwenkhebel mit einem ersten Hebelarm 23.1 bzw. 23.2 und einem zweiten Hebelarm 24.1 bzw. 24.2 angeordnet. Der erste Hebelarm 23 liegt dem Schieber 19 des jeweiligen Leistungsregelventils 18.1 bzw. 18.2 an. Der zweite Hebelarm 24 ist zwischen dem ersten Kolben 15 und der Kolbenstange 25 eines zweiten Kolbens 26, die ihm beide anliegen, angeordnet. Daher ist die Anordnung der Kolben 15, 26 gegenüber dem zweiten Hebelarm 24 so getroffen, daß der erste Steuerdruck gegen den Druck der ersten und der zweiten Druckfeder 22 bzw. 30 wirkt. Jeder zweite Kolben 26.1, 26.2 ist in je einem Zylinder 27.1 bzw. 27.2 verschiebbar gelagert und begrenzt mit seiner (kleineren) Kolbenringfläche einen Steuerraum 28 und mit seiner (größeren) Kolbenfläche einen Federraum 29, in dem eine einstellbare zweite Druckfeder 30 angeordnet ist. Die Steuerräume 28.1, 28.2 der den beiden Verstellpumpen 1, 2 zugeordneten Zylinder 27.1 bzw. 27.2 sind über je eine zweite Steuerdruckleitung 31.2 bzw. 31.1 sozusagen über Kreuz mit der Arbeitsleitung 6.2 bzw. 6.1 der jeweils anderen Verstellpumpe 2 bzw. 1 verbunden. Auf diese Weise ist der dem Leistungsregelventil 18.1 der Verstellpumpe 1 zugeordnete zweite Kolben 26.1 mit dem Arbeitsdruck in der Arbeitsleitung 6.2 der Verstellpumpe 2 als zweiten Steuerdruck beaufschlagbar. Gleiches gilt sinngemäß für den zweiten Kolben 26.2.Arranged on the side of each output control valve 18.1 or 18.2 opposite the first compression spring 22 is a two-armed pivot lever with a first lever arm 23.1 or 23.2 and a second lever arm 24.1 or 24.2 which can be pivoted about a pivot bearing 32.1 or 32.2. The first lever arm 23 bears against the slide 19 of the respective power control valve 18.1 or 18.2. The second lever arm 24 is arranged between the first piston 15 and the piston rod 25 of a second piston 26, both of which bear against it. Therefore, the arrangement of the pistons 15, 26 relative to the second lever arm 24 is such that the first control pressure acts against the pressure of the first and second compression springs 22 and 30. Each second piston 26.1, 26.2 is slidably mounted in a cylinder 27.1 or 27.2 and delimits a control chamber 28 and with its (smaller) piston ring surface its (larger) piston surface has a spring chamber 29 in which an adjustable second compression spring 30 is arranged. The control rooms 28.1, 28.2 of the cylinders 27.1 and 27.2 assigned to the two variable pumps 1, 2 are each connected via a second control pressure line 31.2 and 31.1, so to speak, so to speak, with the working line 6.2 and 6.1 of the other variable pumps 2 and 1, respectively. In this way, the second piston 26.1 assigned to the power control valve 18.1 of the variable pump 1 can be acted upon with the working pressure in the working line 6.2 of the variable pump 2 as the second control pressure. The same applies analogously to the second piston 26.2.
Nachstehend ist die Funktion der erfindungsgemäßen Vorrichtung anhand einer Leistungsbeschränkung der Verstellpumpen 1, 2 im Verhältnis von 60/40 beschrieben. Dementsprechend sind die Druckfedern 22.1 sowie 30.2 auf 60 % und die Druckfedern 22.2 sowie 30.1 auf 40 % der vom Antriebsmotor zur Verfügung gestellten Gesamtantriebsleistung, d.h. auf einen Wert entsprechend dem Quotienten aus 100 % Gesamtantriebsleistung und max. Fördervolumen der jeweiligen Verstellpumpe, eingestellt. Die Leistungsregelventile 18.1, 18.2 befinden sich in ihrer Ausgangsstellung, so daß beide Verstellpumpen 1,2 auf maximales Fördervolumen eingestellt sind.The function of the device according to the invention is described below on the basis of a power limitation of the variable pumps 1, 2 in the ratio of 60/40. Accordingly, the compression springs 22.1 and 30.2 are at 60% and the compression springs 22.2 and 30.1 at 40% of the total drive power provided by the drive motor, i.e. to a value corresponding to the quotient of 100% total drive power and max. Delivery volume of the respective variable pump. The power control valves 18.1, 18.2 are in their starting position, so that both variable pumps 1, 2 are set to the maximum delivery volume.
Beide Verstellpumpen werden durch den Antriebsmotor mit gleicher und konstanter Drehzahl angetrieben. Wenn dabei die Verstellpumpe 2 beispielsweise keine Leistung aufnimmt und dementsprechend der zweite Steuerdruck den Wert Null hat, ist die zweite Druckdifferenz am zweiten Kolben 26.1 gleich dem Einstellwert der zweiten Druckfeder 30.1, so daß das Leistungsregelventil 18.1 und damit die Verstellpumpe 1 auf 100 % Leistung eingestellt ist.Both variable pumps are driven by the drive motor at the same and constant speed. If the variable displacement pump 2 does not take up any power, for example, and the second control pressure accordingly has the value zero, the second pressure difference at the second piston 26.1 is equal to the set value of the second pressure spring 30.1, so that the power control valve 18.1 and thus the variable displacement pump 1 are set to 100% power is.
Wenn nun die Verstellpumpe 1 diese eingestellte Leistung aufnimmt und bei entsprechender Belastung durch den angeschlossenen Verbraucher die über den ersten Kolben 15.1 und den Schwenkhebel 23.1, 24.1 auf das Leistungsregelventil 18.1 wirkende hydraulische Kraft des Arbeitsdrucks in der Arbeitsleitung 6.1 und damit des ersten Steuerdrucks die Einstellkraft der beiden Druckfedern 28.1 und 30.1 übersteigt, wird der Schieber 19.1 des Leistungsregelventils 18.1 nach links in die Regelstellung verschoben, in der die beiden Zylinderräume 11.1 und 12.1 des Stellzylinders 7.1 miteinander verbunden sind. Der Arbeitsdruck in der Arbeitsleitung 6.1 beaufschlagt nun als Stelldruck die größere Kolbenfläche des Stellkolbens 8.1 und verschiebt diesen unter Zurückschwenken der Verstellpumpe 1 so lange nach links, bis Kraftgleichgewicht am Leistungsregelventil 18.1 herrscht. Dabei verkürzt sich die Hebellänge des zweiten Hebelarmes 24.1, so daß der Arbeitsdruck in der Arbeitsleitung 6.1 im gleichen Verhältnis ansteigen kann, wie sich das Fördervolumen der Verstellpumpe 1 verringert. Das Produkt aus Arbeitsdruck und Fördervolumen wird auf diese Weise konstant gehalten, d.h. die Verstellpumpe 1 entlang einer hyperbolischen Kennlinie geregelt.If the variable pump 1 now takes up this set power and, with a corresponding load from the connected consumer, the hydraulic force of the working pressure in the working line 6.1, and thus the first control pressure, the adjusting force of the working pressure 6.1 via the first piston 15.1 and the pivoting lever 23.1, 24.1 exceeds two compression springs 28.1 and 30.1, the slide 19.1 of the power control valve 18.1 is moved to the left into the control position in which the two cylinder spaces 11.1 and 12.1 of the actuating cylinder 7.1 are connected to one another are connected. The working pressure in the working line 6.1 now acts as the actuating pressure on the larger piston surface of the actuating piston 8.1 and moves it to the left while pivoting the variable displacement pump 1 until there is a force equilibrium at the power control valve 18.1. The lever length of the second lever arm 24.1 is shortened, so that the working pressure in the working line 6.1 can increase in the same ratio as the delivery volume of the variable pump 1 decreases. The product of the working pressure and delivery volume is kept constant in this way, ie the variable pump 1 is regulated along a hyperbolic characteristic.
Bei maximaler Leistungsaufnahme der Verstellpumpe 1 wirkt der Arbeitsdruck in der Arbeitsleitung 6.1 über die zweite Steuerdruckleitung 31.1 als zweiter Steuerdruck auf den zweiten Kolben 26.2 und reduziert die gegen den ersten Steuerdruck wirkende Druckdifferenz gegenüber der zweiten Druckfeder 30.2 auf den Wert Null. Das Leistungsregelventil 18.2 und damit die Verstellpumpe 2 ist nun entsprechend dem Einstellwert der ersten Druckfeder 22.2 auf 40 % der Gesamtantriebsleistung eingestellt.At maximum power consumption of the variable displacement pump 1, the working pressure in the working line 6.1 acts via the second control pressure line 31.1 as a second control pressure on the second piston 26.2 and reduces the pressure difference against the first control pressure compared to the second pressure spring 30.2 to the value zero. The power control valve 18.2 and thus the variable pump 2 is now set to 40% of the total drive power in accordance with the setting value of the first compression spring 22.2.
Wenn nun die Verstellpumpe 2 diese Leistung von 40 % aufnimmt, wird ihr Fördervolumen in der vorstehend anhand der Verstellpumpe 1 bereits beschriebenen Weise verringert und entlang einer hyperbolischen Kennlinie geregelt, wenn die hydraulische Kraft des Arbeitsdrucks in der Arbeitsleitung 6.2 bei entsprechender Belastung durch den angeschlossenen Verbraucher die Einstellkraft der ersten Druckfeder 22.2 übersteigt. Gleichzeitig wirkt der Arbeitsdruck in der Arbeitsleitung 6.2 über die zweite Steuerdruckleitung 31.2 als zweiter Steuerdruck auf den zweiten Kolben 26.1 und reduziert die gegen den ersten Steuerdruck wirkende Druckdifferenz gegenüber der zweiten Druckfeder 30.1 auf den Wert Null. Das Leistungsregelventil 18.1 und damit die Verstellpumpe 1 ist nun entsprechend dem Einstellwert der ersten Druckfeder 22.1 auf 60 % der Gesamtantriebsleistung eingestellt.If the variable pump 2 now consumes this power of 40%, its delivery volume is reduced in the manner already described above with the variable pump 1 and regulated along a hyperbolic characteristic curve when the hydraulic force of the working pressure in the working line 6.2 with a corresponding load by the connected consumer the setting force of the first compression spring exceeds 22.2. At the same time, the working pressure in the working line 6.2 acts via the second control pressure line 31.2 as the second control pressure on the second piston 26.1 and reduces the pressure difference acting against the first control pressure compared to the second pressure spring 30.1 to the value zero. The power control valve 18.1 and thus the variable pump 1 is now set to 60% of the total drive power in accordance with the setting value of the first compression spring 22.1.
Wenn beide Verstellpumpen 1, 2 diese eingestellten Leistungswerte von 60 % bzw. 40 % der Gesamtantriebsleistung übertragen, sind sie auf diese Werte beschränkt, da die Leistungseinstellung jeder Verstellpumpe auch bei Überschreiten des Einstellwertes der zugeordneten zweiten Druckfeder 30 durch den der Leistungsaufnahme der jeweils anderen Verstellpumpe entsprechenden zweiten Steuerdruck nicht reduziert wird; in einem solchen Fall hebt die Kolbenstange 25 des vom zweiten Steuerdruck beaufschlagten zweiten Kolbens 26 nämlich vom zweiten Hebelarm 24 ab, so daß die Leistungseinstellung der jeweiligen Verstellpumpe durch die Leistungsaufnahme der jeweils anderen Verstellpumpe nicht mehr beeinflußt werden kann.If both variable pumps 1, 2 transmit these set power values of 60% or 40% of the total drive power, they are limited to these values, since the power setting of each variable pump also exceeds the set value of the assigned second compression spring 30 is not reduced by the second control pressure corresponding to the power consumption of the respective other variable displacement pump; in such a case, the piston rod 25 of the second piston 26 acted upon by the second control pressure lifts off from the second lever arm 24, so that the power setting of the respective variable pump can no longer be influenced by the power consumption of the other variable pump.
Eine höhere Leistungsaufnahme durch eine der beiden Verstellpumpen ist nur dann möglich, wenn die Leistungsaufnahme der jeweils anderen Verstellpumpe unter den Einstellwert der ihr zugeordneten ersten Druckfeder 22 fällt.A higher power consumption by one of the two variable pumps is only possible if the power consumption of the other variable pump falls below the set value of the first compression spring 22 assigned to it.
Claims (3)
- Device for the power control of at least two hydrostatic variable displacement pumps, driven by a common drive motor and delivering into respective operating lines, through the adjustment of their displacement in dependence upon the operating pressure in both operating lines by means in each case of an adjusting device which can be acted upon with an adjusting pressure and is biassed in the direction of maximum displacement,
having in each case a power control valve associated with each adjusting device, which valve is acted upon by a first control pressure, corresponding with the operating pressure in the operating line of the variable displacement pump to be adjusted by the adjusting device, against a pressure difference in the direction of a control position, in which the power control valve controls the adjusting pressure acting upon the adjusting device in the direction tending to reduce the displacement of the variable displacement pump along a hyperbolic control curve,
whereby the pressure difference results from a backpressure of a spring arrangement counteracting the first control pressure and from a second control pressure corresponding with the operating pressure in the operating line of the respective other variable displacement pump, and with increasing second control pressure drops from a specified maximum value to a specified minimum value,
characterized in that,
the spring arrangement is divided into a first and a second pressure spring (22, 30), in that the first pressure spring (22) is set to a force corresponding with the minimum value (Δpmin) of the pressure difference and the second pressure spring (30) is set to a force corresponding with the difference (Δpmax-Δpmin) between the maximum value (Δpmax) and the minimum value (Δpmin) of the pressure difference, and in that the first pressure spring (22) with its set force and the second pressure spring (30) with a force decreasing with increasing second control pressure act upon the power control valve (18.1 and 18.2). - Device according to claim 1,
characterized in that,
the first and the second pressure spring (22, 30) are adjustable. - Device according to claim 1 or 2,
characterized in that,
in each case a two-armed pivoted lever (23.1, 24.1 and 23.2, 24.2) with a first lever arm (23.1 and 23.2) and a second lever arm (24.1 and 24.2) is associated with each power control valve (18.1, 18.2) and abuts the side of the power control valve lying opposite the first pressure spring (22) with the first lever arm (23.1 and 23.2), and in that the second lever arm (24.1 and 24.2) is arranged between a first and a second piston each abutting the second lever arm, whereby the first piston (15.1 and 15.2) is mounted in the adjusting piston (8) of the adjusting device constructed as adjustment cylinder (7.1 and 7.2) so as to be displaceable perpendicular to the direction of movement of the adjusting piston and is acted upon by the first control pressure in the direction of the second lever arm (24.1 and 24.2), and whereby the second piston (26.1 and 26.2) is acted upon by the second pressure spring (30.1 and 30.2) against the second control pressure in the direction of the second lever arm (24.1 and 24.2).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4208925 | 1992-03-19 | ||
| DE4208925A DE4208925C1 (en) | 1992-03-19 | 1992-03-19 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0561153A1 EP0561153A1 (en) | 1993-09-22 |
| EP0561153B1 true EP0561153B1 (en) | 1995-11-02 |
Family
ID=6454520
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP93102076A Expired - Lifetime EP0561153B1 (en) | 1992-03-19 | 1993-02-10 | Capacity regulating device for at least two hydrostatic variable displacement pumps |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US5333997A (en) |
| EP (1) | EP0561153B1 (en) |
| JP (1) | JP3526885B2 (en) |
| DE (2) | DE4208925C1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10358727B3 (en) * | 2003-12-15 | 2005-08-25 | Brueninghaus Hydromatik Gmbh | Total power controller |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4405234C1 (en) * | 1994-02-18 | 1995-04-06 | Brueninghaus Hydraulik Gmbh | Arrangement for the cumulative power regulation of at least two hydrostatic variable-displacement pumps |
| US5584640A (en) * | 1994-04-20 | 1996-12-17 | Eaton Corporation | Grain tank unloading auger drive means |
| DE19626793C1 (en) * | 1996-07-03 | 1997-06-26 | Brueninghaus Hydromatik Gmbh | Hydraulic equipment for parallel regulation of hydrostatic displacement pumps |
| US6109030A (en) * | 1998-02-13 | 2000-08-29 | Sauer Inc. | Apparatus and method for ganging multiple open circuit pumps |
| 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 |
| US11725647B2 (en) * | 2021-05-18 | 2023-08-15 | Hamilton Sundstrand Corporation | On-demand dual variable displacement positive displacement pumping system |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1922269A1 (en) * | 1969-04-29 | 1970-11-12 | Bellows Valvair Kaemper Gmbh | Total power controller |
| GB1526085A (en) * | 1975-11-04 | 1978-09-27 | Plessey Co Ltd | Hydraulic pumping arrangements |
| DE3044143A1 (en) * | 1980-11-24 | 1982-06-24 | Linde Ag, 6200 Wiesbaden | CONTROL DEVICE FOR A HYDROSTATIC DRIVE SYSTEM |
| DE3130661A1 (en) * | 1981-08-03 | 1983-02-17 | Linde Ag, 6200 Wiesbaden | HYDROSTATIC DRIVE SYSTEM WITH A PRINT NETWORK |
| DE3130660A1 (en) * | 1981-08-03 | 1983-03-03 | Linde Ag, 6200 Wiesbaden | CONTROL AND REGULATION DEVICE FOR AN ADJUSTABLE HYDROSTATIC UNIT |
| DE3323278C2 (en) * | 1983-06-28 | 1986-05-22 | Hydromatik GmbH, 7915 Elchingen | Control device for several drive units consisting of hydrostatic gears |
| DE3345264A1 (en) * | 1983-12-14 | 1985-06-27 | Brueninghaus Hydraulik Gmbh, 7240 Horb | TORQUE CONTROL UNIT FOR AN ADJUSTABLE HYDROPUMP |
| DE3513452A1 (en) * | 1985-04-15 | 1986-10-16 | Mannesmann Rexroth GmbH, 8770 Lohr | HYDRAULIC SYSTEM FOR SUPPLYING A HYDROSTATIC STEERING |
| DE3638889A1 (en) * | 1986-11-14 | 1988-05-26 | Hydromatik Gmbh | TOTAL PERFORMANCE CONTROL DEVICE FOR AT LEAST TWO HYDROSTATIC GEARBOXES |
| US4813235A (en) * | 1987-06-09 | 1989-03-21 | Deere & Company | Hydraulic gain reduction circuit |
| DE3728207A1 (en) * | 1987-08-24 | 1989-03-09 | Rexroth Mannesmann Gmbh | Valve arrangement for two load-regulated pumps driven by a common drive |
| EP0329860A1 (en) * | 1988-02-25 | 1989-08-30 | RIVA CALZONI S.p.A. | Apparatus for the feed and the speed and torque control of a hydraulic motor with variable displacement at constant pressure |
| DE3919175A1 (en) * | 1989-06-12 | 1990-12-13 | Hydromatik Gmbh | CONTROL DEVICE FOR AN ADJUSTABLE PUMP |
| DE4025638C1 (en) * | 1990-08-13 | 1991-12-05 | Brueninghaus Hydraulik Gmbh, 7240 Horb, De |
-
1992
- 1992-03-19 DE DE4208925A patent/DE4208925C1/de not_active Expired - Fee Related
-
1993
- 1993-02-10 DE DE59300837T patent/DE59300837D1/en not_active Expired - Fee Related
- 1993-02-10 EP EP93102076A patent/EP0561153B1/en not_active Expired - Lifetime
- 1993-03-02 US US08/025,625 patent/US5333997A/en not_active Expired - Lifetime
- 1993-03-18 JP JP05884493A patent/JP3526885B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10358727B3 (en) * | 2003-12-15 | 2005-08-25 | Brueninghaus Hydromatik Gmbh | Total power controller |
Also Published As
| Publication number | Publication date |
|---|---|
| DE59300837D1 (en) | 1995-12-07 |
| JP3526885B2 (en) | 2004-05-17 |
| EP0561153A1 (en) | 1993-09-22 |
| JPH0617761A (en) | 1994-01-25 |
| US5333997A (en) | 1994-08-02 |
| DE4208925C1 (en) | 1993-06-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| DE102008038435A1 (en) | Hydraulic system with an adjustable hydrostatic machine | |
| EP2307726B1 (en) | Adjustable pump | |
| EP1588077B1 (en) | Control of a hydrostatic gearbox | |
| DE3345264A1 (en) | TORQUE CONTROL UNIT FOR AN ADJUSTABLE HYDROPUMP | |
| DE3321484A1 (en) | HYDRAULIC SYSTEM WITH TWO HYDRAULIC ENERGY CONSUMERS | |
| EP0561153B1 (en) | Capacity regulating device for at least two hydrostatic variable displacement pumps | |
| EP0736708B1 (en) | Device for adjustment of the delivery rate of a hydraulic pump | |
| EP2655895B1 (en) | Hydraulic drive | |
| DE19626793C1 (en) | Hydraulic equipment for parallel regulation of hydrostatic displacement pumps | |
| EP0471166B1 (en) | Control apparatus for regulating the delivery flow rate setting of several hydrostatic adjustable pumps | |
| DE3422164C2 (en) | Hydraulic system with at least two consumers of hydraulic energy | |
| DE3919175C2 (en) | ||
| DE69923688T2 (en) | Continuously variable transmission with electro-hydraulic control system and control method for such a transmission | |
| DE3607138C2 (en) | Hydraulic system with a control device | |
| DE3041856C2 (en) | Control device for a hydrostatic transmission | |
| EP0746690B1 (en) | Hydraulic pump control system | |
| DE19735110B4 (en) | Control device with diaphragm seal | |
| DE4026849C2 (en) | Valve arrangement for generating a control pressure in a hydraulic system | |
| DE19756600C1 (en) | Capacity control valve | |
| DE2349124A1 (en) | Hydraulic pressure control of positive displacement pumps - for pumps used in hydraulic circuits with pressure accumulators | |
| DE19808127C2 (en) | Power control device | |
| DE19840894B4 (en) | Hydraulic actuating device | |
| DE4342487B4 (en) | Hydrostatic drive system with after-suction valve | |
| EP1304482B1 (en) | Total power controller | |
| EP0211096A1 (en) | Capacity control or torque limitation |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB IT SE |
|
| 17P | Request for examination filed |
Effective date: 19940119 |
|
| 17Q | First examination report despatched |
Effective date: 19950223 |
|
| RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: BRUENINGHAUS HYDROMATIK GMBH |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT SE |
|
| ITF | It: translation for a ep patent filed |
Owner name: JACOBACCI & PERANI S.P.A. |
|
| REF | Corresponds to: |
Ref document number: 59300837 Country of ref document: DE Date of ref document: 19951207 |
|
| ET | Fr: translation filed | ||
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 19960208 |
|
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed | ||
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20080214 Year of fee payment: 16 Ref country code: IT Payment date: 20080220 Year of fee payment: 16 Ref country code: GB Payment date: 20080220 Year of fee payment: 16 Ref country code: DE Payment date: 20080219 Year of fee payment: 16 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20080214 Year of fee payment: 16 |
|
| EUG | Se: european patent has lapsed | ||
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20090210 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20091030 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090901 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090210 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090302 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090210 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090211 |