EP2138720A2 - Adjustment device for the adjustment of axial piston engines. - Google Patents
Adjustment device for the adjustment of axial piston engines. Download PDFInfo
- Publication number
- EP2138720A2 EP2138720A2 EP09007975A EP09007975A EP2138720A2 EP 2138720 A2 EP2138720 A2 EP 2138720A2 EP 09007975 A EP09007975 A EP 09007975A EP 09007975 A EP09007975 A EP 09007975A EP 2138720 A2 EP2138720 A2 EP 2138720A2
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- EP
- European Patent Office
- Prior art keywords
- control
- adjusting
- adjusting device
- actuating
- piston
- 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.)
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Classifications
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- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
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- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2042—Valves
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- 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
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- 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
- F04B49/10—Other safety measures
Definitions
- the present invention generally relates to the hydraulic adjustment of mechanical systems, wherein the adjustment range of the respective system extends in opposite directions to either side of a zero crossing.
- the adjustment range can be a swivel range but also a linear range.
- the invention relates to an adjusting device according to the preamble of claim 1.
- the pumping or driving action depends on the pivoting angle of the respective pivotable element. At zero swing angle, the pumping or driving action of the machine is zero, while it increases with swinging out of zero position with increasing swing angle.
- hydraulically actuated actuators are often used, e.g. be controlled by solenoid operated multi-way valves.
- an adjustable axial piston machine in swash plate construction in which the swash plate surface is formed on a pivotable about a pivot axis, substantially semi-cylindrical cradle body, with its semi-cylindrical outer surface in a corresponding hollow cylindrical Support surface is mounted in the machine housing of the axial piston machine, and provided for pivoting the cradle body actuating means which are in operative connection with a lever which is connected to the cradle body and whose longitudinal central axis intersects the pivot axis.
- the adjusting devices are designed as double-acting actuating cylinder adjusting piston units, each with two arranged in the opposite effective direction control piston surfaces.
- the actuating cylinder actuating piston unit comprises a transverse split actuating piston consisting of two adjusting piston parts.
- the two Stellkolbenmaschine be braced by spring assemblies against each other, have the same dimensions and produce the same size, oppositely directed spring forces.
- neutral position Nullhub too of the machine
- the weighing body is held by the spring assemblies on the Stellkolbenmaschine in its center position. Since only the spring assemblies are responsible for the zero position, they must be sufficiently strong in relation to the spring force, which must be overcome in normal operation at a deflection from the zero position significant counter forces.
- a hydrostatic displacement unit in the form of a swashplate axial piston machine with an actuatable by an actuator adjusting device for adjusting the displacement volume is known, wherein the actuating device is in operative connection with a restoring force generating neutral position centering.
- the zero position centering has a first functional position in which the actuating device can be acted upon by the restoring force and has a second functional position in which the actuating device can be relieved of the restoring force.
- two return pistons of the neutral position centering are longitudinally displaceably mounted in a housing bore of the housing of the displacer unit, which operatively connected to opposite contact surfaces of a driver element of the pivotally mounted swash plate can be brought.
- the return piston can be acted upon by means of a respective spring, which is arranged in a control pressure chamber, in the direction of the driver element.
- Each of the return pistons has a control pressure surface counteracting the spring, wherein the control pressure chamber arranged in front of the control pressure surface is connected to a control pressure line in which, for example, a control pressure is applied, which acts on a setting cylinder of the control device that is in operative connection with the lift actuator.
- a mechanical feedback device for resetting the control piston.
- This includes a return lever which engages in a corresponding groove in the actuating piston.
- the return lever is in operative connection with the control piston.
- the return lever of the return device is pivotally mounted about an axis.
- a pin is formed, which deflects one of two rocker arms upon pivoting of the return lever.
- a return spring is arranged between the hook-shaped end portions of the rocker arm.
- the rocker arms engage with the spool to apply the aforementioned restoring force.
- the return spring causes the centering of the control piston after switching off the control pressures acting on the control piston.
- Additionally are on the adjusting piston Centering arranged by which the actuator piston is centered in the neutral position.
- the mechanical return means are coupled via opposing acting, the restoring force generating springs in such a manner to the actuating means that the effect of the tension springs in the neutral position of the actuating means and the control repeals.
- control means comprise a valve arrangement
- control element comprises a valve slide of the valve arrangement.
- a control valve is associated with each of the pressure surfaces within the valve arrangement, wherein the control valves work in opposite directions and the control slide of the two control valves are mechanically rigidly coupled and form a common valve spool.
- control valves can each be designed as 3/3-way valves and be electromagnetically controllable.
- the mechanical return means comprise a pivotable mounted about a pivot axis, two-armed return lever, that the tension springs engage with one end on one arm of the return lever, and that the other arm of the return lever so mechanically with the control is coupled, that a pivoting movement of the return lever is converted into a deflection movement of the control.
- adjusting means are provided with which the restoring force generated by the tension springs in the neutral position of the actuating means and the control element can be adjusted to zero, wherein the adjusting means comprise in particular equipped with an eccentric adjusting mechanism, with which the Pivoting axis of the return lever in the pivoting plane can be offset.
- a further embodiment of the invention is characterized in that the adjusting means comprise two oppositely operating, mechanically coupled to each other actuating piston, the via associated control pressure chambers can be acted upon with a control pressure, and that the tension springs are each secured with one end to one of the control piston.
- the two actuating pistons engage via associated piston rods on an adjusting lever, by means of which an axial piston machine (hydrostat) mounted pivotably with a bearing journal can be pivoted to change the volume throughput.
- an axial piston machine hydrostat mounted pivotably with a bearing journal
- adjusting means comprise a hydraulic cylinder adjustable in displaced directions, whose actuating forces can be transmitted in both directions by means of corresponding piston rods, and that the tension springs each engage with one end on one of the piston rods.
- the hydraulic cylinder may advantageously be a steering cylinder of a hydraulically assisted vehicle steering system.
- the adjusting device according to the invention can be used with particular advantage in a machine unit equipped with an axial piston machine, in particular a continuously variable transmission.
- Fig. 1 is shown in a simplified functional diagram, a first embodiment of an adjusting device according to the invention.
- the adjusting device 10 comprises as actuating means two control pistons 12 and 15, which are each slidably mounted in an associated cylinder 11 and 14 and with the cylinder 11, 14 define a control pressure chamber 13 and 16, respectively, via control pressure lines 30 and 33 with a control pressure can be acted upon.
- the two adjacent to the control pressure chambers 13, 16 pressure surfaces (51, 52 in Fig. 2A ) of the actuating piston 12, 15 act in the opposite direction.
- the two adjusting pistons 12, 15 are rigidly connected in the example shown via a rod-like connecting element 18, but can also - as in Fig.
- control pressures for the control pressure chambers 13, 16 of the actuating piston 12, 15 are provided via a control valve arrangement, which is connected on the input side to a feed line 35.
- the control valve arrangement consists of two opposite directions arranged, electromagnetically actuated control valves 28 and 31, which are designed as 3/3-way valves (instead of the electromagnetic shown in the example but also just as good hydraulic or other actuators can be used).
- Each of the control valves 28, 31 is actuated by means of an actuator (electromagnet) 29 and 32, respectively, and outputs in a conventional manner a control force to the control valve Valve slide, which is thereby displaced in the axial direction, so that the control pressure to the associated actuating piston 12, 15 passed and at the same time the respective opposite control pressure chamber 13, 16 relieved to the tank.
- valve slide 27 by a corresponding control signal to one of the electromagnets 29, 32 to the left or right from the in Fig. 1 deflected shown neutral position, one of the control pressure chambers 13, 14 is acted upon by a corresponding control pressure and the actuating piston assembly 12, 15 is also made of their in Fig. 1 shown neutral position deflected.
- To control the adjustment is generated by increasing the deflection of the restoring force by means of the deflection of the piston assembly 12, 15 and introduced into the valve spool 27 by a mechanical feedback so that it counteracts the magnetic force of the controlled electromagnet 29 and 32 respectively.
- a pivot lever assembly which comprises a two-armed, pivotable about a pivot axis 24 return lever 23 which engages with a fork-shaped coupling piece 25 at the free end of one arm mounted on a valve spool 27 coupling pin 26.
- two tension springs 21 and 22 are fixed with their one end in opposite directions.
- the tension springs 21, 22 are attached to one of the adjusting pistons 12, 15.
- valve spool 27 is deflected to the right and it flows according to Fig. 2C Hydraulic fluid via the control pressure line 30 in the control pressure chamber 13 of the control pressure piston 12 and there builds a control pressure, while 15 hydraulic fluid is discharged via the control pressure line 33 from the control pressure chamber 16 of the other actuating piston.
- valve spool 27 is deflected due to the no longer compensated tensile force of the stretched tension spring in the opposite direction and causes an automatic and accurate return of the actuating piston 12, 15 in the neutral position.
- Fig. 3A shows again the neutral position
- Fig. 3B analogous to Fig. 2D the deflection to the right
- the adjusting pistons 12, 15 act via the piston rods 18a, 18b and the bearing axle 36 on an adjusting lever 37 which is fastened to the (indicated) bearing journal 38 of an axial piston machine.
- the displacement of the actuating piston thus leads to a pivoting of the axial piston machine and an associated change in the volume flow rate.
- FIG. 4 Another embodiment of the adjustment device according to the invention, as is particularly suitable for hydraulic steering systems or the like, is known in Fig. 4 schematically illustrated:
- a steering cylinder or generally a hydraulic cylinder 41 has a arranged in the cylinder center Control piston 53, which can be acted upon from either side via corresponding lines with a control pressure.
- To control the control pressure turn two control valves 48 and 49 are provided, which analogous to Fig. 1 interact.
- From the actuating piston 53 extending from both sides of the cylinder 41 outstanding two piston rods 42, 43, which are equipped at the free end with means (eg holes, eyes or the like.)
- means eg holes, eyes or the like.
- the tension springs 46, 47 engage a return lever 50, which, like the return lever 23 Fig. 1 the restoring forces on the valve assembly 48, 49 and preferably is also equipped with an adjustment mechanism 39.
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Abstract
Description
Die vorliegende Erfindung bezieht sich generell auf die hydraulische Verstellung von mechanischen Systemen, wobei sich der Verstellbereich des jeweiligen Systems in entgegengesetzten Richtungen zu beiden Seiten eines Nulldurchgangs erstreckt. Der Verstellbereich kann dabei eine Schwenkbereich aber auch eine linearer Bereich sein. Die Erfindung betrifft eine Verstellvorrichtung gemäss dem Oberbegriff des Anspruchs 1.The present invention generally relates to the hydraulic adjustment of mechanical systems, wherein the adjustment range of the respective system extends in opposite directions to either side of a zero crossing. The adjustment range can be a swivel range but also a linear range. The invention relates to an adjusting device according to the preamble of claim 1.
Bei Axialkolbenmaschinen in Schrägachsen- oder Schrägscheibenbauweise beispielsweise hängt die Pump- bzw. Antriebswirkung vom Schwenkwinkel des jeweiligen verschwenkbaren Elements ab. Beim Schwenkwinkel Null (Nullstellung) ist die Pump- bzw. Antriebswirkung der Maschine Null, während sie beim Ausschwenken aus der Nullstellung mit zunehmendem Schwenkwinkel zunimmt. Für das Verschwenken werden häufig hydraulisch betätigte Stellvorrichtungen eingesetzt, die z.B. durch elektromagnetisch betätigte Mehrwegeventile gesteuert werden.For example, in axial piston machines of a bent-axis or swash-plate design, the pumping or driving action depends on the pivoting angle of the respective pivotable element. At zero swing angle, the pumping or driving action of the machine is zero, while it increases with swinging out of zero position with increasing swing angle. For pivoting, hydraulically actuated actuators are often used, e.g. be controlled by solenoid operated multi-way valves.
In vielen Fällen ist es - unter anderem aus Sicherheitsgründen - erwünscht oder vorgeschrieben, dass bei Ausfall oder Unterbrechung bestimmter Systemfunktionen wie z.B. des für die elektromagnetisch betätigten Ventile benötigten Stroms, die Maschinen selbsttätig in die Nullstellung zurückschwenken und dort verharren. Dies gilt insbesondere aber auch für hydraulische Lenkhilfen von Fahrzeugen, wie sie in Form von Lenkzylindern beispielsweise aus der
Aus der Druckschrift
Aus der Druckschrift
Dazu sind in einer Gehäusebohrung des Gehäuses der Verdrängereinheit zwei Rückstellkolben der Nulllagenzentrierung längsverschiebbar gelagert, die mit gegenüberliegenden Anlageflächen eines Mitnehmerelements der schwenkbar gelagerten Schrägscheibe in Wirkverbindung bringbar sind. Die Rückstellkolben sind mittels jeweils einer Feder, die in einem Steuerdruckraum angeordnet ist, in Richtung des Mitnehmerelements beaufschlagbar. Die Rückstellkolben weisen jeweils eine der Feder entgegenwirkende Steuerdruckfläche auf, wobei der vor der Steuerdruckfläche angeordnete Steuerdruckraum an eine Steuerdruckleitung angeschlossen ist, in der beispielsweise ein Stelldruck ansteht, der einen mit dem Huberzeuger in Wirkverbindung stehenden Stellzylinder der Stelleinrichtung beaufschlagt. Wird Stelldruck auf den Steuerdruckraum gegeben, fährt der zugehörige Rückstellkolben aus der Nulllagenzentrierungsstellung zurück und drückt die Feder zusammen, so dass die federbedingte Rückstellwirkung auf den Kolben aufgehoben wird. Fällt der Stelldruck im Steuerdruckraum dagegen ab, drückt die Feder den Rückstellkolben und damit auch das Mitnehmerelement in die Nulllage. Auf diese Weise wird die Nulllagenzentrierung nur aktiv, wenn die zugehörige Steuerung ausfällt. Nachteilig ist bei dieser Lösung eine deutliche erhöhte Komplexität in der Steuerung. Darüber hinaus müssen auch in diesem Fall wieder die Federkräfte für die Rückstellung so gross gewählt, dass sie allein die Rückstellung in die Nulllage bewirken können.For this purpose, two return pistons of the neutral position centering are longitudinally displaceably mounted in a housing bore of the housing of the displacer unit, which operatively connected to opposite contact surfaces of a driver element of the pivotally mounted swash plate can be brought. The return piston can be acted upon by means of a respective spring, which is arranged in a control pressure chamber, in the direction of the driver element. Each of the return pistons has a control pressure surface counteracting the spring, wherein the control pressure chamber arranged in front of the control pressure surface is connected to a control pressure line in which, for example, a control pressure is applied, which acts on a setting cylinder of the control device that is in operative connection with the lift actuator. If control pressure is applied to the control pressure chamber, the associated return piston moves back from the neutral position centering position and compresses the spring so that the spring-related restoring action on the piston is released. On the other hand, if the signal pressure in the control pressure chamber drops, the spring pushes the return piston and thus also the driver element into the zero position. In this way, the neutralization is only active if the associated controller fails. A disadvantage of this solution is a significant increase in complexity in the controller. In addition, in this case too, the spring forces for the provision must again be so large that they alone can bring about the provision for the zero position.
Aus der
Durch die Rückführeinrichtung wird eine der Verstellung des Stellkolbens aus seiner Neutralstellung proportionale Rückstellkraft auf den zur Steuerung des Stellkolbens vorgesehenen Steuerkolben ausgeübt, die der von dem Steuerdruck auf den Steuerkolben ausgeübten Stellkraft entgegenwirkt. Nach Erreichen des Kräftegleichgewichts zwischen der Stellkraft und der Rückstellkraft wächst der Druck in den Stelldruckkammern nicht weiter an und die dem Steuerdruck proportionale Stellung des Stellkolbens ist erreicht.By the return means an adjustment of the actuating piston from its neutral position proportional restoring force is exerted on the control piston intended for controlling the control piston, which counteracts the force exerted by the control pressure on the control piston actuating force. After reaching the equilibrium of forces between the actuating force and the restoring force, the pressure in the control pressure chambers does not increase any further and the control pressure proportional position of the control piston is reached.
Eine vergleichbare Konfiguration ist aus der Druckschrift
Es ist daher Aufgabe der Erfindung, eine Verstellvorrichtung der eingangs genannten Art so weiterzuentwickeln, dass die Nachteile der bekannten Lösungen vermieden werden, und dass insbesondere auf einfache und funktionssichere Weise mit geringem Zusatzaufwand und ohne Beschränkung beim Verstellweg die notwendigen Rückstellkräfte erzeugt werden.It is therefore an object of the invention to develop an adjustment of the type mentioned so that the disadvantages of the known solutions are avoided, and that in particular in a simple and reliable manner with little additional effort and without restriction in the adjustment, the necessary restoring forces are generated.
Die Aufgabe wird durch die Gesamtheit der Merkmale des Anspruchs 1 gelöst.The object is solved by the entirety of the features of claim 1.
Wesentlich für die Erfindung ist, dass die mechanischen Rückführungsmittel über gegenläufig wirkende, die Rückstellkraft erzeugende Zugfedern derart an die Stellmittel angekoppelt sind, dass sich die Wirkung der Zugfedern in der Neutralstellung der Stellmittel und des Steuerelements aufhebt. Hierdurch lassen sich sehr einfach und funktionssicher die notwendigen Rückstellkräfte erzeugen, wobei ohne Schwierigkeiten grosse Verstellwege der Stellmittel realisiert werden können.It is essential for the invention that the mechanical return means are coupled via opposing acting, the restoring force generating springs in such a manner to the actuating means that the effect of the tension springs in the neutral position of the actuating means and the control repeals. This makes it possible to easily and reliably the necessary Generate restoring forces, with great difficulty adjusting paths of the actuating means can be realized without difficulty.
Eine Ausgestaltung der Erfindung zeichnet sich dadurch aus, dass die Steuermittel eine Ventilanordnung umfassen, und dass das Steuerelement einen Ventilschieber der Ventilanordnung umfasst. Vorzugsweise ist innerhalb der Ventilanordnung jeder der Druckflächen ein Regelventil zugeordnet, wobei die Regelventile gegenläufig arbeiten und die Regelschieber der beiden Regelventile mechanisch starr gekoppelt sind und einen gemeinsamen Ventilschieber bilden.An embodiment of the invention is characterized in that the control means comprise a valve arrangement, and in that the control element comprises a valve slide of the valve arrangement. Preferably, a control valve is associated with each of the pressure surfaces within the valve arrangement, wherein the control valves work in opposite directions and the control slide of the two control valves are mechanically rigidly coupled and form a common valve spool.
Insbesondere können die Regelventile jeweils als 3/3-Wegeventile ausgebildet und elektromagnetisch ansteuerbar sein.In particular, the control valves can each be designed as 3/3-way valves and be electromagnetically controllable.
Eine andere Ausgestaltung der Erfindung ist dadurch gekennzeichnet, dass die mechanischen Rückführungsmittel einen um eine Schwenkachse schwenkbar gelagerten, zweiarmigen Rückführhebel umfassen, dass die Zugfedern mit ihrem einen Ende am einen Arm des Rückführhebels angreifen, und dass der andere Arm des Rückführhebels derart mit dem Steuerelement mechanisch verkoppelt ist, dass eine Schwenkbewegung des Rückführhebels in eine Auslenkbewegung des Steuerelements umgesetzt wird.Another embodiment of the invention is characterized in that the mechanical return means comprise a pivotable mounted about a pivot axis, two-armed return lever, that the tension springs engage with one end on one arm of the return lever, and that the other arm of the return lever so mechanically with the control is coupled, that a pivoting movement of the return lever is converted into a deflection movement of the control.
Zur Erhöhung der Genauigkeit ist es von Vorteil, wenn Justiermittel vorgesehen sind, mit welchen die von den Zugfedern erzeugte Rückstellkraft in der Neutralstellung der Stellmittel und des Steuerelements auf Null einjustierbar ist, wobei die Justiermittel insbesondere einen mit einem Exzenter ausgestatteten Justiermechanismus umfassen, mit welchen die Schwenkachse des Rückführhebels in der Schwenkebene versetzt werden kann.To increase the accuracy, it is advantageous if adjusting means are provided with which the restoring force generated by the tension springs in the neutral position of the actuating means and the control element can be adjusted to zero, wherein the adjusting means comprise in particular equipped with an eccentric adjusting mechanism, with which the Pivoting axis of the return lever in the pivoting plane can be offset.
Eine weitere Ausgestaltung der Erfindung zeichnet sich dadurch aus, dass die Stellmittel zwei gegensinnig arbeitende, mechanisch miteinander gekoppelte Stellkolben umfassen, die über zugehörige Stelldruckkammern mit einem Stelldruck beaufschlagbar sind, und dass die Zugfedern jeweils mit ihrem einen Ende an einem der Stellkolben befestigt sind.A further embodiment of the invention is characterized in that the adjusting means comprise two oppositely operating, mechanically coupled to each other actuating piston, the via associated control pressure chambers can be acted upon with a control pressure, and that the tension springs are each secured with one end to one of the control piston.
Gemäss einer bevorzugten Weiterbildung greifen die beiden Stellkolben über zugehörige Kolbenstangen an einem Stellhebel an, mittels dessen eine mit einem Lagerzapfen schwenkbar gelagerte Axialkolbenmaschine (Hydrostat) zur Veränderung des Volumendurchsatzes verschwenkt werden kann.According to a preferred development, the two actuating pistons engage via associated piston rods on an adjusting lever, by means of which an axial piston machine (hydrostat) mounted pivotably with a bearing journal can be pivoted to change the volume throughput.
Eine andere Ausgestaltung der Erfindung ist dadurch gekennzeichnet, dass die Stellmittel einen in entegengesetzte Richtungen verstellbaren Hydraulikzylinder umfassen, dessen Stellkräfte in beiden Richtungen mittels entsprechender Kolbenstangen übertragbar sind, und dass die Zugfedern jeweils mit ihrem einen Ende an einer der Kolbenstangen angreifen.Another embodiment of the invention is characterized in that the adjusting means comprise a hydraulic cylinder adjustable in displaced directions, whose actuating forces can be transmitted in both directions by means of corresponding piston rods, and that the tension springs each engage with one end on one of the piston rods.
Der Hydraulikzylinder kann mit Vorteil ein Lenkzylinder einer hydraulisch unterstützten Fahrzeuglenkung sein.The hydraulic cylinder may advantageously be a steering cylinder of a hydraulically assisted vehicle steering system.
Andere Einsatzmöglichkeiten der erfindungsgemässen Verstellvorrichtung sind überall dort denkbar, wo eine geregelte hydraulische Verstellung über einen grossen Verstellbereich mit Neutralstellung realisiert werden muss.Other possible uses of the adjustment device according to the invention are conceivable everywhere where a regulated hydraulic adjustment over a large adjustment range with neutral position has to be realized.
Erfindungsgemäss kann die Verstellvorrichtung nach der Erfindung mit besonderem Vorteil in einer mit einer Axialkolbenmaschine ausgestatteten Maschineneinheit, insbesondere einem stufenlosen Getriebe eingesetzt werden.According to the invention, the adjusting device according to the invention can be used with particular advantage in a machine unit equipped with an axial piston machine, in particular a continuously variable transmission.
Die Erfindung soll nachfolgend anhand von Ausführungsbeispielen im Zusammenhang mit der Zeichnung näher erläutert werden. Es zeigen
- Fig. 1
- in einem vereinfachten Funktionsschema ein erstes Ausführungsbeispiel einer Verstellvorrichtung nach der Erfindung;
- Fig. 2A-2G
- in mehreren Teilfiguren (2A bis 2G) verschiedene Betriebszustände einer zu
Fig. 1 vergleichbaren Verstellvorrichtung nach der Erfindung; - Fig. 3A,B
- das Funktionsschema der in
Fig. 2 gezeigten Verstellvorrichtung in der Neutralstellung (3A) und bei einer Auslenkung nach rechts (3B); und - Fig. 4
- eine anderes Ausführungsbeispiel einer erfindungsgemässen Verstellvorrichtung im Rahmen einer hydraulischen Lenkung.
- Fig. 1
- in a simplified functional diagram, a first embodiment of an adjusting device according to the invention;
- Fig. 2A-2G
- in several sub-figures (2A to 2G) different operating conditions one to
Fig. 1 comparable adjusting device according to the invention; - Fig. 3A, B
- the functional scheme of in
Fig. 2 shown adjusting device in the neutral position (3A) and at a deflection to the right (3B); and - Fig. 4
- another embodiment of an inventive adjustment in the context of a hydraulic steering.
In
Die Stelldrücke für die Stelldruckkammern 13, 16 der Stellkolben 12, 15 werden über eine Regelventilanordnung bereitgestellt, die eingangsseitig an eine Speiseleitung 35 angeschlossen ist. Im Beispiel der
Wird der Ventilschieber 27 durch ein entsprechendes Steuersignal an einem der Elektromagneten 29, 32 nach links oder rechts aus der in
Zur Erzeugung und Rückführung der Rückstellkräfte ist eine Schwenkhebelanordnung vorgesehen, die einen zweiarmigen, um eine Schwenkachse 24 schwenkbaren Rückführhebel 23 umfasst, der mit einem gabelförmigen Kupplungsstück 25 am freien Ende des einen Arms einen am Ventilschieber 27 angebrachten Kupplungsbolzen 26 umgreift. Am freien Ende des anderen Arms sind in gegenläufigen Richtungen zwei Zugfedern 21 und 22 mit ihrem einen Ende befestigt. Mit dem jeweils anderen Ende sind die Zugfedern 21, 22 an einem der Stellkolben 12, 15 befestigt.To generate and return the restoring forces a pivot lever assembly is provided which comprises a two-armed, pivotable about a
Die Wirkungsweise der in
In der in
Wird jetzt gemäss
Der am Stellkolben 12 anstehende Stelldruck schiebt den Kolben nach rechts. Am Ende des Stellvorgangs (
Wird gemäss
Fällt die Steuerkraft in
Im Ausführungsbeispiel der
Eine andere Ausgestaltung der erfindungsgemässen Verstellvorrichtung, wie sie für hydraulische Lenkungen oder dgl. besonders geeignet ist, ist in
Für den Verstellmechanismus gemäss
- 10,10'10.10 '
- Verstellvorrichtungadjustment
- 11,1411.14
- Zylindercylinder
- 12,1512.15
- Stellkolbenactuating piston
- 13,1613.16
- StelldruckkammerAdjusting pressure chamber
- 1717
- Betätigungselementactuator
- 1818
- Verbindungselementconnecting element
- 18a,b18a, b
- Kolbenstangepiston rod
- 19,2019.20
- Betätigungselementactuator
- 21,2221.22
- Zugfedermainspring
- 2323
- Rückführhebel (zweiarmig)Return lever (two-armed)
- 2424
- Schwenkachseswivel axis
- 2525
- Kupplungsstück (gabelförmig)Coupling piece (forked)
- 2626
- Kupplungsbolzencoupling pin
- 2727
- Ventilschiebervalve slide
- 28,3128.31
- Regelventil (3/3-Wegeventil)Control valve (3/3-way valve)
- 29,3229.32
- Stellglied (elektrisch oder hydraulisch; z.B. Elektromagnet)Actuator (electric or hydraulic, e.g., solenoid)
- 30,3330.33
- StelldruckleitungSetting pressure line
- 3434
- Rückleitung (Hydraulikfluid)Return line (hydraulic fluid)
- 3535
- Speiseleitung (Hydraulikfluid)Feed line (hydraulic fluid)
- 3636
- Lagerachsebearing axle
- 3737
- Stellhebellever
- 3838
- Lagerzapfen (Hydrostat)Bearing pin (hydrostat)
- 3939
- Justiermechanismus (Exzenter)Adjusting mechanism (eccentric)
- 4040
- Verstellvorrichtungadjustment
- 4141
- Hydraulikzylinder (Lenkzylinder)Hydraulic cylinder (steering cylinder)
- 42,4342.43
- Kolbenstangepiston rod
- 44,4544.45
- Abgrifftap
- 46,4746.47
- Zugfedermainspring
- 48,4948.49
- 3/3-Wegeventil3/3-way valve
- 5050
- RückführhebelReturn lever
- 51,5251.52
- Druckflächeprint area
- 5353
- Stellkolbenactuating piston
Claims (12)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH9632008 | 2008-06-24 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2138720A2 true EP2138720A2 (en) | 2009-12-30 |
EP2138720A3 EP2138720A3 (en) | 2010-01-20 |
Family
ID=40524962
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09007975A Withdrawn EP2138720A3 (en) | 2008-06-24 | 2009-06-18 | Adjustment device for the adjustment of axial piston engines. |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP2138720A3 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010009975A1 (en) * | 2010-03-03 | 2011-09-08 | Sauer-Danfoss Gmbh & Co Ohg | Hydrostatic drive for use in safety-related functions, comprises closed hydraulic circuit, in which axial-piston motor and axial-piston pump with stroke volume adjusting unit are arranged |
DE102012010726A1 (en) * | 2011-10-31 | 2013-05-02 | Alpha Fluid Hydrauliksysteme Müller GmbH | Hydraulic linear drive for use in mobile machinery, has tension spring whose end is coupled with end face of control slide, and further coupled with side of auxiliary spring in mechanical coupling point |
EP2860397A1 (en) * | 2013-09-24 | 2015-04-15 | CLAAS Selbstfahrende Erntemaschinen GmbH | Drive system for hydraulically driven working parts of a working machine |
DE102014013925A1 (en) * | 2014-09-18 | 2016-03-24 | Alpha Fluid Hydrauliksysteme Müller GmbH | Electrohydraulic linear amplifier |
WO2018189153A1 (en) * | 2017-04-13 | 2018-10-18 | Danfoss Power Solutions Gmbh & Co Ohg | Self-sustaining power supply for hydrostatic pumps and motors |
DE102020205336A1 (en) | 2020-04-28 | 2021-10-28 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydraulic machine with safe zero position and synchronous adjustment cylinder |
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DE4002017A1 (en) | 1990-01-24 | 1991-07-25 | Linde Ag | Swashplate-type axial piston machine - has double-armed adjusting lever to external adjusting mechanisms |
EP0544086A2 (en) | 1991-11-28 | 1993-06-02 | Robert Bosch Gmbh | Hydraulic power assisted steering system for motor vehicles |
DE19540654C1 (en) | 1995-10-31 | 1996-12-19 | Brueninghaus Hydromatik Gmbh | Adjusting device for adjusting piston of hydrostatic engine |
DE19926965A1 (en) | 1999-06-14 | 2000-12-21 | Linde Ag | Hydrostatic axial piston engine of swash plate construction has zero position centering unit with two function positions, dependent upon regulator unit charged with/relieved from return force |
EP0802896B1 (en) | 1995-11-10 | 2001-01-03 | Mitsui Chemicals, Inc. | Method for purifying crude naphthalenedicarboxylic acid |
DE10043451A1 (en) | 1999-09-03 | 2001-04-19 | Sauer Inc | Swivel inclined axes hydraulic unit for proportional regulation has proportional magnetic fluid valve connected to computer and to control piston to control fluid pressure and cylinder block |
DE10259314A1 (en) | 2002-12-18 | 2004-07-15 | Brueninghaus Hydromatik Gmbh | electromagnet |
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DE2141724A1 (en) * | 1971-08-20 | 1973-03-01 | Bosch Gmbh Robert | CONTROL AND REGULATING DEVICE FOR A HYDROPUMP |
US4145887A (en) * | 1974-11-06 | 1979-03-27 | U.S. Philips Corporation | Swashplate compensation mechanism |
DE2834420C2 (en) * | 1978-08-05 | 1986-11-27 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Steering valve |
DE2913534A1 (en) * | 1979-04-04 | 1980-10-16 | Bosch Gmbh Robert | Flow and pressure control for variable delivery pump - has flow control valve operated by throttle differential and limited pilot pressure |
US5122037A (en) * | 1991-07-12 | 1992-06-16 | Sauer, Inc. | Manual displacement control |
DE4125706C1 (en) * | 1991-08-02 | 1993-01-14 | Hydromatik Gmbh, 7915 Elchingen, De | |
US7111545B1 (en) * | 2001-05-14 | 2006-09-26 | Hydro-Gear Limited Partnership | Return to neutral device for a hydraulic apparatus |
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2009
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Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4002017A1 (en) | 1990-01-24 | 1991-07-25 | Linde Ag | Swashplate-type axial piston machine - has double-armed adjusting lever to external adjusting mechanisms |
EP0544086A2 (en) | 1991-11-28 | 1993-06-02 | Robert Bosch Gmbh | Hydraulic power assisted steering system for motor vehicles |
DE19540654C1 (en) | 1995-10-31 | 1996-12-19 | Brueninghaus Hydromatik Gmbh | Adjusting device for adjusting piston of hydrostatic engine |
EP0802896B1 (en) | 1995-11-10 | 2001-01-03 | Mitsui Chemicals, Inc. | Method for purifying crude naphthalenedicarboxylic acid |
DE19926965A1 (en) | 1999-06-14 | 2000-12-21 | Linde Ag | Hydrostatic axial piston engine of swash plate construction has zero position centering unit with two function positions, dependent upon regulator unit charged with/relieved from return force |
DE10043451A1 (en) | 1999-09-03 | 2001-04-19 | Sauer Inc | Swivel inclined axes hydraulic unit for proportional regulation has proportional magnetic fluid valve connected to computer and to control piston to control fluid pressure and cylinder block |
DE10259314A1 (en) | 2002-12-18 | 2004-07-15 | Brueninghaus Hydromatik Gmbh | electromagnet |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010009975A1 (en) * | 2010-03-03 | 2011-09-08 | Sauer-Danfoss Gmbh & Co Ohg | Hydrostatic drive for use in safety-related functions, comprises closed hydraulic circuit, in which axial-piston motor and axial-piston pump with stroke volume adjusting unit are arranged |
DE102012010726A1 (en) * | 2011-10-31 | 2013-05-02 | Alpha Fluid Hydrauliksysteme Müller GmbH | Hydraulic linear drive for use in mobile machinery, has tension spring whose end is coupled with end face of control slide, and further coupled with side of auxiliary spring in mechanical coupling point |
DE102012010726B4 (en) | 2011-10-31 | 2023-10-19 | Alpha Fluid Hydrauliksysteme Müller GmbH | Proportional hydraulic linear drive |
EP2860397A1 (en) * | 2013-09-24 | 2015-04-15 | CLAAS Selbstfahrende Erntemaschinen GmbH | Drive system for hydraulically driven working parts of a working machine |
DE102014013925A1 (en) * | 2014-09-18 | 2016-03-24 | Alpha Fluid Hydrauliksysteme Müller GmbH | Electrohydraulic linear amplifier |
WO2018189153A1 (en) * | 2017-04-13 | 2018-10-18 | Danfoss Power Solutions Gmbh & Co Ohg | Self-sustaining power supply for hydrostatic pumps and motors |
DE102020205336A1 (en) | 2020-04-28 | 2021-10-28 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydraulic machine with safe zero position and synchronous adjustment cylinder |
Also Published As
Publication number | Publication date |
---|---|
EP2138720A3 (en) | 2010-01-20 |
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