EP2776713B1 - Hydrostatic piston engine - Google Patents
Hydrostatic piston engine Download PDFInfo
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- EP2776713B1 EP2776713B1 EP12775661.7A EP12775661A EP2776713B1 EP 2776713 B1 EP2776713 B1 EP 2776713B1 EP 12775661 A EP12775661 A EP 12775661A EP 2776713 B1 EP2776713 B1 EP 2776713B1
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- 230000002706 hydrostatic effect Effects 0.000 title claims description 19
- 239000012530 fluid Substances 0.000 claims description 39
- 230000033001 locomotion Effects 0.000 claims description 6
- 230000010349 pulsation Effects 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 238000013461 design Methods 0.000 description 5
- 238000013016 damping Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000002045 lasting effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003973 paint Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
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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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
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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
- F04B1/205—Cylindrical
Definitions
- the invention relates to a hydrostatic piston engine, in particular an axial piston engine, according to the preamble of patent claim 1.
- a hydrostatic piston engine has a rotating cylinder part with a plurality of cylinder chambers, in which pistons carrying a lifting movement are arranged during operation.
- each cylinder space is alternately connected via a cylinder space opening to a low pressure control port and a high pressure control port on a control surface of a stationary control part at which there are two Um Kunststoffe between the low pressure control port and the high pressure control within which a piston reverses its direction of motion, and the one Vormatinut extending from a control opening into a Um Kunststoff Kunststoff into.
- Such axial piston machine is for example in the DE 197 06 116 A1 revealed.
- the known axial piston machine has as a cylinder part arranged on a drive shaft cylinder drum with a plurality of cylinder chambers, in each of which a piston is movably guided.
- Each cylinder space can be alternately connected to a cylinder-shaped opening introduced on the front side of the cylinder drum with a kidney-shaped low-pressure control opening and high-pressure control opening provided in a control disk serving as a control part.
- the cylinder drum slides along the face of the control disk.
- the low-pressure control opening and the high-pressure opening lie on a common pitch circle and are spaced apart in the circumferential direction, whereby two Um Kunststoff Kunststoffe are formed.
- a respective piston is located in a Um Kunststoff Kunststoff in the region of its inner dead center or bottom Dead Center (BDC), where he is the farthest immersed in his cylinder chamber, and in the other Um Kunststoffe in the area of its outer dead center or Top Dead Center (TDC), in which it protrudes furthest out of his cylinder room.
- BDC bottom Dead Center
- TDC Top Dead Center
- the from the DE 197 06 116 A1 known hydrostatic axial piston machine in swash plate design is adjustable from a positive displacement volume above zero displacement volume to a negative displacement volume and can work in four-quadrant operation, ie in both directions both as a pump and as a motor.
- the reversal between high pressure and low pressure is to be improved in terms of reducing pressure pulsations by virtue of the fact that the cylinder chambers in the corresponding reversing region are connected to a fluid capacity or to a storage volume.
- a memory element is provided which is connected via a non-return valve blocking it and a throttle arranged parallel to the check valve with an orifice in the reversal area of a control plate.
- the orifice is at a certain mode of operation of the known displacement machine at a short distance from the high pressure control port of the control plate.
- a cylinder chamber opening is opened to the orifice as soon as their connection to the low pressure control opening is closed.
- pressurized fluid flows via the check valve from the storage element into the cylinder chamber.
- the connection of the cylinder chamber is made with the high pressure control port and then brought the storage element via the throttle back to high pressure.
- the reversal is further influenced by the fact that from the high-pressure control opening from a pilot groove extends into the Um Kunststoff Kunststoff inside.
- a cavity which is filled or to be filled with a liquid pressure medium, for example hydraulic oil, and in which a pressure change is due solely to the compressibility of the pressure medium connected to an inflow or outflow of pressure medium.
- a liquid pressure medium for example hydraulic oil
- the invention has for its object to provide a hydrostatic piston engine in which a Umêtkapaztician is easily throttled constantly connected to the associated pressure port.
- a hydrostatic piston engine in particular an axial piston engine, has a rotating cylinder part with a plurality of cylinder chambers, in which pistons carrying a lifting movement are arranged during operation.
- Each cylinder chamber is in operation via a cylinder chamber opening alternately connectable to a low pressure control port and a high pressure control port on a control surface of a stationary control part, in which there are two Um Kunststoff Kunststoffe between the low pressure control port and the high pressure control within which a piston at a dead center reverses its direction, and the one Vor Kunststoffnut extending from a control opening into a Um Kunststoff Kunststoff into.
- an opening is provided in a reversing area, which at least approximately approaches the cylinder space openings paint over their entire length. It is provided a fluid capacity of defined size, with which the outlet is connected via a particular throttled fluid connection. The outlet is located in the pilot groove.
- the pilot control groove in which the orifice is located, advantageously has a cross section, which in particular increases continuously in the direction of the control opening.
- the cross-sectional ratios are obtained simply by positioning the outlet of the fluid connection in the pilot groove so that the pilot groove extends from the orifice over a greater distance, preferably over about two-thirds of its total length toward the control port and over a smaller distance to its Leaping out.
- the type of reversal is chosen in particular for a reversal of low pressure to high pressure in pump operation or engine operation. Accordingly, the pilot control groove, in which the mouth of the fluid connection is positioned to the fluid capacity, exits from the high pressure control port. However, the type of reversal is also applicable to the reversal of high pressure to low pressure.
- the throttling effect of the fluid communication between the orifice and the fluid capacity is advantageously independent of the direction of flow of the fluid.
- parts of a hydrostatic axial piston machine are shown in swash plate design, which is to be operated while maintaining the direction of rotation and without change of high pressure and low pressure side both as a pump and as a motor.
- the swash plate not shown in detail can therefore be pivoted in opposite directions in a known manner with respect to a zero position in which at least theoretically no pressure medium flow through the machine.
- Such an axial piston machine is usually referred to as being pivotable or adjustable over zero.
- a cylinder drum 25 In a cylinder drum 25 are in each case the same distance from a drum axis and at equal angular intervals from each other several, for example, nine cylinder chambers 26 in the form of cylinder bores in which non-illustrated pistons are movably received and at one end of the cylinder drum in elongated, usually curved cylinder space openings 27, which in the Following control slots are called, open.
- the width of the control slots 27 is smaller than the diameter of a cylinder bore.
- the cylinder drum 25 rests with the end face with the control slots 27 on a serving as a control part control plate 28 and slides in operation over this time.
- the control plate has two kidney-shaped control openings 29 and 30, which are located on the same pitch circle as the control slots 27 and of which present the control port 29 as a high pressure control port in which a high pressure (for example a pressure of 200 bar) is present in operation, and the Control port 30 serves as a low-pressure control opening in which a low pressure (for example, a pressure of less than 5 bar), in particular tank pressure, is present during operation.
- control slots 27 change from an open fluidic connection to the high-pressure control opening 29 to an open fluidic connection to the low-pressure control opening 30, and a reversing area 32, in that the control slots 27 change from an open fluidic connection to the low-pressure control opening 30 to an open fluidic connection to the high-pressure control opening 29.
- pilot grooves mounted, of which in the figures, a pilot control groove 34 is shown at the high pressure control port.
- the pilot groove 34 is designed so that its cross section from the high pressure control port 29 decreases continuously. It is a triangular notch whose depth and width are linearly reduced from a control port.
- the control plate 28 is against rotation on a connection plate 40 of the axial piston machine, wherein in the connection plate, a high-pressure channel 41 and a low-pressure channel 42 are formed, which lead from an outer side of the connection plate to the control plate facing end side of the connection plate and at this end face a the control openings in the control plate have corresponding cross-sectional shape and at least largely coincide with the control openings.
- connection plate 40 which forms a fluid capacity or a storage volume and of which a through the connection plate 40th and the control plate 28 passing through bore 46 with an opening 47 in the Um Grill Scheme 31.
- the orifice 47 is located in the pilot control groove 34, which, as already mentioned, is a triangular groove with a continuously decreasing cross section away from the control opening 29.
- the position of the orifice in the pilot groove 34 is selected so that the cross section of the pilot groove in the region of the orifice is smaller than the cross section of the throttle bore 46.
- FIG. 2 There is a two control slots 27 separated from each other web of the cylinder drum 25 just above the pilot groove 34.
- a control slot 27 is located in front of the pilot groove 34 in the Um Kunststoff Anlagen 32.
- the storage volume 45 is connected via the throttle bore 46 and the pilot control groove 34 with the high pressure control port 29 and further to the high pressure passage 41. Therefore, the same pressure prevails in the storage volume 45 as in the high-pressure control opening 29.
- the leading edge of the control slot 27 continues to sweep the pilot groove 34 to a position where it reaches the high pressure pilot port 29 (see FIG FIG. 4 ).
- the further pressure buildup proceeds as in a standard reversing, which has only the pilot control groove 34.
- the control slot 27 of the cylinder chamber 26 passes over the high pressure control port 29 (see FIG. 5 ). Due to the above-described cross-sectional ratios of throttle bore 46 and pilot control groove 34, the pressure equalization between the high pressure control port 29 and the storage volume 45 begins substantially only after the pressure equalization between the high pressure control port 29 and the cylinder chamber 26 is reached. The result is a total of over a longer period lasting and thus uniformed fluid removal from the high-pressure control port 29 and the related parts of the hydraulic circuit for the pressure build-up in the cylinder chamber 26 and thus a significant reduction in pressure pulsations in the high pressure area.
Description
Die Erfindung betrifft eine hydrostatische Kolbenmaschine, insbesondere eine Axialkolbenmaschine, gemäß dem Oberbegriff des Patentanspruchs 1. Eine solche hydrostatische Kolbenmaschine weist ein rotierendes Zylinderteil mit mehreren Zylinderräumen, in denen im Betrieb eine Hubbewegung ausführende Kolben angeordnet sind. Im Betrieb wird jeder Zylinderraum über eine Zylinderraumöffnung wechselweise mit einer Niederdrucksteueröffnung und einer Hochdrucksteueröffnung an einer Steuerfläche eines ruhenden Steuerteils verbunden, an dem sich zwischen der Niederdrucksteueröffnung und der Hochdrucksteueröffnung zwei Umsteuerbereiche befinden, innerhalb derer ein Kolben in einem Totpunkt seine Bewegungsrichtung umkehrt, und das eine Vorsteuernut aufweist, die sich von einer Steueröffnung aus in einen Umsteuerbereich hinein erstreckt.The invention relates to a hydrostatic piston engine, in particular an axial piston engine, according to the preamble of patent claim 1. Such a hydrostatic piston engine has a rotating cylinder part with a plurality of cylinder chambers, in which pistons carrying a lifting movement are arranged during operation. In operation, each cylinder space is alternately connected via a cylinder space opening to a low pressure control port and a high pressure control port on a control surface of a stationary control part at which there are two Umsteuerbereiche between the low pressure control port and the high pressure control within which a piston reverses its direction of motion, and the one Vorsteuernut extending from a control opening into a Umsteuerbereich into.
Eine derartige Axialkolbenmaschine ist zum Beispiel in der
Die aus der
Arbeitet die aus der
Die Begriffe "Speichervolumen und "Fluidkapazität" sollen im Folgenden jeweils dieselbe Bedeutung haben. Insbesondere wird ein Hohlraum so benannt, der mit einem flüssigen Druckmittel, zum Beispiel Hydrauliköl gefüllt ist oder zu füllen ist und bei dem eine Druckänderung schon allein wegen der Kompressibilität des Druckmittels mit einem Zufluss oder Abfluss von Druckmittel verbunden ist.The terms "storage volume and" fluid capacity "shall each have the same meaning in the following: In particular, a cavity is named which is filled or to be filled with a liquid pressure medium, for example hydraulic oil, and in which a pressure change is due solely to the compressibility of the pressure medium connected to an inflow or outflow of pressure medium.
Der liegt der Erfindung die Aufgabe zugrunde, eine hydrostatische Kolbenmaschine zu schaffen, bei der eine Umsteuerkapazität auf einfache Weise ständig gedrosselt an den zugehörigen Druckanschluss angebunden ist.The invention has for its object to provide a hydrostatic piston engine in which a Umsteuerkapazität is easily throttled constantly connected to the associated pressure port.
Diese Aufgabe wird gelöst durch eine hydrostatische Kolbenmaschine gemäß den Merkmalen des Patentanspruchs 1.This object is achieved by a hydrostatic piston engine according to the features of patent claim 1.
Erfindungsgemäß hat eine hydrostatische Kolbenmaschine, insbesondere eine Axialkolbenmaschine, ein rotierendes Zylinderteil mit mehreren Zylinderräumen, in denen im Betrieb eine Hubbewegung ausführende Kolben angeordnet sind. Jeder Zylinderraum ist im Betrieb über eine Zylinderraumöffnung wechselweise mit einer Niederdrucksteueröffnung und einer Hochdrucksteueröffnung an einer Steuerfläche eines ruhenden Steuerteils verbindbar, an dem sich zwischen der Niederdrucksteueröffnung und der Hochdrucksteueröffnung zwei Umsteuerbereiche befinden, innerhalb derer ein Kolben in einem Totpunkt seine Bewegungsrichtung umkehrt, und das eine Vorsteuernut aufweist, die sich von einer Steueröffnung aus in einen Umsteuerbereich hinein erstreckt. Erfindungsgemäß ist in einem Umsteuerbereich eine Ausmündung vorgesehen, die die Zylinderraumöffnungen zumindest annähernd auf ihrer gesamten Länge überstreichen. Es ist eine Fluidkapazität definierter Größe vorgesehen, mit der die Ausmündung über eine insbesondere gedrosselte Fluidverbindung verbunden ist. Die Ausmündung liegt in der Vorsteuernut.According to the invention, a hydrostatic piston engine, in particular an axial piston engine, has a rotating cylinder part with a plurality of cylinder chambers, in which pistons carrying a lifting movement are arranged during operation. Each cylinder chamber is in operation via a cylinder chamber opening alternately connectable to a low pressure control port and a high pressure control port on a control surface of a stationary control part, in which there are two Umsteuerbereiche between the low pressure control port and the high pressure control within which a piston at a dead center reverses its direction, and the one Vorsteuernut extending from a control opening into a Umsteuerbereich into. According to the invention, an opening is provided in a reversing area, which at least approximately approaches the cylinder space openings paint over their entire length. It is provided a fluid capacity of defined size, with which the outlet is connected via a particular throttled fluid connection. The outlet is located in the pilot groove.
Bisher in der Praxis eingesetzte hydrostatische Kolbenmaschinen mit einer internen Druckübertragung auf Stell- und/oder Regelsysteme erfordern eine für die Stabilität notwendige Dämpfung des Systems. Auftretende hohe Pulsationen für die Drucksignalverarbeitung müssen hydraulisch oder elektrisch gedämpft werden. Dies hat negative Auswirkungen auf die Dynamik der Einheit. Bestehende Lösungen basieren also auf der Dämpfung des Nutzsignals, wobei bei einer hydraulischen Bedämpfung außer einer Verringerung der Dynamik auch hydraulische Verluste aufgrund von Dämpfungsdüsen auftreten können. Erfindungsgemäß findet eine direkte, verlustfreie Pulsationsreduzierung an der Signalentnahmestelle der Fluid-Kolbenmaschine statt. Es ist eine höhere Verstelldynamik möglich. Wegen geringerer Dämpfungsverluste aufgrund der erfindungsgemäßen Ausbildung ist bei hydraulischen Reglern eine Wirkungsgradverbesserung der Einheit im Regelbetrieb möglich. Das Betriebsverhalten der Kolbenmaschine ist also verbessert. Die erfindungsgemäße Ausbildung ist in einfacher Weise bei vorhandenen Umsteuerungen möglich. Eine erfindungsgemäße Umsteuerung hat einen großen nutzbaren Funktionsbereich.Previously used in practice hydrostatic piston machines with an internal pressure transfer to control and / or regulating systems require a necessary for stability damping of the system. Occurring high pulsations for the pressure signal processing must be hydraulically or electrically damped. This has a negative impact on the dynamics of the unit. Existing solutions are therefore based on the attenuation of the useful signal, wherein in a hydraulic damping in addition to a reduction in dynamics and hydraulic losses due to damping nozzles can occur. According to the invention, a direct, loss-free pulsation reduction takes place at the signal delivery point of the fluid piston machine. It is possible a higher Verstelldynamik. Due to lower damping losses due to the design according to the invention, an improvement in the efficiency of the unit in control mode is possible with hydraulic controllers. The operating behavior of the piston engine is thus improved. The inventive design is possible in a simple manner with existing reversals. A reversal according to the invention has a large usable functional area.
Bei einer erfindungsgemäßen hydrostatischen Kolbenmaschine ist somit eine zur Umsteuerung genutzte Fluidkapazität auf einfache, kostengünstige und kompakte Weise ständig an den zugeordneten Druckanschluss (Hochdrucksteueröffnung oder Niederdrucksteueröffnung am Steuerteil) angebunden.In a hydrostatic piston machine according to the invention thus used for reversal fluid capacity in a simple, inexpensive and compact way constantly connected to the associated pressure port (high pressure control port or low pressure control port on the control part).
Vorteilhafte Weiterbildungen einer erfindungsgemäßen hydrostatischen Kolbenmaschine finden sich in den Unteransprüchen.Advantageous developments of a hydrostatic piston engine according to the invention can be found in the subclaims.
Die Vorsteuernut, in der die Ausmündung liegt, hat vorteilhafterweise einen Querschnitt, der sich zur Steueröffnung hin insbesondere kontinuierlich vergrößert. Durch geeignete Wahl der Stelle, an der sich die Ausmündung längs der Vorsteuernut befindet, können dann Durchflussquerschnitte und damit die Fluidmengen, die einerseits zwischen Zylinderraum und Fluidkapazität und andererseits zwischen Zylinderraum und die Steueröffnung fließen, aufeinander abgestimmt werden.The pilot control groove, in which the orifice is located, advantageously has a cross section, which in particular increases continuously in the direction of the control opening. By suitable choice of the point at which the orifice is located along the pilot groove, can flow cross sections and thus the amounts of fluid flowing on the one hand between the cylinder chamber and fluid capacity and on the other hand between the cylinder chamber and the control port, are matched.
Eine vorteilhafte Abstimmung ergibt sich durch eine solche Positionierung der Ausmündung in der Vorsteuernut und einen solchen Drosselquerschnitt der Fluidverbindung, dass der Drosselquerschnitt der Fluidverbindung größer ist als der Querschnitt der Vorsteuernut im Bereich der Ausmündung und die Vorsteuernut zur Steueröffnung hin noch einen Querschnitt hat, der wesentlich größer als der Drosselquerschnitt der Fluidverbindung ist, und zu seinem Auslauf hin noch einen Querschnitt hat, der wesentlich kleiner als der Drosselquerschnitt der Fluidverbindung ist.An advantageous vote results from such a positioning of the orifice in the pilot groove and such a throttle cross-section of the fluid connection, that the throttle cross section of the fluid connection is greater than the cross section of the pilot groove in the region of the orifice and the pilot groove to the control opening out still has a cross section, the essential is greater than the throttle cross section of the fluid connection, and to its outlet still has a cross-section which is substantially smaller than the throttle cross section of the fluid connection.
Bevorzugt erhält man die Querschnittverhältnisse einfach dadurch, dass die Ausmündung der Fluidverbindung in die Vorsteuernut so positioniert ist, dass sich die Vorsteuernut von der Ausmündung aus über eine größere Strecke, vorzugsweise über etwa zwei Drittel seiner Gesamtlänge zur Steueröffnung hin und über eine kleinere Strecke zu seinem Auslaufende hin erstreckt.Preferably, the cross-sectional ratios are obtained simply by positioning the outlet of the fluid connection in the pilot groove so that the pilot groove extends from the orifice over a greater distance, preferably over about two-thirds of its total length toward the control port and over a smaller distance to its Leaping out.
Die Art der Umsteuerung wird insbesondere für eine Umsteuerung von Niederdruck zu Hochdruck im Pumpenbetrieb oder Motorbetrieb gewählt. Dementsprechend geht die Vorsteuernut, in der die Ausmündung der Fluidverbindung zu der Fluidkapazität positioniert ist, von der Hochdrucksteueröffnung aus. Die Art der Umsteuerung ist jedoch auch auf die Umsteuerung von Hochdruck zu Niederdruck übertragbar.The type of reversal is chosen in particular for a reversal of low pressure to high pressure in pump operation or engine operation. Accordingly, the pilot control groove, in which the mouth of the fluid connection is positioned to the fluid capacity, exits from the high pressure control port. However, the type of reversal is also applicable to the reversal of high pressure to low pressure.
Die Drosselwirkung der Fluidverbindung zwischen der Ausmündung und der Fluidkapazität ist vorteilhafterweise unabhängig von der Strömungsrichtung des Fluids.The throttling effect of the fluid communication between the orifice and the fluid capacity is advantageously independent of the direction of flow of the fluid.
Vom anderen Ende der bisher betrachteten Steueröffnung oder von einem Ende der anderen Steueröffnung aus kann sich in einen Umsteuerbereich hinein ebenfalls eine Vorsteuernut mit insbesondere kontinuierlicher Querschnittserweiterung erstrecken. Eine Ausmündung der Fluidverbindung zu einer anderen Fluidkapazität kann in Laufrichtung des Zylinderteils gesehen seitlich neben dieser zweiten Vorsteuernut in der Steuerfläche liegen.From the other end of the previously considered control opening or from one end of the other control opening can also extend in a Umsteuerbereich into a pilot groove with particular continuous cross-sectional widening. An opening of the fluid connection to another fluid capacity can in the running direction the cylinder part seen laterally adjacent to this second pilot groove in the control surface.
Im Folgenden wird ein bevorzugtes Ausführungsbeispiel der Erfindung anhand von Zeichnungen näher erläutert.In the following, a preferred embodiment of the invention will be explained in more detail with reference to drawings.
Es zeigen:
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Figur 1 in einem Schnitt Steuerplatte und Anschlussplatte einer erfindungsgemäßen Axialkolbenmaschine gemäß dem Ausführungsbeispiel, -
Figur 2 in einem Schnitt Zylindertrommel, Steuerplatte und Anschlussplatte des Ausführungsbeispiel nachFigur 1 , wobei die Zylindertrommel eine bestimmte Position gegenüber einer Steuerplatte einnimmt und sich die Axialkolbenmaschine im Pumpenbetrieb befindet, -
Figur 3 denselben Schnitt wie inFigur 2 bei weitergedrehter Zylindertrommel, -
Figur 4 denselben Schnitt wie inFigur 3 bei weitergedrehter Zylindertrommel und -
Figur 5 denselben Schnitt wie inFigur 4 bei weitergedrehter Zylindertrommel.
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FIG. 1 in a section control plate and connection plate of an axial piston according to the invention according to the embodiment, -
FIG. 2 in a section cylinder drum, control plate and connection plate of the embodiment according toFIG. 1 in which the cylinder drum assumes a specific position in relation to a control plate and the axial piston machine is in pump operation, -
FIG. 3 the same cut as inFIG. 2 with further rotated cylindrical drum, -
FIG. 4 the same cut as inFIG. 3 at further rotated cylinder drum and -
FIG. 5 the same cut as inFIG. 4 with further rotated cylinder drum.
In den Figuren sind jeweils Teile einer hydrostatischen Axialkolbenmaschine in Schrägscheibenbauweise gezeigt, die unter Beibehaltung der Drehrichtung und ohne Wechsel von Hochdruck- und Niederdruckseite sowohl als Pumpe als auch als Motor betrieben werden soll. Die nicht näher gezeigte Schrägscheibe kann deshalb in bekannter Weise bezüglich einer Nulllage, in der wenigstens theoretisch kein Druckmittelfluss durch die Maschine stattfindet, nach entgegengesetzten Richtungen verschwenkt werden. Eine solche Axialkolbenmaschine wird üblicherweise als über null verschwenkbar oder verstellbar bezeichnet.In the figures, parts of a hydrostatic axial piston machine are shown in swash plate design, which is to be operated while maintaining the direction of rotation and without change of high pressure and low pressure side both as a pump and as a motor. The swash plate not shown in detail can therefore be pivoted in opposite directions in a known manner with respect to a zero position in which at least theoretically no pressure medium flow through the machine. Such an axial piston machine is usually referred to as being pivotable or adjustable over zero.
In einer Zylindertrommel 25 befinden sich in jeweils gleichem Abstand von einer Trommelachse und in gleichen Winkelabständen voneinander mehrere, zum Beispiel neun Zylinderräume 26 in Form von Zylinderbohrungen, in denen nicht näher dargestellte Kolben bewegbar aufgenommen sind und die an einer Stirnseite der Zylindertrommel in länglichen, üblicherweise gekrümmten Zylinderraumöffnungen 27, die im Folgenden Steuerschlitze genannt werden, ausmünden. Die Breite der Steuerschlitze 27 ist kleiner als der Durchmesser einer Zylinderbohrung.In a
Die Zylindertrommel 25 liegt mit der Stirnseite mit den Steuerschlitzen 27 an einer als Steuerteil dienenden Steuerplatte 28 an und gleitet im Betrieb über diese hinweg. Die Steuerplatte besitzt zwei nierenförmige Steueröffnungen 29 und 30, die sich auf demselben Teilkreis wie die Steuerschlitze 27 befinden und von denen vorliegend die Steueröffnung 29 als Hochdrucksteueröffnung, in der im Betrieb ein hoher Druck (zum Beispiel ein Druck von 200 bar) ansteht, und die Steueröffnung 30 als Niederdrucksteueröffnung dient, in der im Betrieb ein niedriger Druck (zum Beispiel ein Druck kleiner 5 bar), insbesondere Tankdruck ansteht. Zwischen der Hochdrucksteueröffnung 29 und der Niederdrucksteueröffnung 30 gibt es auf der Steuerplatte zwei Umsteuerbereiche, nämlich einen nicht gezeigten Umsteuerbereich, in dem die Steuerschlitze 27 von einer offenen fluidischen Verbindung zur Hochdrucksteueröffnung 29 zu einer offenen fluidischen Verbindung zur Niederdrucksteueröffnung 30 wechseln, und einen Umsteuerbereich 32, in dem die Steuerschlitze 27 von einer offenen fluidischen Verbindung zur Niederdrucksteueröffnung 30 zu einer offenen fluidischen Verbindung zur Hochdrucksteueröffnung 29 wechseln.The
Innerhalb der beiden Umsteuerbereiche liegen auch die Totpunkte in der Hubbewegung der Kolben, in denen die Kolben am weitesten in eine Zylinderbohrung eingetaucht sind (innerer Totpunkt) oder am weitesten aus einer Zylinderbohrung herausragen (äußerer Totpunkt). Je nachdem, wie die Schrägscheibe gerade bezüglich der Nulllage verschwenkt ist, liegt ein Totpunkt innerhalb des einen Umsteuerbereichs oder innerhalb des anderen Umsteuerbereichs.Within the two Umsteuerbereiche are also the dead centers in the lifting movement of the piston, in which the pistons are the most immersed in a cylinder bore (internal dead center) or furthest out of a cylinder bore (outer dead center). Depending on how the swash plate is pivoted with respect to the zero position, a dead center lies within the one Umsteuerbereichs or within the other Umsteuerbereichs.
Um bei der Umsteuerung Druckspitzen in den Zylinderbohrungen und ungleichförmige Strömung und Druckpulsationen in den Steueröffnungen 29 und 30 und damit in Fluid-anschlüsse der Axialkolbenmaschine und im gesamten hydraulischen System gering zu halten, sind an einem Ende oder an beiden Enden einer Steueröffnung oder an den Enden beider Steueröffnungen 29 und 30 Vorsteuernuten angebracht, von denen in den Figuren eine Vorsteuernut 34 an der Hochdrucksteueröffnung gezeigt ist. Die Vorsteuernut 34 ist so gestaltet, dass sich ihr Querschnitt von der Hochdrucksteueröffnung 29 aus kontinuierlich verringert. Sie ist eine Dreieckskerbe, deren Tiefe und Breite sich von einer Steueröffnung aus linear verringern.In order to keep small pressure peaks in the cylinder bores and non-uniform flow and pressure pulsations in the
Die Steuerplatte 28 liegt verdrehsicher an einer Anschlussplatte 40 der Axialkolbenmaschine an, wobei in der Anschlussplatte ein Hochdruckkanal 41 und ein Niederdruckkanal 42 ausgebildet sind, die von einer Außenseite der Anschlussplatte zu der der Steuerplatte zugekehrten Stirnseite der Anschlussplatte führen und die an dieser Stirnseite eine den Steueröffnungen in der Steuerplatte entsprechende Querschnittsform haben und sich mit den Steueröffnungen zumindest weitgehend decken.The
Um über die Wirkung der Vorsteuernuten hinaus eine Funktionsverbesserung der Umsteuerung bei der bestimmungsgemäß als Pumpe und als Motor betreibbaren Axialkolbenmaschine herbeizuführen, ist in der Anschlussplatte 40 ein Hohlraum 45 definierter Größe vorgesehen, der eine Fluidkapazität oder ein Speichervolumen bildet und von dem eine durch die Anschlussplatte 40 und die Steuerplatte 28 hindurchgehende Bohrung 46 mit einer Ausmündung 47 in den Umsteuerbereich 31 ausgeht. Durch die Bohrung 46 ist eine gedrosselte Verbindung zwischen dem Speichervolumen und der Ausmündung 47 gebildet. Die Ausmündung 47 befindet sich in der Vorsteuernut 34, die wie schon erwähnt eine Dreiecksnut mit von der Steueröffnung 29 weg kontinuierlich abnehmendem Querschnitt ist.In order to bring about the effect of Vorsteuernuten addition function improvement of the reversal in the intended operation as a pump and motor axial piston, a
Und zwar ist die Position der Ausmündung in der Vorsteuernut 34 so gewählt, dass der Querschnitt der Vorsteuernut im Bereich der Ausmündung kleiner als der Querschnitt der Drosselbohrung 46 ist. Andererseits gibt es zwischen der Ausmündung 47 und dem auslaufenden ende der Vorsteuernut 34 noch eine längere Strecke, in der der Querschnitt der Vorsteuernut wesentlich kleiner als der Querschnitt der Drosselbohrung 46 ist. Zur Hochdrucksteueröffnung 29 gibt es andererseits noch eine Strecke der Vorsteuernut 34, in der deren Querschnitt wesentlich größer als der Querschnitt der Drosselbohrung 46 ist.Namely, the position of the orifice in the
An der Steuerplatte 28 gleitet im Betrieb eine Zylindertrommel 25 mit Zylinderräumen 26, in denen sich Kolben befinden und die sich in Steuerschlitzen 27 zur Steuerplatte hin öffnen, entlang. Dies ist genauso wie bei den schon beschriebenen Ausführungsbeispielen.During operation, a
Ausgangspunkt für die Betrachtung der Funktionsweise sei nun die
Bei weiterer Drehung der Zylindertrommel 25 überstreicht der Steuerschlitz 27 eines betrachteten Zylinderraums 26 die Vorsteuernut von deren der Hochdrucksteueröffnung 29 entfernten Ende her, bis sich ihre Vorderkante über der Ausmündung 47 befindet (siehe
Die Vorderkante des Steuerschlitzes 27 überstreicht die Vorsteuernut 34 weiter bis zu einer Position, an der sie die Hochdrucksteueröffnung 29 erreicht (siehe
Somit wird bei einer Umsteuerung von Niederdruck zu Hochdruck bis zum Druckausgleich zwischen einem Zylinderraum und der Hochdrucksteueröffnung weniger Fluid für den Druckaufbau im Zylinderraum aus der Hochdrucksteueröffnung 29 und dem Hochdruckkanal 41 entnommen als bei einer Umsteuerung ohne Speichervolumen.Thus, in a reversal of low pressure to high pressure to the pressure equalization between a cylinder chamber and the high-pressure control opening less fluid for the pressure build-up in the cylinder chamber from the high-
Zum in der
Bei weiterer Drehung der Zylindertrommel 25 überstreicht der Steuerschlitz 27 des Zylinderraums 26 die Hochdrucksteueröffnung 29 (siehe
Die Lösung, bei der die Ausmündung in einer Vorsteuernut liegt, bietet insbesondere folgende Vorteile:
- Gegenüber einer Standardumsteuerung mit Vorsteuernuten mit kontinuierlicher Querschnittserweiterung sind die Druckpulsationen an dem Anschluss, zu dem hin die erfindungsgemäße Umsteuerung angewandt wird, deutlich geringer. Zudem ist eine Kolbenmaschine mit herkömmlicher Umsteuerung mit einem geringen Aufwand bei der Auslegung nachrüstbar.
- Gegenüber einer Umsteuerung unter Nutzung eines Speichervolumens, bei dem die Ausmündung eines das Speichervolumen mit einem Umsteuerbereich verbindenden
- Compared to a standard reversing with pilot control grooves with continuous cross-sectional widening, the pressure pulsations at the connection, to which the reversal control according to the invention is applied, are significantly lower. In addition, a piston engine with conventional reversal with a little effort in the design can be retrofitted.
- Compared to a reversal using a storage volume, wherein the mouth of the storage volume with a Umsteuerbereich connecting
Kanals außerhalb einer Vorsteuernut im Umsteuerbereich liegt, besteht der Vorteil, dass mit einem einzigen Speichervolumen und einer einzigen Ausmündung ein größerer Betriebsbereich einer hydrostatischen Kolbenmaschine sehr gut abgedeckt werden, da die unterlegte Standardumsteuerung mit einer Vorsteuernut deutlich "toleranter" ist. Das Speichervolumen kann kleiner ausgelegt werden, wobei die Umsteuerung voll funktionsfähig erhalten bleibt.
Gegenüber einer Umsteuerung mit einer ständigen, gedrosselten Verbindung zwischen dem Speichervolumen und einer Hochdrucksteueröffnung, bei der zusätzlich zu einem Kanal, der vom Speichervolumen zum Umsteuerbereich führt, eine zusätzliche Drosselbohrung zwischen dem Speichervolumen und dem Hochdruckbereich der Kolbenmaschine vorhanden ist, entfällt diese zusätzliche Drosselbohrung. Die Wirksamkeit des Speichervolumens ist durch die automatisch querschnittsgesteuerte Unterbrechung des Ladevorgangs noch verbessert.Channel lies outside a pilot groove in the Umsteuerbereich, there is the advantage that with a single storage volume and a single orifice a larger operating range of a hydrostatic piston engine are very well covered, as the underlying standard reversal with a pilot groove is significantly "tolerant". The storage volume can be made smaller, while the reversal remains fully functional.
Compared to a reversal with a constant, throttled connection between the storage volume and a high-pressure control opening, in addition to a channel leading from the storage volume to the Umsteuerbereich, an additional throttle bore between the storage volume and the high pressure region of the piston engine is present, eliminating this additional throttle bore. The effectiveness of the storage volume is further improved by the automatic cross-section-controlled interruption of the charging process.
Claims (6)
- Hydrostatic piston engine, in particular hydrostatic axial piston engine, having a rotating cylinder part (25) with a plurality of cylinder spaces (26), in which pistons are arranged which perform a reciprocating movement during operation, it being possible for each cylinder space (26) to be connected via a cylinder space opening (27) alternately to a low pressure control opening (30) and a high pressure control opening (29) of a stationary control part (28), on which two reversing regions are situated between the low pressure control opening (30) and the high pressure control opening (29), within which reversing regions a piston reverses its direction of movement at a dead centre, and which control part (28) has a pilot control groove (34) which extends from a control opening (29) into a reversing region (32), characterized in that a mouth (47) is provided in the said reversing region (32), over which mouth (47) the cylinder space openings (27) sweep at least approximately on their entire length, in that a fluid capacity (45) of defined magnitude is provided which is connected to the mouth (47) via an, in particular, throttled fluid connection (46), and in that the mouth (47) lies in the pilot control groove (34).
- Hydrostatic piston engine according to Patent Claim 1, characterized in that the cross section of the pilot control groove (34) increases in size, in particular continuously, towards the control opening (29).
- Hydrostatic piston engine according to Patent Claim 2, characterized by positioning of the mouth (47) in the pilot control groove (34) such that, and a throttle cross section of the fluid connection (46) which is such that, the throttle cross section of the fluid connection (46) is greater than the cross section of the pilot control groove (34) in the region of the mouth (47) and the pilot control groove (34) still has a cross section towards the control opening (29), which cross section is substantially greater than the throttle cross section of the fluid connection (29), and still has a cross section towards its outlet, which cross section is substantially smaller than the throttle cross section of the fluid connection (46).
- Hydrostatic piston engine according to Patent Claim 2 or 3, characterized in that the pilot control groove (34), in which the mouth (47) of the fluid connection (46) is positioned towards the fluid capacity (45), emanates from the high pressure control opening (29).
- Hydrostatic piston engine according to a preceding patent claim, characterized in that the throttle action of the fluid connection (46) is independent of the flow direction of the fluid in it.
- Hydrostatic piston engine according to a preceding patent claim, characterized in that a second pilot control groove with, in particular, continuous cross-sectional widening extends from a control opening into a reversing region, in that a second fluid capacity of defined magnitude is provided, and in that the second fluid capacity is connected via an, in particular, throttled fluid connection to a mouth which lies laterally next to the pilot control groove as viewed in the running direction of the cylinder part.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102011118402 | 2011-11-12 | ||
PCT/EP2012/070534 WO2013068213A1 (en) | 2011-11-12 | 2012-10-17 | Hydrostatic piston engine |
Publications (2)
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EP2776713A1 EP2776713A1 (en) | 2014-09-17 |
EP2776713B1 true EP2776713B1 (en) | 2015-12-30 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP12775661.7A Active EP2776713B1 (en) | 2011-11-12 | 2012-10-17 | Hydrostatic piston engine |
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EP (1) | EP2776713B1 (en) |
CN (1) | CN103917780B (en) |
DE (1) | DE102012218888A1 (en) |
IN (1) | IN2014DN03439A (en) |
WO (1) | WO2013068213A1 (en) |
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DE102014208406A1 (en) * | 2014-05-06 | 2015-11-12 | Robert Bosch Gmbh | Hydrostatic piston machine |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
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DE3725361A1 (en) * | 1987-07-30 | 1989-02-16 | Brueninghaus Hydraulik Gmbh | AXIAL PISTON MACHINE IN TYPE DISC OR TYPE AXIS DESIGN WITH SLOT CONTROL AND PRESSURE COMPENSATION CHANNELS |
JPH08144941A (en) * | 1994-11-21 | 1996-06-04 | Uchida Yuatsu Kiki Kogyo Kk | Pulsation reduction device for cam plate type axial piston pump |
JP3362576B2 (en) * | 1995-02-10 | 2003-01-07 | ダイキン工業株式会社 | Variable displacement piston machine |
DE19706116C5 (en) | 1997-02-17 | 2012-12-20 | Linde Material Handling Gmbh | Device for pulsation reduction on hydrostatic displacement units |
JP2000345955A (en) * | 1999-05-31 | 2000-12-12 | Toshiba Mach Co Ltd | Piston pump/motor |
DE10206957B4 (en) * | 2002-02-19 | 2014-09-04 | Linde Hydraulics Gmbh & Co. Kg | Hydrostatic displacement unit with a device comprising a memory element for reducing pulsations |
JP4646972B2 (en) * | 2005-02-10 | 2011-03-09 | 株式会社小松製作所 | Hydraulic piston pump |
-
2012
- 2012-10-17 CN CN201280055240.0A patent/CN103917780B/en active Active
- 2012-10-17 IN IN3439DEN2014 patent/IN2014DN03439A/en unknown
- 2012-10-17 DE DE201210218888 patent/DE102012218888A1/en not_active Withdrawn
- 2012-10-17 WO PCT/EP2012/070534 patent/WO2013068213A1/en active Application Filing
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CN103917780B (en) | 2016-12-14 |
IN2014DN03439A (en) | 2015-06-05 |
WO2013068213A1 (en) | 2013-05-16 |
EP2776713A1 (en) | 2014-09-17 |
CN103917780A (en) | 2014-07-09 |
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