EP2324245B1 - Hydrostatic piston engine having a pulsation reduction device - Google Patents
Hydrostatic piston engine having a pulsation reduction device Download PDFInfo
- Publication number
- EP2324245B1 EP2324245B1 EP09777918A EP09777918A EP2324245B1 EP 2324245 B1 EP2324245 B1 EP 2324245B1 EP 09777918 A EP09777918 A EP 09777918A EP 09777918 A EP09777918 A EP 09777918A EP 2324245 B1 EP2324245 B1 EP 2324245B1
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- EP
- European Patent Office
- Prior art keywords
- piston
- connection
- pressure
- piston chamber
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
- F04B1/20—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
- 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
- F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
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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
- F04B2205/00—Fluid parameters
- F04B2205/16—Opening or closing of a valve in a circuit
Definitions
- the invention relates to a hydrostatic piston engine.
- Hydrostatic piston machines such as axial piston pumps, generate a pulsating volume flow due to their mode of operation at the pump outlet.
- a pressure difference must be overcome in the transition from the suction side to the pressure side.
- Um Kunststoff Kunststoff in which a piston chamber is not connected to the suction side or the delivery pressure side, to use the occurring there piston stroke for compression of the pressure medium located in the piston chamber.
- such an increase in the pressure on the delivery-side pressure level is usually not fully adjusted. As a result, there are vibrations, noise and even Kravitations penetrate due to the flow rates that occur through the remaining pressure differences.
- the invention is therefore based on the object to provide a hydrostatic piston engine with improved pulsation reduction.
- a hydrostatic piston engine has at least one piston chamber in which a piston is slidably disposed.
- the piston chamber is alternately connected via a piston chamber opening with a first control opening and a second control opening, which are both arranged in a control part. Between the first control opening and the second control opening, a first Um Kunststoff Kunststoff or at the other Tot Vietnameses Club a second Um Kunststoff is formed.
- the hydrostatic piston engine also has a storage element which can be connected to the piston chamber opening via a connection which opens out into the first reversing region. Furthermore, the connection has a valve device. These Valve device is designed so that a flow cross-section of the connection decoupled from a position angle of the piston chamber opening relative to the control part is temporally variable by them. The position angle defines the relative position of a piston chamber opening to the control part.
- the valve device comprises at least one electromagnetically or piezoelectrically actuated valve.
- An electromagnetically operable valve is able to realize the required short switching times. It is particularly advantageous if a simple switching valve is used as a valve. Such valves are inexpensive and small and therefore can be easily integrated into a machine according to the invention.
- the control via an electromagnet also has the advantage that the operating conditions are already known for example in a control unit and therefore from the other control specifications, a corresponding control signal for timing the actuation of the solenoid-operated valve can be derived.
- the Interrupt connection temporarily completely. This improves the efficiency of the engine and allows further precompression by the piston stroke.
- the solenoid-operated valve is a switching valve with variable stroke limitation.
- the connection can only fail as a simple line, since the change in cross section is easily accessible from a first flow-through cross-section to a second flow-through cross section for the charging or discharging by this stroke-limited switching valve.
- the connection can also be completely interrupted.
- connection has a first connection line section and a second connection line section.
- a single electromagnetically actuated switching valve is preferably arranged in each connecting line section.
- the cross section can be determined via the line and it can be used in both lines identical valves.
- the limitation of the flow cross section takes place via the line cross section and not over the stroke limit of the switching valve as in the previous example. This requires the use of particularly simple constructed switching valves.
- each of the connecting line sections may be advantageously developed further in that each of the connecting line sections has a separate opening in the reversing area.
- the two discharge openings are arranged offset to one another in the direction of movement of the piston chamber opening relative to the control part. Since in a relative movement of the Piston chamber opening with respect to the control part due to the geometry of the piston chamber opening at some point the connection with the first orifice is completed, during a further relative movement of the piston chamber opening whose connection with the second orifice for a charging of the memory element can be used.
- the usable position angle range between the piston chamber opening and the control part is thus increased and the available time or, in the case of an axial piston machine, the rotational angle of the cylinder drum, which is available for the precompression and the subsequent charging of the storage element, is increased.
- this orifice is arranged relative to the first control port so that via the piston chamber opening, a connection between the first control port with the orifice can be generated.
- a connection between the first control opening and the outlet is thus produced after the pressure in the piston chamber has been increased by supplying pressure medium from the storage element through the piston chamber opening.
- the orifice is preferably arranged so that a connection of the second control opening with the orifice via the piston chamber opening is impossible solely due to the geometric conditions. This ensures that it is not possible to reduce pressure from the storage element into the low-pressure area of the pump, regardless of a possible valve position.
- the first reversing region can be connected to the first control opening by means of the valve device.
- the pressure equalization between the high pressure region of the pump and the piston chamber can be continued by removing pressure medium from the first control port after adjusting the pressure in the piston chamber and the storage element.
- the pressure can thus be further increased, so that by removing pressure medium from the high pressure side via the valve device, the pressure in the piston chamber can be adapted to the high pressure side.
- only the valve device is actuated, is then generated by the connection from the first control port to the orifice in the first Um Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff
- the temporal adaptation thus makes it possible to adapt the axial piston machine or, in general, a hydrostatic piston machine to different operating points.
- the filling of the storage element from the already degraded pressure at the transition from the high pressure to the suction side also leads to an improvement in efficiency, since the stored Liquid quantity is not removed from the delivery volume.
- the opening of the second connection in the second reversing region is also arranged so that it can be connected to the second control orifice by means of the piston chamber opening.
- the opening of the second connection in the second reversing region can also be connected to the second control opening.
- This has a similar effect as previously described for the high pressure side.
- the hydrostatic piston machine is a pump, in particular an axial piston pump, wherein the first control port is the high pressure control port and the second control port is the low pressure control port. That is, the first control port is connected to the delivery side of the pump and the second control port is connected to the suction side of the pump.
- the first Um Grill Stud then characterized in a pump, which is driven only in one direction, the transition of a piston chamber opening from the suction side to the pressure side. This is also referred to as a pressure buildup page. Therefore, the second switching area corresponds to the pressure reduction side.
- the hydrostatic piston engine is an axial piston pump, which is intended for only one direction of rotation.
- a radial piston machine with a corresponding device.
- at Machines working in two directions can use the proposed solution.
- a second, analogously constructed pulsation reduction device which is used in the case of the reverse direction of rotation.
- a temporally variable adjustment of the flow cross section is possible by means of the solution according to the invention, can be shut down when reversing the direction of rotation Pulsationsminderungsvorraum and another put into operation.
- a plan view of a control part 1 is shown.
- This control part 1 has a first control opening, hereinafter referred to as high-pressure kidney 2, and a second control opening, hereinafter referred to as suction kidney 3, on.
- the high-pressure control kidney 2 and the suction kidney 3 are approximately kidney-shaped and extend along a common circle.
- a piston chamber opening 4 is shown, which connects a front side of a cylinder drum of the axial piston machine with a piston chamber arranged therein.
- pistons are displaceably arranged for generating a delivery stroke.
- a plurality of such piston chambers are arranged distributed along a circumference circle.
- the basic structure of an axial piston machine is known, which is why a complete explanation can be dispensed with.
- the cylinder drum rotates with the direction of rotation in the Fig. 1 indicated by the arrow d.
- the individual piston chamber openings are successively alternately with the high-pressure kidney 2 or 3 Saugniere brought into connection.
- This is a pressure medium flow from the Piston space in the high-pressure kidney 2 at a corresponding pressure stroke of the piston allows.
- a suction of pressure medium in the piston chamber from the suction kidney 3 allows.
- the two Um Kunststoff Kunststoffe are the dead zones of the piston movement.
- the first Um Tavern Scheme 5 is that Um Kunststoff Kunststoff in which in a promotion of pressure medium through the axial piston machine, a transition of the piston chamber opening 4 from the suction kidney 3 to the high-pressure kidney 2 takes place.
- the pulsation reduction device comprises a storage element 7, in which pressure medium can be stored under high pressure.
- the memory element 7 is connected via a connection 8 with the first Um Kunststoff Anlagen 5.
- connection 8 opens at an orifice 9 in the first Um Kunststoff Scheme 5 so that in a relative movement of the piston chamber opening 4 to the control part of the suction kidney 3 to the high-pressure kidney 2 temporarily a contact with the orifice 9 and thus the connection 8 exists.
- the connection 8 has a first connecting line section 8.1 and a second connecting line section 8.2.
- the first connecting line section 8.1 and the second connecting line section 8.2 are formed parallel to each other and open together via the Outlet 9 in the first Um Tavern Scheme 5 off.
- a throttle is formed, which may be given for example by the line cross section of the second connecting line section 8.2.
- a valve which in this case alone forms a valve device 10.
- this valve device 10 is designed as a switching valve which can open or close the connecting line section 8.1.
- the valve device 10 forms a discharge valve, which is held by a spring in its rest position. In this position, the connection of the first connecting line section 8.1 is interrupted. From this rest position, an unthrottled connection of the first connecting line section 8.1 can be generated by means of an electromagnet, which acts on the valve against the force of the spring.
- Fig. 1 takes the piston chamber opening 4 a position angle relative to the outer dead center AT, in which there is already a contact with the orifice 9. Therefore, a connection between the piston chamber and the storage element 7 is made at least via the throttle in the second connecting line section 8.2.
- the valve device 10 is actuated for the unloading process.
- the solenoid-operated valve opens and releases the flow path of the first connecting line section 8.1 in addition. For a quick pressure equalization between the storage element 7 and the piston chamber is possible.
- FIG. 2 A second embodiment, which in contrast to the only valve-supported embodiment of Fig. 1 is valve controlled, is in the Fig. 2 shown.
- the same reference numerals mean the same elements. Their complete re-description is omitted to avoid unnecessary repetition.
- the connection 8 consists, as in the first embodiment, of a first connecting line section 8.1 and a second connecting line section 8.2.
- the valve device is now realized by a first valve 10.1 and a second valve 10.2.
- the first valve 10.1 corresponds to the already from the Fig. 1 known switching valve.
- a corresponding second valve is now also arranged in the second connecting line section 8.2.
- the connection between the memory element 7 and the first Um Kunststoff Scheme 5 can thus be completely separated. This can be achieved by the incipient piston stroke movement Exceeding the outer dead center AT in the first reversing region 5 by the piston stroke further compression of the pressure medium located in the piston chamber and thus an increase of the prevailing pressure to the pressure level of the high pressure kidney 2 takes place without pressure fluid already flows to load the storage element 7.
- the first valve 10.1 is closed.
- the second valve 10.2 is still in its closed position. Only when the pressure level of the high-pressure kidney 2 is reached, the second valve 10.2 is opened. This is advantageously done before the piston chamber opening 4 is open to the high pressure kidney 2, so that the storage element 7 can damp an overshoot of the pressure in the piston chamber. From the piston chamber and, when the piston chamber opening 4 is in communication with the high-pressure kidney 2, from the high-pressure side, charging of the storage element 7 to the pressure level of the high-pressure side is now possible. After refilling the storage element 7, the second valve 10.2 is closed again. After the next (in the Fig. 2 not shown) piston chamber opening is in contact with the orifice 9, then the first valve 10.1 is opened again.
- the flow cross sections via the first connecting line section 10.1 or the second connecting line section 10.2 are different.
- the loading and unloading processes can therefore be adapted specifically and in particular be controlled independently of time.
- FIG. 3 Such an adaptation of the flow cross sections for the loading and unloading process is also in the Fig. 3 shown.
- the connection 8 formed only by a conduit.
- the valve device 10 ' is arranged, which is realized in this case by a stroke-limited switching valve.
- a stroke-limited switching valve By means of the stroke limitation, a flow cross-section between the fully closed position of the valve device 10 'and the unthrottled position of the valve device 10' can be adjusted for the discharge.
- the formation of a second connecting line section can be omitted.
- Such a stroke-controlled switching valve can therefore effect both the function of adjusting the flow cross-section during the charging and discharging process as well as the complete separation of memory element 7 and reversing area 5.
- FIG. 4 an embodiment is shown in which the usable angle of rotation of the cylinder barrel over the embodiment with only one orifice 9 is increased.
- the charging and discharging process is again effected via a first connecting line section 18.1 or a second connecting line section 18.2. While the first connecting line section 18.1 for discharging opens at a first opening 9.1 in the first reversing area 5, the second connecting line section 18.2 opens at a second opening in the first reversing area 5.
- the first and the second orifice 9.1 and 9.2 together form the orifice 9 of the connection 8.
- the arrangement of the first orifice 9.1 and the second orifice 9.2 can therefore be carried out in the Um Kunststoff Kunststoffmaschinen, so that a larger angular position range can be used in a rotation of the cylinder drum.
- the first valve 10.1 is opened for the unloading process. As a result, the pressure in the piston chamber is increased from the storage element 7 until a pressure equilibrium between the piston chamber and the Memory element 7 is reached. Thereafter, the first valve 10.1 is closed. As has already been described above, starting from the outer dead center AT, the pressure in the piston chamber is increased by the piston stroke when the valves 10.1 and 10.2 are closed.
- the time of opening of the first valve 10.1 and the time of its closing is adjusted so that the entire Vorkompressionsvorgang, ie the discharge of pressure medium from the storage element 7 in the piston chamber and the subsequent precompression by the piston stroke generates a high pressure in the piston chamber, which Entry into the high-pressure kidney 2 corresponds to the pressure prevailing there.
- a second phase of precompression could also be done by an additional notch.
- the second discharge opening 9.2 does not open out in the first reversing area 5, but directly in the high-pressure kidney 2. This is particularly advantageous in combination with the additional notch.
- the second valve 10.2 is opened and the charging process of the storage element 7 can begin.
- the piston chamber opening 4 no longer has to be in connection with the first orifice 9.1 for this purpose.
- the total rotation angle available for a loading and unloading operation is increased.
- the usable for the pre-compression piston stroke is increased. If, for example, a nine-piston pump is used, the maximum change in the position angle ⁇ of the cylinder drum relative to the control part 1 of 40 degrees is available before the precompression operation for the next piston chamber begins.
- the second valve 10.2 must therefore be closed before the first valve 10.1 is opened again.
- Such a nine-piston pump has an opening angle of the piston chamber opening 4 of z. B. about 30 degrees.
- opening angle of the piston chamber opening 4 of z. B. about 30 degrees.
- the charging of the storage element 7 can be started by bringing the second valve 10.2 into its open position, as shown by the curve portion with a positional angle of about 372 ° to about 396 °.
- the opening of the second valve 10.2 Shortly after the opening of the second valve 10.2, an increasing connection between the piston chamber opening 4 and the high-pressure kidney 2 is produced, as shown by the curve section Hd.
- the timing of the first valve 10.1 and the second valve 10.2 is adapted to the respective operating state. In particular, the pressure increase can be taken into account by the piston stroke, so that between the closing of the first valve 10.1 and the opening of the second valve 10.2 and one of the in the Fig. 5 shown time sequence changed timing can occur.
- the Fig. 6 to 8 show a further embodiment, at different times of loading and unloading.
- the orifice 9 in the first Um Kunststoff Anlagen 5 via the valve device 10 with the high-pressure kidney 2 is connected.
- the valve device 10 is designed for this purpose as a 3/2-way valve. It can be set variably between its two end positions. In a first end position, which is predetermined as a rest position by means of a spring, the orifice 9 is connected via a line 11 to the high-pressure kidney 2. In contrast, in the second end position of the valve device 10, the connection 8 between the outlet 9 and the storage element 7 is made as already described.
- the second reversing region 6 can be connected via a further line 12 as a second connection to the connection 8.
- the connection point between the connection 8 and the further line 12 lies between the valve device 10 and the memory element 7.
- a direct connection of the two Um Kunststoff Anlagene 5 and 6 is thus avoided.
- a further valve device 14 is arranged in the further line 12.
- the further valve device 14 allows an unthrottled flow through the further line 12 in its rest position, which is also predetermined by a spring.
- the valve device 14 can be adjusted by the force of an electromagnet in the direction of the second end position.
- a second orifice 13 with which the further line 12 terminates in the second reversing region 6, is connected to the suction kidney 3.
- a Saugnieren effet 15 is provided, which connects the second valve device 14 with the suction kidney 3.
- a pressure equalization in the piston chamber is also required in the transition from the high pressure side to the low pressure side.
- a piston chamber opening 4.1 which just has no contact with the high-pressure kidney 2 due to the rotation of the cylinder drum, is replaced by the second Um Kunststoff Kunststoff 6 closed.
- the second Um Kunststoff Kunststoff 6 After exceeding the so-called inner dead center IT, a relaxation of the pressure medium in the piston chamber is made possible due to the lifting movement. The relaxation is carried out not only via the piston movement, but also via a connection of the second Um Kunststoffrios 6 with the storage element 7. After passing through the inner dead center IT, a connection between the piston chamber opening 4.1 and the other outlet 13 is made.
- the second valve device 14 is located in the in Fig. 6 shown first end position.
- the first valve device 10 is initially unchanged in its in the Fig. 6 shown rest position.
- the valve device 10 is actuated and made a connection between the storage element 7 and the orifice 9.
- the charged memory 7 in the piston chamber opening 4.3 and thus the associated piston chamber to the pressure equalization between the piston chamber and the storage element 7 relaxed.
- a connection of the storage element 7 with the second orifice 13 is not given, since the second valve device 14 in the in the Fig. 7 is shown switching position. This moment, in which the valve device 10 is brought into its switching position and the connection between the orifice 9 and the storage element 7 is made, is in the Fig. 7 shown.
- the first valve device 10 is returned to its rest position. This condition is in the Fig. 8 shown. Furthermore, the shows Fig. 8 on that the second valve device 14 is returned to its rest position. This is done after the connection between the piston chamber opening 4.1 and the second outlet 13 is interrupted.
- a modified version of the Pulsationsminderungsvortechnisch the Fig. 6 to 8 is in the Fig. 9 shown.
- the valve device 10 now comprises switching valve 10.1 ', which corresponds to the first valve 10.1 provided for the unloading process Fig. 2 and 4 equivalent.
- an additional switching valve 10.3 is provided.
- the storage element 7 is connected to the outlet 9.
- the third switching valve 10.3 is arranged in the line 11, so that regardless of the switching state of the switching valve 10.1 a connection of the orifice 9 can be made with the high-pressure kidney 2.
- a throttle 19 is further arranged.
- the second storage element 17 is connected via a storage line branch 16 to the line 11 between the throttle point 19 and the third switching valve 10.3. In this way, charging of the second storage element 17 via the throttle 19 from the high-pressure kidney 2 is possible.
- the switching valve 10.1 In order to allow after adjusting the pressure between the storage element 7 and the piston chamber of the piston chamber opening 4.3 a further pressure increase in the direction of the prevailing in the high pressure kidney 2 high pressure, after the pressure equalization between the storage element 7 and the piston chamber of the piston chamber opening 4.3, the switching valve 10.1 'in brought his closed position. This condition is in the Fig. 9 shown. Thereafter, the third switching valve 10.3 is brought into its open position and thus the second storage element 17 unthrottled connected to the outlet 9. While an unthrottled removal of the pressure medium from the storage element 17 and thus a further pressure increase in the piston chamber of the piston chamber opening 4.3 is possible, after adjusting the pressure to the high pressure of the high-pressure kidney 2, the third switching valve 10.3 can be closed again. When the third switching valve 10.3 is closed again, there is a charging of the second memory 17 via the throttle point 19. Thus, the charging cycle of the second memory 17 is extended and equalization of the pressure in the high pressure region of the axial piston machine achieved.
- the execution corresponds to the Fig. 9 already with reference to the Fig. 6 to 8 described.
- the efficiency of the piston engine As there increases the removal of the pressure fluid from the piston chambers to their required pressure reduction, the efficiency of the piston engine. However, this does not charge the storage element 7 to the level of the high-pressure side. As a result, the pressure level attainable by the precompression discharge operation is lower than in the embodiments of FIGS Fig. 1-4 , In the example below Fig. 9 This is avoided by the use of the second memory 17.
- the invention is not limited to the illustrated embodiments. In particular, it is possible to advantageously combine individual features of the various embodiments with each other.
Abstract
Description
Die Erfindung betrifft eine hydrostatische Kolbenmaschine.The invention relates to a hydrostatic piston engine.
Hydrostatische Kolbenmaschinen, wie beispielsweise Axialkolbenpumpen, erzeugen aufgrund ihrer Funktionsweise am Pumpenausgang einen pulsierenden Volumenstrom. Zudem muss beim Übergang von der Saugseite zur Druckseite ein Druckunterschied überwunden werden. Dazu ist es bekannt, im Umsteuerbereich, in dem also ein Kolbenraum nicht mit der Saugseite oder der Förderdruckseite verbunden ist, den dort stattfindenden Kolbenhub zur Kompression des in dem Kolbenraum befindlichen Druckmittels zu verwenden. Eine solchermaßen durchgeführte Anhebung des Drucks auf das förderseitige Druckniveau ist jedoch in der Regel nicht vollständig angepasst. Infolgedessen kommt es zu Vibrationen, Geräuschentwicklungen und sogar zu Kravitationsschädigungen aufgrund der Volumenströme, die durch die verbleibenden Druckunterschiede auftreten.Hydrostatic piston machines, such as axial piston pumps, generate a pulsating volume flow due to their mode of operation at the pump outlet. In addition, a pressure difference must be overcome in the transition from the suction side to the pressure side. For this purpose, it is known, in the Umsteuerbereich, in which a piston chamber is not connected to the suction side or the delivery pressure side, to use the occurring there piston stroke for compression of the pressure medium located in the piston chamber. However, such an increase in the pressure on the delivery-side pressure level is usually not fully adjusted. As a result, there are vibrations, noise and even Kravitationsschädigungen due to the flow rates that occur through the remaining pressure differences.
Aus der
Die beschriebene Lösung hat jedoch den Nachteil, dass eine Steuerung allein aufgrund der existierenden Druckunterschiede stattfindet. Eine Optimierung im Hinblick auf verschiedene Betriebszustände der Kolbenmaschine durch zeitlich gesteuerte Anpassung der unterschiedlichen Strömungsquerschnitte für den Lade- und Entladevorgang des Speicherelements kann dagegen nicht erfolgen.However, the solution described has the disadvantage that a control takes place solely because of the existing pressure differences. An optimization with regard to different operating conditions of the piston engine by timed adjustment of the different flow cross sections for the charging and discharging of the memory element, however, can not be done.
Der Erfindung liegt daher die Aufgabe zugrunde, eine hydrostatische Kolbenmaschine mit einer verbesserten Pulsationsminderung zu schaffen.The invention is therefore based on the object to provide a hydrostatic piston engine with improved pulsation reduction.
Die Aufgabe wird durch die erfindungsgemäße hydrostatische Kolbenmaschine mit den Merkmalen des Anspruchs 1 gelöst.The object is achieved by the hydrostatic piston engine according to the invention with the features of
Eine hydrostatische Kolbenmaschine gemäß der vorliegenden Erfindung weist zumindest einen Kolbenraum auf, in dem ein Kolben verschiebbar angeordnet ist. Der Kolbenraum ist über eine Kolbenraumöffnung wechselweise mit einer ersten Steueröffnung und einer zweiten Steueröffnung verbunden, die beide in einem Steuerteil angeordnet sind. Zwischen der ersten Steueröffnung und der zweiten Steueröffnung ist ein erster Umsteuerbereich beziehungsweise am anderen Totpunktsbereich ein zweiter Umsteuerbereich ausgebildet. Die hydrostatische Kolbenmaschine weist ferner ein Speicherelement auf, das über eine Verbindung, die in den ersten Umsteuerbereich ausmündet, mit der Kolbenraumöffnung verbindbar ist. Weiter weist die Verbindung eine Ventilvorrichtung auf. Diese Ventilvorrichtung ist so ausgebildet, dass durch sie ein Strömungsquerschnitt der Verbindung entkoppelt von einem Positionswinkel der Kolbenraumöffnung relativ zu dem Steuerteil zeitlich variierbar ist. Der Positionswinkel definiert die relative Stellung einer Kolbenraumöffnung zu dem Steuerteil.A hydrostatic piston engine according to the present invention has at least one piston chamber in which a piston is slidably disposed. The piston chamber is alternately connected via a piston chamber opening with a first control opening and a second control opening, which are both arranged in a control part. Between the first control opening and the second control opening, a first Umsteuerbereich or at the other Totpunktsbereich a second Umsteuerbereich is formed. The hydrostatic piston engine also has a storage element which can be connected to the piston chamber opening via a connection which opens out into the first reversing region. Furthermore, the connection has a valve device. These Valve device is designed so that a flow cross-section of the connection decoupled from a position angle of the piston chamber opening relative to the control part is temporally variable by them. The position angle defines the relative position of a piston chamber opening to the control part.
Die Ventileinrichtung umfasst zumindest ein elektromagnetisch oder piezoelektrisch betätigtes Ventil.The valve device comprises at least one electromagnetically or piezoelectrically actuated valve.
Durch eine solche zeitliche Variation des Strömungsquerschnitts, bei der der Zeitpunkt, in dem sich der Strömungsquerschnitt der Verbindung ändert, einstellbar ist, ist es möglich, die Pulsationsminderungseinrichtung optimal auf den jeweiligen Betriebszustand der Maschine anzupassen. Die Anpassung der Strömungsquerschnitte für den Ladevorgang des Speicherelements und den Entladevorgang des Speicherelements und damit der Vorkompression des Druckmittels in dem Kolbenraum kann damit zeitlich gesteuert erfolgen.By such a temporal variation of the flow cross section, in which the time at which the flow cross section of the connection changes, is adjustable, it is possible to optimally adapt the pulsation reduction device to the respective operating state of the machine. The adjustment of the flow cross sections for the charging of the storage element and the discharge of the storage element and thus the precompression of the pressure medium in the piston chamber can thus be controlled in time.
In den Unteransprüchen sind vorteilhafte Weiterbildungen der erfindungsgemäßen hydrostatischen Kolbenmaschine ausgeführt.In the dependent claims advantageous developments of the hydrostatic piston engine according to the invention are carried out.
Ein elektromagnetisch betätigbares Ventil ist in der Lage, die geforderten kurzen Schaltzeiten zu realisieren. Dabei ist es besonders vorteilhaft, wenn als Ventil ein einfaches Schaltventil zum Einsatz kommt. Solche Ventile sind preisgünstig und klein und können daher einfach in eine erfindungsgemäße Maschine integriert werden. Die Ansteuerung über einen Elektromagneten hat ferner den Vorteil, dass die Betriebszustände beispielsweise in einem Steuergerät bereits bekannt sind und deswegen aus den sonstigen Steuerungsvorgaben auch ein entsprechendes Steuersignal zur zeitlichen Steuerung der Betätigung des elektromagnetisch betätigten Ventils abgeleitet werden können. Mittels des Ventils ist besonders bevorzugt die Verbindung zeitweilig vollständig zu unterbrechen. Dies verbessert den Wirkungsgrad der Maschine und erlaubt eine weitere Vorkompression durch den Kolbenhub.An electromagnetically operable valve is able to realize the required short switching times. It is particularly advantageous if a simple switching valve is used as a valve. Such valves are inexpensive and small and therefore can be easily integrated into a machine according to the invention. The control via an electromagnet also has the advantage that the operating conditions are already known for example in a control unit and therefore from the other control specifications, a corresponding control signal for timing the actuation of the solenoid-operated valve can be derived. By means of the valve is particularly preferred the Interrupt connection temporarily completely. This improves the efficiency of the engine and allows further precompression by the piston stroke.
Es ist vorteilhaft, wenn das elektromagnetisch betätigte Ventil ein Schaltventil mit variabler Hubbegrenzung ist. In einem solchen Fall kann die Verbindung lediglich als einfache Leitung ausfallen, da die Querschnittsänderung von einem ersten durchströmbaren Querschnitt auf einen zweiten durchströmbaren Querschnitt für den Lade- beziehungsweise Entladevorgang durch dieses hubbegrenzte Schaltventil einfach erreichbar ist. Zudem kann die Verbindung ebenfalls vollständig unterbrochen werden.It is advantageous if the solenoid-operated valve is a switching valve with variable stroke limitation. In such a case, the connection can only fail as a simple line, since the change in cross section is easily accessible from a first flow-through cross-section to a second flow-through cross section for the charging or discharging by this stroke-limited switching valve. In addition, the connection can also be completely interrupted.
Gemäß einer alternativen Ausführungsform weist die Verbindung einen ersten Verbindungsleitungsabschnitt und einen zweiten Verbindungsleitungsabschnitt auf. Dabei ist vorzugsweise in jedem Verbindungsleitungsabschnitt ein einzelnes elektromagnetisch betätigtes Schaltventil angeordnet. Mit einer solchen Anordnung ist es möglich, jeweils einen Verbindungsleitungsabschnitt dem Ladevorgang und den anderen Verbindungsleitungsabschnitt dem Entladevorgang zuzuordnen. Damit kann der Querschnitt über die Leitung festgelegt werden und es können in beiden Leitungen identische Ventile zum Einsatz kommen. Die Begrenzung des Strömungsquerschnitts erfolgt dabei über den Leitungsquerschnitt und nicht wie im vorigen Beispiel über die Hubbegrenzung des Schaltventils. Dies erfordert den Einsatz besonders einfach aufgebauter Schaltventile.According to an alternative embodiment, the connection has a first connection line section and a second connection line section. In this case, a single electromagnetically actuated switching valve is preferably arranged in each connecting line section. With such an arrangement, it is possible to allocate one connecting line section to the charging process and the other connecting line section to the discharging process. Thus, the cross section can be determined via the line and it can be used in both lines identical valves. The limitation of the flow cross section takes place via the line cross section and not over the stroke limit of the switching valve as in the previous example. This requires the use of particularly simple constructed switching valves.
Die Ausführungsform mit den zwei Verbindungsleitungsabschnitten kann dahingehend vorteilhaft weiterentwickelt werden, dass jeder der Verbindungsleitungsabschnitte eine separate Ausmündungsöffnung in dem Umsteuerbereich aufweist. Die beiden Ausmündungsöffnungen sind in Bewegungsrichtung der Kolbenraumöffnung relativ zu dem Steuerteil versetzt zueinander angeordnet. Da bei einer Relativbewegung der Kolbenraumöffnung gegenüber dem Steuerteil aufgrund der Geometrie der Kolbenraumöffnung irgendwann die Verbindung mit der ersten Ausmündungsöffnung beendet ist, kann während einer weiteren Relativbewegung der Kolbenraumöffnung deren Verbindung mit der zweiten Ausmündungsöffnung für einen Ladevorgang des Speicherelements genutzt werden. Der nutzbare Positionswinkelbereich zwischen der Kolbenraumöffnung und dem Steuerteil wird somit vergrößert und die verfügbare Zeit beziehungsweise im Falle einer Axialkolbenmaschine der Drehwinkel der Zylindertrommel, der für die Vorkompression und die anschließende Aufladung des Speicherelements zur Verfügung steht, wird vergrößert.The embodiment with the two connecting line sections may be advantageously developed further in that each of the connecting line sections has a separate opening in the reversing area. The two discharge openings are arranged offset to one another in the direction of movement of the piston chamber opening relative to the control part. Since in a relative movement of the Piston chamber opening with respect to the control part due to the geometry of the piston chamber opening at some point the connection with the first orifice is completed, during a further relative movement of the piston chamber opening whose connection with the second orifice for a charging of the memory element can be used. The usable position angle range between the piston chamber opening and the control part is thus increased and the available time or, in the case of an axial piston machine, the rotational angle of the cylinder drum, which is available for the precompression and the subsequent charging of the storage element, is increased.
Gemäß einer anderen bevorzugten Ausführungsform ist im Falle einer einzelnen Ausmündungsöffnung als Ausmündung der Verbindung in dem ersten Umsteuerbereich diese Ausmündung relativ zu der ersten Steueröffnung so angeordnet, dass über die Kolbenraumöffnung eine Verbindung zwischen der ersten Steueröffnung mit der Ausmündung erzeugbar ist. Während einer Drehung beispielsweise der Zylindertrommel einer Axialkolbenmaschine wird somit nach dem Anheben des Drucks in dem Kolbenraum durch Zuführen von Druckmittel aus dem Speicherelement durch die Kolbenraumöffnung eine Verbindung zwischen der ersten Steueröffnung und der Ausmündung hergestellt. Damit wird, wenn beispielsweise im Falle der Axialkolbenpumpe die erste Steueröffnung die Hochdruckseite ist, eine Wiederaufladen des Speicherelements ermöglicht.According to another preferred embodiment, in the case of a single orifice as the mouth of the connection in the first Umsteuerbereich this orifice is arranged relative to the first control port so that via the piston chamber opening, a connection between the first control port with the orifice can be generated. During a rotation, for example, of the cylinder drum of an axial piston machine, a connection between the first control opening and the outlet is thus produced after the pressure in the piston chamber has been increased by supplying pressure medium from the storage element through the piston chamber opening. Thus, when, for example, in the case of the axial piston pump, the first control port is the high pressure side, recharging of the memory element is enabled.
Andererseits ist die Ausmündung vorzugsweise so angeordnet, dass allein aufgrund der geometrischen Gegebenheiten eine Verbindung der zweiten Steueröffnung mit der Ausmündung über die Kolbenraumöffnung unmöglich ist. Damit wird sichergestellt, dass unabhängig von einer eventuellen Ventilposition ein Abbau von Druck aus dem Speicherelement in den Niederdruckbereich der Pumpe nicht möglich ist.On the other hand, the orifice is preferably arranged so that a connection of the second control opening with the orifice via the piston chamber opening is impossible solely due to the geometric conditions. This ensures that it is not possible to reduce pressure from the storage element into the low-pressure area of the pump, regardless of a possible valve position.
Ferner ist es vorteilhaft, wenn zusätzlich mittels der Ventilvorrichtung der erste Umsteuerbereich mit der ersten Steueröffnung verbindbar ist. Damit kann der Druckausgleich zwischen Hochdruckbereich der Pumpe und dem Kolbenraum durch Entnahme von Druckmittel aus der ersten Steueröffnung nach dem Angleichen des Drucks in dem Kolbenraum und dem Speicherelement fortgesetzt werden. Der Druck lässt sich damit weiter erhöhen, so dass durch Entnahme von Druckmittel aus der Hochdruckseite über die Ventilvorrichtung der Druck in dem Kolbenraum an die Hochdruckseite angepasst werden kann. Hierzu wird lediglich die Ventilvorrichtung betätigt, durch die dann die Verbindung von der ersten Steueröffnung zu der Ausmündung in dem ersten Umsteuerbereich erzeugt wird.Furthermore, it is advantageous if, in addition, the first reversing region can be connected to the first control opening by means of the valve device. Thus, the pressure equalization between the high pressure region of the pump and the piston chamber can be continued by removing pressure medium from the first control port after adjusting the pressure in the piston chamber and the storage element. The pressure can thus be further increased, so that by removing pressure medium from the high pressure side via the valve device, the pressure in the piston chamber can be adapted to the high pressure side. For this purpose, only the valve device is actuated, is then generated by the connection from the first control port to the orifice in the first Umsteuerbereich.
Entsprechend der vorstehenden Druckangleichung beziehungsweise Druckanhebung im Kolbenraum beim Übergang von der Saugseite zur Druckseite einer Pumpe ist auch ein Druckabbau beim Übergang von der Hochdruckseite zur Niederdruckseite erforderlich. Hierzu ist es gemäß einer weiteren Weiterentwicklung vorteilhaft, wenn eine zweite Verbindung des Speicherelements vorgesehen ist, die in den zweiten Umsteuerbereich ausmündet. Diese zweite Verbindung weist eine zweite Ventilvorrichtung auf. Durch diese zweite Ventilvorrichtung ist wiederum der Strömungsquerschnitt der zweiten Verbindung zeitlich entkoppelt von einem Positionswinkel der Kolbenraumöffnung relativ zu dem Steuerteil variierbar. Damit kann auch eine Anpassung des Entspannens des Kolbenraums auf das Druckniveau der Niederdruckseite erfolgen. Die zeitliche Anpassung ermöglicht somit eine Anpassung der Axialkolbenmaschine beziehungsweise allgemein einer hydrostatischen Kolbenmaschine an verschiedene Betriebspunkte. Das Auffüllen des Speicherelements aus dem ohnehin abzubauendem Druck beim Übergang von der Hochdruck- auf die Saugseite führt außerdem zu einer Verbesserung des Wirkungsgrads, da die zu speichernde Flüssigkeitsmenge nicht aus dem Fördervolumen entnommen wird.According to the above pressure equalization or pressure increase in the piston chamber during the transition from the suction side to the pressure side of a pump and a pressure reduction during the transition from the high pressure side to the low pressure side is required. For this purpose, it is advantageous according to a further development, if a second connection of the memory element is provided, which opens into the second Umsteuerbereich. This second connection has a second valve device. By virtue of this second valve device, in turn, the flow cross-section of the second connection can be decoupled in time from a positional angle of the piston chamber opening relative to the control part. This can also be done to adapt the relaxation of the piston chamber to the pressure level of the low pressure side. The temporal adaptation thus makes it possible to adapt the axial piston machine or, in general, a hydrostatic piston machine to different operating points. The filling of the storage element from the already degraded pressure at the transition from the high pressure to the suction side also leads to an improvement in efficiency, since the stored Liquid quantity is not removed from the delivery volume.
Entsprechend der Anordnung der Ausmündung in dem ersten Umsteuerbereich ist auch die Ausmündung der zweiten Verbindung in dem zweiten Umsteuerbereich so angeordnet, dass sie mittels der Kolbenraumöffnung mit der zweiten Steueröffnung verbindbar ist.In accordance with the arrangement of the orifice in the first reversing region, the opening of the second connection in the second reversing region is also arranged so that it can be connected to the second control orifice by means of the piston chamber opening.
Mittels der zweiten Ventilvorrichtung ist ferner die Ausmündung der zweiten Verbindung in den zweiten Umsteuerbereich auch mit der zweiten Steueröffnung verbindbar. Dies hat einen ähnlichen Effekt wie zuvor für die Hochdruckseite beschrieben. Nachdem eine teilweise Angleichung durch Verbindung der Ausmündung mit dem Speicherelement erfolgt ist und somit ein teilweiser Druckabbau in dem Kolbenraum durchgeführt wurde, kann ein weiterer Druckabbau, der in das bereits gefüllte Speicherelement nicht mehr möglich ist, nun auf die Niederdruckseite, also die zweite Steueröffnung, erfolgen.By means of the second valve device, the opening of the second connection in the second reversing region can also be connected to the second control opening. This has a similar effect as previously described for the high pressure side. After a partial approximation by connection of the orifice with the storage element is carried out and thus a partial pressure reduction was carried out in the piston chamber, a further pressure reduction, which is no longer possible in the already filled storage element, now on the low pressure side, so the second control port, respectively.
Wie es vorstehend bereits beschrieben wurde, ist es bevorzugt, dass die hydrostatische Kolbenmaschine eine Pumpe, insbesondere eine Axialkolbenpumpe, ist, wobei die erste Steueröffnung die Hochdrucksteueröffnung und die zweite Steueröffnung die Niederdrucksteueröffnung ist. Das heißt, dass die erste Steueröffnung mit der Förderseite der Pumpe und die zweite Steueröffnung mit der Saugseite der Pumpe verbunden ist. Der erste Umsteuerbereich charakterisiert dann bei einer Pumpe, die lediglich in eine Richtung antreibbar ist, den Übergang einer Kolbenraumöffnung von der Saugseite zur Druckseite. Dies wird auch als Druckaufbauseite bezeichnet. Daher entspricht der zweite Umsteuerbereich der Druckabbauseite.As already described above, it is preferable that the hydrostatic piston machine is a pump, in particular an axial piston pump, wherein the first control port is the high pressure control port and the second control port is the low pressure control port. That is, the first control port is connected to the delivery side of the pump and the second control port is connected to the suction side of the pump. The first Umsteuerbereich then characterized in a pump, which is driven only in one direction, the transition of a piston chamber opening from the suction side to the pressure side. This is also referred to as a pressure buildup page. Therefore, the second switching area corresponds to the pressure reduction side.
Ausführungsbeispiele sind in der schematischen Zeichnung gezeigt und werden nachfolgend detailliert erläutert. Es zeigen:
- Fig. 1
- ein Ausführungsbeispiel einer ventilgestützten Pulsationsminderungseinrichtung einer hydrostatischen Kolbenmaschine;
- Fig. 2
- ein zweites Ausführungsbeispiel mit einer ventilgesteuerten Pulsationsminderungsvorrichtung;
- Fig. 3
- ein drittes Ausführungsbeispiel, das ebenfalls ventilgesteuert arbeitet und ein hubbegrenztes Schaltventil verwendet;
- Fig. 4
- ein viertes Ausführungsbeispiel mit zwei Ausmündungsöffnungen im ersten Umsteuerbereich;
- Fig. 5
- einen beispielhaften Verlauf der Querschnittsflächen im Falle einer ventilgesteuerten Pulsationsminderungsvorrichtung nach
Fig. 4 ; - Fig. 6
- einen ersten Zeitpunkt eines fünften Ausführungsbeispiels einer ventilgestützten Pulsationsminderungsvorrichtung beim Betrieb der hydrostatischen Kolbenmaschine;
- Fig. 7
- einen zweiten Zeitpunkt der Anordnung der
Fig. 6 ; - Fig. 8
- einen dritten Zeitpunkt der Anordnung nach
Fig. 6 ; und - Fig. 9
- ein abgewandeltes Ausführungsbeispiel der
Fig. 6 mit einem weiteren Speicherelement, das über die Hochdruckseite aufladbar ist.
- Fig. 1
- an embodiment of a valve-based Pulsationsmindernseinrichtung a hydrostatic piston engine;
- Fig. 2
- a second embodiment with a valve-controlled Pulsationsminderungsvorrichtung;
- Fig. 3
- a third embodiment, which also operates valve-controlled and uses a stroke-limited switching valve;
- Fig. 4
- a fourth embodiment with two Ausmündungsöffnungen in the first Umsteuerbereich;
- Fig. 5
- an exemplary profile of the cross-sectional areas in the case of a valve-controlled Pulsationsminderungsvorrichtung after
Fig. 4 ; - Fig. 6
- a first time of a fifth embodiment of a valve-supported Pulsationsminderungsvorrichtung in the operation of the hydrostatic piston engine;
- Fig. 7
- a second time of the arrangement of
Fig. 6 ; - Fig. 8
- a third time of the arrangement after
Fig. 6 ; and - Fig. 9
- a modified embodiment of
Fig. 6 with another storage element that can be charged via the high-pressure side.
Für die nachfolgenden Ausführungen wird davon ausgegangen, dass die hydrostatische Kolbenmaschine eine Axialkolbenpumpe ist, die für lediglich eine Drehrichtung vorgesehen ist. Es ist jedoch ebenso möglich, beispielsweise eine Radialkolbenmaschine mit einer entsprechenden Vorrichtung zu versehen. Auch bei Maschinen, die in zwei Richtungen arbeiten, kann die vorgeschlagene Lösung angewandt werden. Durch die separate Steuerung über ein Ventil beziehungsweise über die ventilgestützte Steuerung ist es nämlich möglich, eine zweite, analog aufgebaute Pulsationsminderungseinrichtung vorzusehen, welche im Fall umgekehrter Drehrichtung zum Einsatz kommt. Dadurch, dass eine zeitlich variierbare Einstellung des Strömungsquerschnitts mittels der erfindungsgemäßen Lösung möglich ist, kann bei der Umkehr der Drehrichtung eine Pulsationsminderungsvorrichtung stillgelegt und eine andere in Betrieb genommen werden.For the following statements it is assumed that the hydrostatic piston engine is an axial piston pump, which is intended for only one direction of rotation. However, it is also possible to provide, for example, a radial piston machine with a corresponding device. Also at Machines working in two directions can use the proposed solution. Because of the separate control via a valve or via the valve-supported control, it is in fact possible to provide a second, analogously constructed pulsation reduction device, which is used in the case of the reverse direction of rotation. The fact that a temporally variable adjustment of the flow cross section is possible by means of the solution according to the invention, can be shut down when reversing the direction of rotation Pulsationsminderungsvorrichtung and another put into operation.
In der
Der grundsätzliche Aufbau einer Axialkolbenmaschine ist bekannt, weswegen auf eine vollständige Erläuterung verzichtet werden kann. Die Zylindertrommel dreht sich mit der Drehrichtung, die in der
Zwischen der Hochdruckniere 2 und der Saugniere 3 sind ein erster Umsteuerbereich 5 an dem sogenannten äußeren Totpunkt AT und ein zweiter Umsteuerbereich 6 am inneren Totpunkt IT angeordnet. Die beiden Umsteuerbereiche sind die Totbereiche der Kolbenbewegung. Der erste Umsteuerbereich 5 ist dabei derjenige Umsteuerbereich, bei dem bei einer Förderung von Druckmittel durch die Axialkolbenmaschine ein Übergang der Kolbenraumöffnung 4 von der Saugniere 3 zur Hochdruckniere 2 erfolgt.Between the high-
Der Kolbenraum wird, solange die Kolbenraumöffnung 4 in Kontakt mit der Saugniere 3 steht, während des Saughubs des Kolbens mit Druckmittel befüllt. Das Druckniveau in dem Kolbenraum ist daher etwa gleich mit dem Druckniveau in der Saugniere 3. Um den Druckstoß, der beim Kontakt mit der Hochdruckniere 2 erfolgen würde, zu verringern, ist eine Pulsationsminderungsvorrichtung vorgesehen. Die Pulsationsminderungsvorrichtung umfasst ein Speicherelement 7, in dem Druckmittel unter hohem Druck gespeichert werden kann. Das Speicherelement 7 ist über eine Verbindung 8 mit dem ersten Umsteuerbereich 5 verbunden. Die Verbindung 8 mündet an einer Ausmündung 9 in den ersten Umsteuerbereich 5 so aus, dass bei einer Relativbewegung der Kolbenraumöffnung 4 zu dem Steuerteil von der Saugniere 3 zu der Hochdruckniere 2 zeitweilig ein Kontakt zu der Ausmündung 9 und damit der Verbindung 8 existiert. In dem dargestellten Ausführungsbeispiel weist die Verbindung 8 einen ersten Verbindungsleitungsabschnitt 8.1 und einen zweiten Verbindungsleitungsabschnitt 8.2 auf. Der erste Verbindungsleitungsabschnitt 8.1 und der zweite Verbindungsleitungsabschnitt 8.2 sind parallel zueinander ausgebildet und münden gemeinsam über die Ausmündung 9 in dem ersten Umsteuerbereich 5 aus. In dem zweiten Verbindungsleitungsabschnitt 8.2 ist eine Drossel ausgebildet, die beispielsweise auch durch den Leitungsquerschnitt des zweiten Verbindungsleitungsabschnitts 8.2 gegeben sein kann.As long as the
In dem ersten Verbindungsleitungsabschnitt 8.2 ist ein Ventil vorgesehen, welches in diesem Fall allein eine Ventilvorrichtung 10 bildet. Diese Ventilvorrichtung 10 ist im dargestellten Beispiel als Schaltventil ausgeführt, welches den Verbindungsleitungsabschnitt 8.1 öffnen oder schließen kann. Die Ventilvorrichtung 10 bildet ein Entladeventil, welches durch eine Feder in seiner Ruheposition gehalten wird. In dieser Position ist die Verbindung des ersten Verbindungsleitungsabschnitts 8.1 unterbrochen. Aus dieser Ruheposition heraus kann mittels eines Elektromagneten, der das Ventil entgegen der Kraft der Feder beaufschlagt, eine ungedrosselte Verbindung des ersten Verbindungsleitungsabschnitts 8.1 erzeugt werden.In the first connecting line section 8.2, a valve is provided which in this case alone forms a
Nachfolgend wird die Funktion zur Pulsationsminderung erläutert. In der
Ein zweites Ausführungsbeispiel, welches im Gegensatz zu dem nur ventilgestützten Ausführungsbeispiel der
Die Verbindung 8 besteht wie schon im ersten Ausführungsbeispiel aus einem ersten Verbindungsleitungsabschnitt 8.1 und einem zweiten Verbindungsleitungsabschnitt 8.2. Die Ventilvorrichtung ist nunmehr jedoch durch ein erstes Ventil 10.1 und ein zweites Ventil 10.2 realisiert. Das erste Ventil 10.1 entspricht dem schon aus der
Um den Ladevorgang des Speicherelements 7 und den Entladevorgang des Speicherelements 7 zu beeinflussen, sind die Strömungsquerschnitte über den ersten Verbindungsleitungsabschnitt 10.1 oder den zweiten Verbindungsleitungsabschnitt 10.2 unterschiedlich. Die Lade- und Entladevorgänge können daher gezielt angepasst werden und insbesondere zeitlich unabhängig gesteuert werden.In order to influence the charging process of the
Eine solche Anpassung der Strömungsquerschnitte für den Lade- und Entladevorgang ist auch in der
In der
Eine schematische Darstellung der jeweils durchströmbaren Querschnitte A über dem Positionswinkel α einer Kolbenraumöffnung 4 relativ zu dem Steuerteil 2 ist in der
Nachdem das erste Ventil 10.1 wieder geschlossen ist, kann der Ladevorgang des Speicherelements 7 begonnen werden, indem das zweite Ventil 10.2 in seine geöffnete Position gebracht wird, wie es durch den Kurvenabschnitt mit einem Positionswinkel von etwa 372° bis etwa 396° gezeigt ist. Kurz nach dem Öffnen des zweiten Ventils 10.2 wird eine zunehmende Verbindung zwischen der Kolbenraumöffnung 4 und der Hochdruckniere 2 hergestellt wie es durch den Kurvenabschnitt Hd gezeigt ist. Die zeitliche Steuerung des ersten Ventils 10.1 und des zweiten Ventils 10.2 wird dabei an den jeweiligen Betriebszustand angepasst. Insbesondere kann auch die Druckerhöhung durch den Kolbenhub berücksichtigt werden, so dass zwischen dem Schließen des ersten Ventils 10.1 und dem Öffnen des zweiten Ventils 10.2 auch ein von der in der
Die
Ferner ist der zweite Umsteuerbereich 6 über eine weitere Leitung 12 als zweite Verbindung mit der Verbindung 8 verbindbar. Der Verbindungspunkt zwischen der Verbindung 8 und der weiteren Leitung 12 liegt dabei zwischen der Ventilvorrichtung 10 und dem Speicherelement 7. Eine direkte Verbindung der beiden Umsteuerbereiche 5 und 6 wird damit vermieden. In der weiteren Leitung 12 ist eine weitere Ventilvorrichtung 14 angeordnet. Die weitere Ventilvorrichtung 14 ermöglicht dabei eine ungedrosselte Durchströmung der weiteren Leitung 12 in ihrer Ruheposition, die ebenfalls durch eine Feder vorgegeben ist. In entgegengesetzter Richtung kann in Richtung der zweiten Endposition die Ventilvorrichtung 14 durch die Kraft eines Elektromagneten verstellt werden. In der zweiten Endposition ist eine zweite Ausmündung 13, mit der die weitere Leitung 12 in dem zweiten Umsteuerbereich 6 ausmündet, mit der Saugniere 3 verbunden. Hierzu ist eine Saugnierenleitung 15 vorgesehen, die die zweite Ventilvorrichtung 14 mit der Saugniere 3 verbindet.Furthermore, the second reversing
Wie es vorstehend bereits angedeutet wurde, ist auch beim Übergang von der Hochdruckseite auf die Niederdruckseite eine Druckangleichung in dem Kolbenraum erforderlich. Eine Kolbenraumöffnung 4.1, die aufgrund der Drehung der Zylindertrommel gerade keinen Kontakt mehr mit der Hochdruckniere 2 hat, wird durch den zweiten Umsteuerbereich 6 verschlossen. Nach dem Überschreiten des sogenannten inneren Totpunkts IT wird aufgrund der Hubbewegung eine Entspannung des Druckmittels in dem Kolbenraum ermöglicht. Die Entspannung wird dabei nicht nur über die Kolbenbewegung durchgeführt, sondern auch über eine Verbindung des zweiten Umsteuerbereichs 6 mit dem Speicherelement 7. Nach dem Durchlaufen des inneren Totpunkts IT wird eine Verbindung zwischen der Kolbenraumöffnung 4.1 und der weiteren Ausmündung 13 hergestellt. Die zweite Ventilvorrichtung 14 befindet sich in der in der
Während des Druckabbaus des Drucks in dem Kolbenraum der Kolbenraumöffnung 4.1 in den Speicher 7 und anschließend in die Saugniere 3 befindet sich die erste Ventilvorrichtung 10 zunächst unverändert in ihrer in der
Bei einer weiteren Drehung, zu einem Zeitpunkt, da eine Druckanhebung in dem Kolbenraum der Kolbenraumöffnung 4.3 durch Entladen des Speichers 7 nicht mehr möglich ist, wird die erste Ventilvorrichtung 10 wieder in ihre Ruheposition gebracht. Dieser Zustand ist in der
Für den Druckabbau der der Kolbenraumöffnung 4.1 nachfolgenden Kolbenraumöffnung beim Übergang von der Hochdruckseite auf die Niederdruckseite ist somit die zweite Ventilvorrichtung 14 wieder bereit und erzeugt die Verbindung zwischen der weiteren Ausmündung 13 und dem Speicherelement 7. Damit kann der beschriebene Lade- und Entladevorgang des Speicherelements 7 und damit verbunden die Angleichung oder Anpassung des Drucks in den Kolbenräumen beim Übergang von der Hochdruck- auf die Niederdruckseite oder der Niederdruck- auf die Hochdruckseite erfolgen.For the pressure reduction of the piston chamber opening 4.1 subsequent piston chamber opening at the transition from the high pressure side to the low pressure side is thus the
Eine abgewandelte Version der Pulsationsminderungsvorrichtung der
Um nach dem Angleichen des Drucks zwischen dem Speicherelement 7 und dem Kolbenraum der Kolbenraumöffnung 4.3 eine weitere Druckerhöhung in Richtung des in der Hochdruckniere 2 herrschenden Hochdrucks zu ermöglichen, wird nach dem Druckangleichen zwischen dem Speicherelement 7 und dem Kolbenraum der Kolbenraumöffnung 4.3 das Schaltventil 10.1' in seine geschlossene Position gebracht. Dieser Zustand ist in der
Im Übrigen entspricht die Ausführung der
Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt. Insbesondere ist es möglich, einzelne Merkmale der verschiedenen Ausführungsbeispiele vorteilhaft miteinander zu kombinieren.The invention is not limited to the illustrated embodiments. In particular, it is possible to advantageously combine individual features of the various embodiments with each other.
Claims (11)
- Hydrostatic piston engine with at least one piston space, in which a piston is arranged displaceably, the piston space being connectable via a piston-space port (4, 4.i) alternately to a first control port (2) or a second control port (3) of a control part (1), and a first and a second reversing region (5, 6) being formed between the first control port (2) and the second control port (3), and with an accumulator element (7) which is connectable to the piston-space port (4, 4.i) via a connection (8) which issues in the first reversing region (5), this connection (8) having a valve device (10), characterized in that, by means of this valve device, the flow cross section of the connection (8) can be varied in time in relation to the control part (1) in a manner decoupled from a position angle (α) of the piston-space port (4), and in that the valve device (10) comprises at least one electromagnetically or piezoelectrically actuated valve (10.1, 10.2, 10.3, 10', 10.1').
- Hydrostatic piston engine according to Claim 1, characterized in that the electromagnetically actuated valve (10') is a switching valve with variable stroke limitation.
- Piston engine according to Claim 1 or 2, characterized in that the connection (8) has a first and a second connecting-line portion (8.1, 8.2), and an electromagnetically or piezoelectrically actuated switching valve (10.1, 10.2) is arranged in each connecting-line portion (8.1, 8.2).
- Piston engine according to Claim 3, characterized in that the first connecting-line portion (8.1) has a first issue (9.1) into the first reversing region (5), and the second connecting-line portion (8.2) has a second issue (9.2) into the first reversing region (5) or into the high-pressure kidney region (2), the first and the second issue (9.1, 9.2) being arranged so as to be offset with respect to one another in relation to the control part (1) in the direction of movement (d) of the piston-space port (4).
- Piston engine according to one of Claims 1 to 3, characterized in that the issue (9) of the connection (8) in the first reversing region (5) is arranged such that the first control port (2) is connectable to the issue (9) by means of the piston-space port (4).
- Piston engine according to one of Claims 1 to 5, characterized in that the issue (9) of the connection (8) in the first reversing region (5) is arranged such that a connection between the second control port (3) and the issue (9) via a piston-space port (4, 4.i) is geometrically not possible.
- Piston engine according to one of Claims 1 to 5, characterized in that the first reversing region (5) is connectable to the first control port (2) by means of the valve device (10).
- Piston engine according to one of Claims 1 to 6, characterized in that a second connection (12) of the accumulator element (7) is provided, which issues in the second reversing region (6), and in that the second connection (12) has a second valve device (14), by means of which the flow cross section of the second connection (12) can be varied in time in relation to the control part (1) in a manner decoupled from a position angle of the piston-space ports (4, 4.i).
- Piston engine according to Claim 7, characterized in that a second issue (13) of the second connection (12) in the second reversing region (6) is arranged such that the said second issue is connectable to the second control port (3) by means of the piston-space port (4, 4.i).
- Piston engine according to Claim 7 or 8, characterized in that the second issue (13) of the second connection (12) into the second reversing region (6) is connectable to the second control port (3) via the second valve device (14).
- Piston engine according to one of Claims 1 to 9, characterized in that the hydrostatic piston engine is a pump and the first control port (2) is connected to the delivery side of the pump and the second control port (3) to the suction side of the pump, and the first reversing region (5) corresponds to the pressure buildup side defined by a direction of movement (d) of the piston-space port (4, 4.i) in relation to the control part (1).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008046258 | 2008-09-08 | ||
DE102008061349A DE102008061349A1 (en) | 2008-09-08 | 2008-12-10 | Hydrostatic piston machine with pulsation reduction device |
PCT/EP2009/005947 WO2010025822A1 (en) | 2008-09-08 | 2009-08-17 | Hydrostatic piston engine having a pulsation reduction device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2324245A1 EP2324245A1 (en) | 2011-05-25 |
EP2324245B1 true EP2324245B1 (en) | 2012-02-29 |
Family
ID=41650900
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09777918A Not-in-force EP2324245B1 (en) | 2008-09-08 | 2009-08-17 | Hydrostatic piston engine having a pulsation reduction device |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2324245B1 (en) |
AT (1) | ATE547626T1 (en) |
DE (1) | DE102008061349A1 (en) |
WO (1) | WO2010025822A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105378278A (en) * | 2013-05-22 | 2016-03-02 | 贺德克传动中心有限公司 | Axial piston pump |
DE102020201800A1 (en) | 2020-02-13 | 2021-08-19 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydrostatic axial piston machine with pressure side change |
DE102020212372A1 (en) | 2020-09-30 | 2022-03-31 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydrostatic axial piston machine |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011117081A1 (en) | 2011-10-27 | 2013-05-02 | Robert Bosch Gmbh | Hydrostatic piston machine |
WO2013068210A1 (en) | 2011-11-12 | 2013-05-16 | Robert Bosch Gmbh | Hydrostatic piston engine |
WO2013068211A1 (en) * | 2011-11-12 | 2013-05-16 | Robert Bosch Gmbh | Hydrostatic piston engine |
FR3000770B1 (en) * | 2013-01-08 | 2015-03-20 | Technoboost | HYDRAULIC MACHINE WITH TWO DIRECTION OF ROTATION, COMPRISING A PRE-COMPRESSION CHAMBER |
DE102021203902A1 (en) | 2021-04-20 | 2022-10-20 | Robert Bosch Gesellschaft mit beschränkter Haftung | Axial piston machine with high operating speed and low pressure pulsation |
DE102022107860A1 (en) | 2022-04-01 | 2023-10-05 | Danfoss Power Solutions Inc. | Hydraulic axial piston unit and method for controlling a hydraulic axial piston unit |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1211943B (en) * | 1957-01-18 | 1966-03-03 | Bosch Gmbh Robert | Device for noise reduction in a rotary valve-controlled hydraulic axial or radial piston machine that can be used as a pump or motor |
US3283726A (en) * | 1964-12-14 | 1966-11-08 | American Brake Shoe Co | Construction for pump/motor devices |
US3956969A (en) * | 1974-12-09 | 1976-05-18 | Caterpillar Tractor Co. | Hydrostatic pump including separate noise reducing valve assemblies for its inlet and outlet pressure ports |
GB2123093B (en) * | 1982-06-03 | 1985-10-23 | Ifield Eng Pty | Hydraulic pumps |
SE507637C2 (en) * | 1991-09-06 | 1998-06-29 | Parker Hannifin Ab | Method and apparatus for damping flow pulsations in hydrostatic displacement hydraulic machines and apparatus for carrying out the method |
JP2606758Y2 (en) * | 1992-12-22 | 2001-01-09 | 株式会社小松製作所 | Hydraulic pump / motor cylinder chamber pressure control device |
DE19706116C5 (en) | 1997-02-17 | 2012-12-20 | Linde Material Handling Gmbh | Device for pulsation reduction on hydrostatic displacement units |
-
2008
- 2008-12-10 DE DE102008061349A patent/DE102008061349A1/en not_active Withdrawn
-
2009
- 2009-08-17 WO PCT/EP2009/005947 patent/WO2010025822A1/en active Application Filing
- 2009-08-17 EP EP09777918A patent/EP2324245B1/en not_active Not-in-force
- 2009-08-17 AT AT09777918T patent/ATE547626T1/en active
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105378278A (en) * | 2013-05-22 | 2016-03-02 | 贺德克传动中心有限公司 | Axial piston pump |
CN105378278B (en) * | 2013-05-22 | 2017-12-19 | 贺德克传动中心有限公司 | Axial poiston pump |
DE102020201800A1 (en) | 2020-02-13 | 2021-08-19 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydrostatic axial piston machine with pressure side change |
US11603829B2 (en) | 2020-02-13 | 2023-03-14 | Robert Bosch Gmbh | Hydrostatic axial piston machine having pressure side change |
DE102020212372A1 (en) | 2020-09-30 | 2022-03-31 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydrostatic axial piston machine |
Also Published As
Publication number | Publication date |
---|---|
ATE547626T1 (en) | 2012-03-15 |
DE102008061349A1 (en) | 2010-03-11 |
WO2010025822A1 (en) | 2010-03-11 |
EP2324245A1 (en) | 2011-05-25 |
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