EP2324245B1 - Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations - Google Patents

Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations Download PDF

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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.)
Not-in-force
Application number
EP09777918A
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German (de)
English (en)
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EP2324245A1 (fr
Inventor
Timo Nafz
Ruslan Rudik
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2324245A1 publication Critical patent/EP2324245A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Claims (11)

  1. Machine à piston hydrostatique comprenant au moins une chambre de piston, dans laquelle est disposé un piston déplaçable, la chambre de piston pouvant être connectée par le biais d'une ouverture de chambre de piston (4, 4.i) de manière alternative à une première ouverture de commande (2) ou à une deuxième ouverture de commande (3) d'une partie de commande (1) et entre la première ouverture de commande (2) et la deuxième ouverture de commande (3) étant réalisées une première et une deuxième région d'inversion (5, 6), et comprenant un élément accumulateur (7) qui peut être connecté par le biais d'une connexion (8), qui débouche dans la première région d'inversion (5), à l'ouverture de chambre de piston (4, 4.i),
    cette connexion (8) présentant un dispositif de soupape (10), caractérisée en ce que la section transversale d'écoulement de la connexion (8) peut être variée dans le temps par ce dispositif de soupape de manière désaccouplée d'un angle de position (a) de l'ouverture de chambre de piston (4) par rapport à la partie de commande (1), et
    en ce que le dispositif de soupape (10) comprend au moins une soupape à commande électromagnétique ou piézoélectrique (10.1, 10.2, 10.3, 10', 10.1').
  2. Machine à piston hydrostatique selon la revendication 1,
    caractérisée en ce que
    la soupape (10') à commande électromagnétique est une soupape de commutation à limite de levée variable.
  3. Machine à piston selon la revendication 1 ou 2,
    caractérisée en ce que
    la connexion (8) présente une première et une deuxième portion de conduite de connexion (8.1, 8.2) et dans chaque portion de conduite de connexion (8.1, 8.2) est disposée une soupape de commutation à commande électromagnétique ou piézoélectrique (10.1, 10.2).
  4. Machine à piston selon la revendication 3,
    caractérisée en ce que
    la première portion de conduite de connexion (8.1) présente une première embouchure (9.1) dans la première région d'inversion (5) et la deuxième portion de conduite de connexion (8.2) présente une deuxième embouchure (9.2) dans la première région d'inversion (5) ou dans la partie en forme de haricot HP (2), la première et la deuxième embouchure (9.1, 9.2) étant disposées de manière décalée l'une par rapport à l'autre dans la direction de déplacement (d) de l'ouverture de chambre de piston (4) par rapport à la partie de commande (1).
  5. Machine à piston selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce que
    l'embouchure (9) de la connexion (8) est disposée dans la première région d'inversion (5) de telle sorte que la première ouverture de commande (2) puisse être connectée à l'embouchure (9) au moyen de l'ouverture de la chambre de piston (4).
  6. Machine à piston selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    l'embouchure (9) de la connexion (8) est disposée dans la première région d'inversion (5) de telle sorte qu'une connexion entre la deuxième ouverture de commande (3) et l'embouchure (9) par le biais d'une ouverture de la chambre de piston (4, 4.i) ne soit pas géométriquement possible.
  7. Machine à piston selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    la première région d'inversion (5) peut être connectée à la première ouverture de commande (2) au moyen du dispositif de soupape (10).
  8. Machine à piston selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce
    qu'une deuxième connexion (12) de l'élément accumulateur (7) est prévue, laquelle débouche dans la deuxième région d'inversion (6) et en ce que la deuxième connexion (12) présente un deuxième dispositif de soupape (14), par le biais duquel la section transversale d'écoulement de la deuxième connexion (12) peut être variée dans le temps de manière désaccouplée d'un angle de position de l'ouverture de la chambre de piston (4, 4.i) par rapport à la partie de commande (1).
  9. Machine à piston selon la revendication 7,
    caractérisée en ce
    qu'une deuxième embouchure (13) de la deuxième connexion (12) est disposée dans la deuxième région d'inversion (6), de telle sorte qu'elle puisse être connectée au moyen de l'ouverture de chambre de piston (4, 4.i) à la deuxième ouverture de commande (3).
  10. Machine à piston selon la revendication 7 ou 8,
    caractérisée en ce que
    la deuxième embouchure (13) de la deuxième connexion (12) peut être connectée dans la deuxième région d'inversion (6) à la deuxième ouverture de commande (3) par le biais du deuxième dispositif de soupape (14).
  11. Machine à piston selon l'une quelconque des revendications 1 à 9,
    caractérisée en ce que
    la machine à piston hydrostatique est une pompe et la première ouverture de commande (2) est connectée au côté refoulement de la pompe et la deuxième ouverture de commande (3) est connectée au côté aspiration de la pompe, et la première région d'inversion (5) correspond au côté d'augmentation de la pression défini par un sens de déplacement (d) de l'ouverture de la chambre de piston (4, 4.i) par rapport à la partie de commande (1).
EP09777918A 2008-09-08 2009-08-17 Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations Not-in-force EP2324245B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008046258 2008-09-08
DE102008061349A DE102008061349A1 (de) 2008-09-08 2008-12-10 Hydrostatische Kolbenmaschine mit Pulsationsminderungsvorrichtung
PCT/EP2009/005947 WO2010025822A1 (fr) 2008-09-08 2009-08-17 Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations

Publications (2)

Publication Number Publication Date
EP2324245A1 EP2324245A1 (fr) 2011-05-25
EP2324245B1 true EP2324245B1 (fr) 2012-02-29

Family

ID=41650900

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09777918A Not-in-force EP2324245B1 (fr) 2008-09-08 2009-08-17 Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations

Country Status (4)

Country Link
EP (1) EP2324245B1 (fr)
AT (1) ATE547626T1 (fr)
DE (1) DE102008061349A1 (fr)
WO (1) WO2010025822A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105378278A (zh) * 2013-05-22 2016-03-02 贺德克传动中心有限公司 轴向活塞泵
DE102020201800A1 (de) 2020-02-13 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine mit Druckseitenwechsel
DE102020212372A1 (de) 2020-09-30 2022-03-31 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011117081A1 (de) 2011-10-27 2013-05-02 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
WO2013068211A1 (fr) * 2011-11-12 2013-05-16 Robert Bosch Gmbh Machine à piston hydrostatique
WO2013068210A1 (fr) 2011-11-12 2013-05-16 Robert Bosch Gmbh Machine à pistons hydrostatique
FR3000770B1 (fr) * 2013-01-08 2015-03-20 Technoboost Machine hydraulique a deux sens de rotation, comportant une chambre de pre-compression
DE102021203902A1 (de) 2021-04-20 2022-10-20 Robert Bosch Gesellschaft mit beschränkter Haftung Axialkolbenmaschine mit hoher Betriebsdrehzahl und geringer Druckpulsation
DE102022107860A1 (de) 2022-04-01 2023-10-05 Danfoss Power Solutions Inc. Hydraulische Axialkolbeneinheit und Verfahren zum Steuern einer hydraulischen Axialkolbeneinheit

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DE1211943B (de) * 1957-01-18 1966-03-03 Bosch Gmbh Robert Einrichtung zur Geraeuschminderung bei einer als Pumpe oder Motor verwendbaren, drehschiebergesteuerten hydraulischen Axial- oder Radialkolbenmaschine
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 (sv) * 1991-09-06 1998-06-29 Parker Hannifin Ab Förfarande och anordning för dämpning av flödespulsationer vid hydrostatiska hydraulmaskiner av deplacementtyp samt anordning för utövande av förfarandet
JP2606758Y2 (ja) * 1992-12-22 2001-01-09 株式会社小松製作所 油圧ポンプ・モータのシリンダ室内圧力コントロール装置
DE19706116C5 (de) 1997-02-17 2012-12-20 Linde Material Handling Gmbh Vorrichtung zur Pulsationsminderung an hydrostatischen Verdrängereinheiten

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105378278A (zh) * 2013-05-22 2016-03-02 贺德克传动中心有限公司 轴向活塞泵
CN105378278B (zh) * 2013-05-22 2017-12-19 贺德克传动中心有限公司 轴向活塞泵
DE102020201800A1 (de) 2020-02-13 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine mit Druckseitenwechsel
US11603829B2 (en) 2020-02-13 2023-03-14 Robert Bosch Gmbh Hydrostatic axial piston machine having pressure side change
DE102020212372A1 (de) 2020-09-30 2022-03-31 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine

Also Published As

Publication number Publication date
DE102008061349A1 (de) 2010-03-11
WO2010025822A1 (fr) 2010-03-11
EP2324245A1 (fr) 2011-05-25
ATE547626T1 (de) 2012-03-15

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