WO2010025822A1 - 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
WO2010025822A1
WO2010025822A1 PCT/EP2009/005947 EP2009005947W WO2010025822A1 WO 2010025822 A1 WO2010025822 A1 WO 2010025822A1 EP 2009005947 W EP2009005947 W EP 2009005947W WO 2010025822 A1 WO2010025822 A1 WO 2010025822A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston chamber
piston
connection
pressure
umsteuerbereich
Prior art date
Application number
PCT/EP2009/005947
Other languages
German (de)
English (en)
Inventor
Timo Nafz
Ruslan Rudik
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to AT09777918T priority Critical patent/ATE547626T1/de
Priority to EP09777918A priority patent/EP2324245B1/fr
Publication of WO2010025822A1 publication Critical patent/WO2010025822A1/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 functionality at the pump outlet.
  • a pressure difference must be overcome in the transition from the suction side to the pressure side.
  • Um Kunststoff 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 too
  • Piston space opening is given to the control part and further as long as the pressure in the storage element is higher than in the piston chamber.
  • the pressure in the piston increases again due to a stroke movement of the piston Piston chamber, so closes the check valve.
  • a non-return valve bypass line section or a separate line is provided, which is permanently connected to the storage element.
  • 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 Colour is formed.
  • the hydrostatic piston machine also has a
  • connection which is connectable via a connection which opens into the first Um Kunststoff Kunststoff Scheme with the piston chamber opening.
  • the connection has a valve device.
  • 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.
  • Pulsation reduction device optimally adapted to the respective operating condition of the machine.
  • Memory element and thus the precompression of the pressure medium in the piston chamber can thus be controlled in time.
  • the valve device comprises at least one solenoid-operated valve.
  • Such 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 and a corresponding control signal for timing the operation of the solenoid-operated valve can be derived.
  • 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.
  • 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 loading or unloading 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.
  • 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 rotation for example, the cylinder drum a
  • Axial piston machine is thus after raising the pressure in the piston chamber by supplying pressure medium from the storage element through the piston chamber opening a
  • 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. 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.
  • 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 Anlagen.
  • a second connection of the memory element which opens into the second Um Kunststoff Kunststoff Kunststoff.
  • This second connection has a second valve device.
  • 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 an adaptation of the relaxation of the piston chamber on the
  • 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.
  • FIG. 1 shows an embodiment of a valve-supported pulsation reduction device of a hydrostatic piston engine.
  • FIG. 2 shows a second embodiment with a valve-controlled PulsationsminderungsVorraum.
  • Fig. 3 shows a third embodiment, which also operates valve-controlled and uses a stroke-limited switching valve
  • Fig. 4 shows a fourth embodiment with two
  • Fig. 5 shows an exemplary course of
  • Fig. 6 is a first time of a fifth
  • FIG. 7 shows a second time of the arrangement of FIG. 6;
  • FIG. 8 shows a third time of the arrangement according to FIG. 6; FIG. and
  • FIG. 9 shows a modified embodiment of FIG. 6 with a further storage element which can be charged via the high-pressure side.
  • 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.
  • FIG. 1 is a plan view of a to explain the hydrostatic piston machine according to the invention with Pulsationsminderungsvorraum
  • 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 by way of example, which connects an end face 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, which is indicated in Fig. 1 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, can be stored in the pressure medium under high pressure.
  • the memory element 7 is connected via a connection 8 with the first Um Kunststoff Scheme 5.
  • the compound 8 opens at an orifice 9 in the first Um Kunststoff Scheme 5 so that at a
  • 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 Kunststoff 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.
  • the piston chamber opening 4 assumes 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.
  • FIG. 1 A second embodiment, which is valve-controlled in contrast to the only valve-supported embodiment of FIG. 1, is shown in FIG.
  • 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 known from FIG. 1 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 Grill Scheme 6 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.
  • FIG. 1 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 known from FIG. 1 switching valve.
  • a corresponding second valve is now also arranged in the second connecting line section 8.
  • 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 piston space opening (not shown in FIG. 2) is in contact with the outlet 9, the first valve 10. 1 is opened again.
  • the flow cross sections are via the first connecting line section 10.1 or the second
  • 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 shown in FIG. 3.
  • the connection is 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.
  • Connecting line section 18.2 causes. 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 Scheme so that a larger angular position range can be used in a rotation of the cylinder drum. If the piston chamber opening 4 is located in the outer dead center labeled AT, then the first valve 10.1 is opened for the unloading process.
  • 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.
  • 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 set so that the entire Vorkompressionsvorgang, ie the discharge of pressure medium from the storage element 7 into the piston chamber and the subsequent precompression by the piston stroke a
  • Outlet opening 9.2 does not open in the first Um Kunststoffmaschine Scheme 5, but directly in the high-pressure kidney 2. This is particularly advantageous in combination with the additional notch. Occurs the piston chamber opening 4 by a further rotation of the cylinder drum in contact with the
  • the second valve 10.2 is opened and the charging 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.
  • 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.
  • 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 by the
  • Piston stroke are taken into account, so that between the closing of the first valve 10.1 and the opening of the second valve 10.2 and a time sequence shown by the timing shown in FIG. 5 may occur.
  • Figs. 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.
  • Valve device 10 initially unchanged in its rest position shown in FIG. After another piston chamber opening 4.3 has passed the outer dead center AT and comes into contact with the orifice 9 in the first Um Kunststoff Kunststoff Kunststoff Kunststoff 5, the valve device 10 is actuated and made a connection between the storage element 7 and the orifice 9. As a result, 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. At this time, a connection of the storage element 7 with the second orifice 13 is not given because the second valve device 14 is in the switching position shown in FIG. 7. 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 shown in FIG. 7.
  • FIG. 8 shows 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.
  • Pulsation reduction device of Fig. 6 to 8 is shown in FIG. 9.
  • the valve device 10 now comprises the switching valve 10. I 1 , which corresponds to the intended for the discharge of the first valve 10.1 of FIGS. 2 and 4.
  • 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 charging cycle of the second memory 17 is extended and equalization of the pressure in the high pressure region of the axial piston machine is achieved.
  • the embodiment of FIG. 9 corresponds to that already described with reference to FIGS. 6 to 8.
  • the efficiency of the piston engine does not charge the storage element 7 to the level of the high-pressure side.
  • the pressure level achievable by the pre-compression discharge process is lower than in the embodiments of Figs. 1-4. In the example of 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)

Abstract

L'invention concerne une machine à piston hydrostatique dotée d'au moins une chambre de piston. Un piston est disposé de façon coulissante dans la chambre de piston, cette chambre pouvant être reliée en alternance à une première ouverture de commande (2) ou une seconde ouverture de commande (3) d'un élément de commande (1) via une ouverture de chambre de piston (4). Une première et une seconde zone d'inversion (5, 6) sont réalisées entre la première ouverture de commande (2) et la seconde ouverture de commande (3). L'ouverture de chambre de piston (4) peut être reliée à un élément d'accumulation (7), qui débouche dans la première zone d'inversion (5) par l'intermédiaire d'un élément de raccordement (8). L'élément de raccordement situé entre la zone d'inversion (5) et l'élément d'accumulation (7) comporte un système de vanne (10). Le système de vanne (10) permet de faire varier dans le temps la section d'écoulement de l'élément de raccordement (8) de manière dissociée par rapport à la variation d'un angle (α) définissant la position de l'ouverture de chambre de piston (4) par rapport à l'élément de commande (1).
PCT/EP2009/005947 2008-09-08 2009-08-17 Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations WO2010025822A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AT09777918T ATE547626T1 (de) 2008-09-08 2009-08-17 Hydrostatische kolbenmaschine mit pulsationsminderungsvorrichtung
EP09777918A EP2324245B1 (fr) 2008-09-08 2009-08-17 Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102008046258.6 2008-09-08
DE102008046258 2008-09-08
DE102008061349.5 2008-12-10
DE102008061349A DE102008061349A1 (de) 2008-09-08 2008-12-10 Hydrostatische Kolbenmaschine mit Pulsationsminderungsvorrichtung

Publications (1)

Publication Number Publication Date
WO2010025822A1 true WO2010025822A1 (fr) 2010-03-11

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ID=41650900

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Application Number Title Priority Date Filing Date
PCT/EP2009/005947 WO2010025822A1 (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 (1)

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US20210254609A1 (en) * 2020-02-13 2021-08-19 Robert Bosch Gmbh Hydrostatic Axial Piston Machine Having Pressure Side Change

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Publication number Priority date Publication date Assignee Title
DE102011117081A1 (de) * 2011-10-27 2013-05-02 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
DE102012218883A1 (de) * 2011-11-12 2013-05-16 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
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
EP2999885B1 (fr) * 2013-05-22 2017-12-06 Hydac Drive Center GmbH Machine à piston axial du type à plateau en biais
DE102020212372A1 (de) 2020-09-30 2022-03-31 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine
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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US4540345A (en) * 1982-06-03 1985-09-10 Ifield Engineering Pty. Limited Precompression valve for hydraulic pumps
DE4229544A1 (de) * 1991-09-06 1993-03-11 Voac Hydraulics I Trollhaettan Verfahren und vorrichtung zur daempfung von stroemungspulsationen bei hydrostatischen hydraulikmaschinen des verdraengungstyps
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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
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210254609A1 (en) * 2020-02-13 2021-08-19 Robert Bosch Gmbh Hydrostatic Axial Piston Machine Having Pressure Side Change
US11603829B2 (en) * 2020-02-13 2023-03-14 Robert Bosch Gmbh Hydrostatic axial piston machine having pressure side change

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EP2324245A1 (fr) 2011-05-25
EP2324245B1 (fr) 2012-02-29
ATE547626T1 (de) 2012-03-15

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