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WO2013068210A1 - Machine à pistons hydrostatique - Google Patents

Machine à pistons hydrostatique Download PDF

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Publication number
WO2013068210A1
WO2013068210A1 PCT/EP2012/070529 EP2012070529W WO2013068210A1 WO 2013068210 A1 WO2013068210 A1 WO 2013068210A1 EP 2012070529 W EP2012070529 W EP 2012070529W WO 2013068210 A1 WO2013068210 A1 WO 2013068210A1
Authority
WO
WIPO (PCT)
Prior art keywords
control
pressure
piston engine
section
fluid
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.)
Ceased
Application number
PCT/EP2012/070529
Other languages
German (de)
English (en)
Inventor
Andrea HELLSTERN
Rudolf Appel
Peter Roos
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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 CN201290000972.5U priority Critical patent/CN204283776U/zh
Publication of WO2013068210A1 publication Critical patent/WO2013068210A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • 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

Definitions

  • the invention relates to a hydrostatic piston machine, in particular an axial piston machine, according to the preamble of patent claim 1.
  • a hydrostatic piston machine has a rotating cylinder part with a plurality of cylinder chambers, in which a stroke movement piston are arranged in operation.
  • each cylinder space is alternately connected via a cylinder space opening to a low pressure control port and a high pressure control port on a control surface of a stationary control part at which there are two Um Kunststoffe between the low pressure control port and the high pressure control within which a piston reverses its direction of movement in a dead center.
  • Such an axial piston machine is disclosed, for example, in DE 42 29 544 C2.
  • This has as a cylinder part arranged on a drive shaft cylinder drum with a plurality of cylinder chambers, in each of which a piston is movably guided.
  • Each cylinder space can be alternately connected to a cylinder-shaped opening introduced on the front side of the cylinder drum with a kidney-shaped low-pressure control opening and high-pressure control opening provided in a control disk serving as a control part.
  • the cylinder drum slides along the face of the control disk.
  • the low-pressure control opening and the high-pressure opening lie on a common pitch circle and are spaced apart in the circumferential direction, whereby two Um Kunststoffmaschinee are formed.
  • a respective piston is located in one Um Kunststoff Kunststoff in the region of its internal dead center or Bottom Dead Center (BDC), in which it is immersed furthest into its cylinder chamber, and in the other Um Kunststoffe in the area nes outer dead center or Top Dead Center (TDC), in which it protrudes furthest out of his cylinder room.
  • BDC Bottom Dead Center
  • TDC Top Dead Center
  • an outlet opens into a channel which is connected to a pre-compression volume (PCV) in the reversing region in which a respective piston is located in the region of its BDC.
  • PCV pre-compression volume
  • the PCV in turn, is connected to the high pressure port via a spool valve and throttle, allowing the PCV to be supplied with high pressure and slowly charging via the throttle when the spool valve is open.
  • the channel in the Um Kunststoff Kunststoff Kunststoff opens seen in the radial direction outside the maximum diameter of the low pressure and high pressure opening.
  • the control opening of a respective piston chamber has an opening portion which is also outside the maximum diameter of the low-pressure and high-pressure opening, so that the control port may overlap with the channel.
  • the cylinder chamber opening of a respective cylinder chamber passes over the Um Kunststoff Kunststoff having the channel mouth, whereby a cylinder space and the piston limited work space is connected via the channel with the memory during a certain contact time and a pressure in the working chamber to the pressure of the PCV quickly approaches while the PCV is slowly charged at high pressure through the throttled and valve-controlled connection to the high-pressure port.
  • the working space is thus filled prior to connection to the high-pressure opening with pressure medium under a certain pressure, which leads to a reduction of pressure medium pulsations of the piston engine.
  • a channel communicating with a storage volume or a fluid capacity opens close to the high-pressure control opening into the reversing area.
  • the cylinder chamber openings have a special contour. This causes the orifice to be fully exposed to the cylinder space opening as soon as the cylinder space opening has exited the low pressure control port and high pressure pressurized fluid quickly the storage volume is discharged into the cylinder chamber. Thereafter, the mouth of the channel is closed again. Subsequently, the outlet is again increasingly exposed to bring the storage volume back to high pressure.
  • a cavity which is filled or to be filled with a liquid pressure medium, for example hydraulic oil, and in which a pressure change is due solely to the compressibility of the pressure medium connected to an inflow or outflow of pressure medium.
  • a liquid pressure medium for example hydraulic oil
  • the document DE 10 2008 061 349 A1 shows a further embodiment of a piston engine in the form of an axial piston machine.
  • a control disk with a kidney-shaped low-pressure and high-pressure control opening is likewise provided.
  • a respective Um Kunststoff Kunststoff Kunststoff between the low-pressure and the Hoch Kunststoffsteuoffo réelle each opens a channel with a channel mouth.
  • the channel which opens into the Um Kunststoff Anlagen, in which a respective piston of a cylinder drum of the axial piston machine is in the region of its BDC, via a switching valve to the high-pressure port or a PCV connectable.
  • the opening in the other Um Tavern Scheme channel is connected via a switching valve with the low-pressure port or the PCV.
  • a hydrostatic axial piston machine is known in swash plate design, which is adjustable from a positive displacement volume over zero displacement volume to a negative displacement volume and which can work in four-quadrant operation, ie in both directions both as a pump and as a motor.
  • a storage element is provided which is connected via a non-return valve blocking it and a throttle arranged parallel to the check valve with an orifice in Um Kunststoff Kunststoff a control plate. The term is at a certain mode of operation of the known
  • the storage element is first charged via the throttle under pressure reduction in the cylinder chamber and discharges when the cylinder chamber with low pressure comes in contact.
  • the invention has for its object to provide a hydrostatic piston engine, which is intended to operate in an application in the form of a hydraulic pump and hydromotor in an open hydraulic circuit in particular and this is adjustable over zero displacement and the reversal is improved in terms of function.
  • a hydrostatic piston engine in particular an axial piston engine, has a rotating cylinder part with a plurality of cylinder chambers in which NEN operating a lifting movement exporting pistons are arranged.
  • Each cylinder space is in operation via a cylinder chamber opening alternately connectable to a Niederbuch Kunststoffo réelle and a Hochbuch Kunststoffo réelle on a control surface of a stationary control part at which there are two Um Tavernriose between the Niederbuch Kunststoff- opening and Hoch foundedsteuoffo réelle within which a piston in a dead center reverses its direction of movement ,
  • an opening is provided in a changeover area, which sweeps over the cylinder space openings at least approximately over their entire length.
  • a fluid capacity of defined size to which the orifice is connected via a throttled fluid connection.
  • the fluid capacity is used in particular in addition to a functional base reversal, in particular in addition to a pilot control groove.
  • Damper nozzles may occur.
  • a direct, loss-free pulsation reduction takes place at the signal delivery point of the fluid piston machine. It is possible a higher Verstelldynamik. Because of lower damping losses due to the design according to the invention, an improvement in the efficiency of the unit in control mode is possible with hydraulic controllers. The operating behavior of the piston engine is thus improved.
  • the inventive design is possible in a simple manner with existing reversals.
  • a reversal according to the invention has a large usable functional area. The fluid capacity is used in particular for the reversal of high pressure to low pressure, wherein the Hochbuchberichteong and the Niederbuchbericht are fixed (constant high pressure side and constant low pressure side or tank side).
  • the orifice of the fluid connection is positioned closer to the low pressure control port than to the high pressure control port of the control member. Then, in particular in an open hydraulic circuit and at low low pressure, the suction behavior in pump operation is improved.
  • a significantly lower pulsation in the low-pressure region of the system within which the piston engine is used is realized.
  • the outlet of the throttled connection can also be positioned closer to the high-pressure control opening than to the low-pressure control opening of the control part.
  • the pressure in the storage volume (in the fluid capacity) reaches the high pressure level and does not drop to low pressure during operation.
  • the throttle effect of the fluid connection is independent of the flow direction of the fluid. It is particularly advantageous if at least one control opening extends from a pilot control groove into at least one reversing area. The fluid capacity with appropriate outlet is then available in addition to a functional Basisum penetrateung. The orifice may be located laterally next to the pilot control groove in the control surface.
  • such a positioning of the orifice in the pilot control groove and such a throttle cross section of the fluid connection are selected such that the throttle cross section of the fluid connection is greater than the cross section of the pilot groove in the region of the orifice and the pilot groove toward the control orifice still has a cross section which is substantially larger than the throttle cross section of the fluid connection is, and to its outlet still has a cross-section which is substantially smaller than the throttle cross section of the fluid connection.
  • the cross-sectional ratios are obtained simply by positioning the outlet of the fluid connection in the pilot groove so that the pilot groove extends from the orifice over a greater distance, preferably over about two thirds of its total length toward the control port and over a smaller distance extends to its end.
  • the pilot control groove, in which the opening of the fluid connection to the fluid capacity is positioned, preferably starts from the high pressure control port.
  • Um Kunststoffeschen be arranged. If the fluid connection between the throttle cross section and the fluid capacity has a cross section which is at least eight times greater than the throttle cross section, the length of the connecting line to the storage volume (to the fluid capacity) can be up to ten times the hydraulic diameter of the connecting line. If the cross section of the connecting line is even twenty times the throttle cross-section, then the length of the connecting line to the storage volume can be extended almost without any impairment to the function.
  • the filling volume of the connecting line is in each case attributable to the storage volume.
  • the fluid capacity can now also be formed in a separate capacity housing.
  • two fluid capacities can also be formed in the capacity housing, of which one is used for the reversal of low pressure to high pressure and one for the reversal of high pressure to low pressure. It is still possible direct integration into a free space of the housing of the displacer unit, but there is a greater choice in terms of placement.
  • FIG. 2 shows the same plan view and the same section as in FIG. 1 with the cylinder drum further rotated
  • FIG. 3 shows the same plan view and the same section as in FIG. 2 with the cylinder drum further rotated
  • FIG. 4 shows the same plan view and the same section as in FIG. 3 with the cylinder drum further rotated
  • FIG. 5 is a plan view of the same Um Walter Surrey the control plate and in a section cylinder drum, control plate and connecting plate of the axial piston according to the invention according to Figure 1, wherein the cylinder drum occupies a certain position relative to a control plate and the axial piston engine is in engine operation,
  • FIG. 6 shows the same plan view and the same section as in FIG. 5 with the cylinder drum further rotated
  • FIG. 7 shows the same plan view and the same section as in FIG. 6 with the cylinder drum further rotated
  • FIG. 8 shows the same plan view and the same section as in FIG. 7 with the cylinder drum further rotated
  • FIG. 9 is a plan view of a reversing area of a control plate and in a Nem section cylinder drum, control plate and connection plate of an inventive axial piston machine according to a second embodiment, wherein the cylinder drum occupies a certain position relative to a control plate and the axial piston machine is in engine operation,
  • FIG. 10 shows the same plan view and the same section as in FIG. 9 with the cylinder drum further rotated
  • FIG. 11 shows the same plan view and the same section as in FIG. 10 with the cylinder drum further rotated
  • FIG. 12 shows the same plan view and the same section as in FIG. 11 with the cylinder drum rotated further
  • FIG. 13 shows in a section control plate and connection plate of an axial piston machine according to the invention according to a third embodiment, in which the mouth of a connecting channel to a storage volume in a pilot groove,
  • FIG. 14 shows a section of the cylinder drum, control plate and connecting plate of the exemplary embodiment according to FIG. 13, wherein the cylinder drum assumes a specific position relative to a control plate and the axial piston machine is in pump operation,
  • FIG. 16 shows the same section as in FIG. 15 with the cylinder drum further rotated
  • FIG. 17 shows the same section as in FIG. 16 with the cylinder drum rotated further
  • FIG. 18 shows a fourth exemplary embodiment in which two storage volumes in FIG a mounted on the outside of the housing of a hydrostatic axial piston machine capacity housing.
  • Such an axial piston machine is usually referred to as being pivotable or adjustable over zero.
  • a Zylindertronnnnel 25 are in each case the same distance from a drum axis and at equal angular intervals from each other several, for example, nine cylinder chambers 26 in the form of cylinder bores in which non-illustrated pistons are longitudinally movably received and at one end of the cylinder drum in elongated, usually curved cylinder space openings 27, which are referred to in the following control slots, open out.
  • the width of the control slots 27 is smaller than the diameter of a cylinder bore.
  • the cylinder drum 25 rests with the end face with the control slots 27 on a serving as a control part control plate 28 and slides in operation on the control board away.
  • the control plate has two kidney-shaped control openings 29 and 30, which are located on the same pitch circle as the control slots 27 and of which present the control port 29 as a high pressure control port in which a high pressure (for example a pressure of 200 bar) is present in operation, and the Control port 30 serves as a low-pressure control opening, in which a low pressure (for example a pressure of less than 5 bar), in particular tank pressure, is present during operation.
  • pilot grooves 33 and pilot grooves 34 are at one end or at both ends of a control port or on the ends of both control openings 29 and 30 pilot grooves 33 and pilot grooves 34 introduced.
  • a pilot control groove 33 is present in the reversing region 31 at the low-pressure opening 30.
  • the low-pressure control opening has a pilot control groove 33 and the high-pressure control opening has a pilot control groove 34 in the reversing region.
  • pilot control groove 34 is provided on the high-pressure control port 29 in a reversing region.
  • the pilot grooves are designed so that their cross-section continuously decreases from a control port.
  • the pilot grooves are triangular notches whose depth and width are linearly reduced from a control port.
  • the control plate 28 is against rotation on a connection plate 40 of the axial piston machine, wherein in the connection plate, a high-pressure channel 41 and a low-pressure channel 42 are formed, which lead from an outer side of the connection plate to the control plate facing end side of the connection plate and at this end face a control openings in the control panel corresponding
  • a hollow space 45 of defined size is provided in the connecting plate 40 in the exemplary embodiment according to FIGS. 1 to 18.
  • hen which forms a fluid capacity or a storage volume and from which passes through a through the connecting plate 40 and the control plate 28 passing bore 46 with an opening 47 in the Um Grill Stud 31.
  • the orifice 47 is located closer to the low-pressure control opening 30 than to the high-pressure control opening 29 and adjacent to the pilot control groove 33. Through the bore 46 there is a throttled connection between the storage volume and the outlet 47 educated.
  • a reversal of the control slots 27 from the high-pressure control opening 29 to the low-pressure control opening 30 takes place in the reversing area 31.
  • the free volume in the cylinder chamber is small because the corresponding piston is close to or in its inner dead center.
  • a control slot 27 has just reached the pilot control groove 33 during pump operation after a delivery stroke of the corresponding piston.
  • the cylinder chamber 26 still prevails the high system pressure.
  • the storage volume 45 there is low pressure.
  • the control slot 27 Upon further rotation of the cylinder drum 25, the control slot 27 passes over the pilot control groove 33 and establishes a connection between the cylinder chamber 26 and the storage volume via the throttle bore 46 at a suitable time (see FIG. 2). Much of the fluid quantity of the pressure reduction in the cylinder chamber 26 now flows not via the pilot control groove 33, but via the throttle bore 46 into the storage volume 45, so that there increases the pressure.
  • the control slot 27 reaches the Niederbuch horro réelle 30 (see Figure 3) and covers this something. In this case, the pressure reduction was completed without the amount of fluid required for the pressure reduction has completely drained into the low pressure port. The pressure in the storage volume is higher at this time than in the Niederbuchbericht 30. The piston finally passes over its inner dead center.
  • a particular advantage of the invention thus lies in the possibility of freely sucking in the operation of the hydrostatic piston machine as a pump, ie without precharging the low-pressure region, to realize significantly higher rotational speeds than in the case of the known piston engine without a suction deficiency , During engine operation, in the exemplary embodiment according to FIGS.
  • the control slot 27 sweeps over the pilot groove 33 in the direction of the low-pressure control opening 30 and establishes a connection between the cylinder chamber 27 and the storage volume 45 at a suitable time via the throttle bore 46 (see FIG. 6). Part of the fluid quantity of the pressure reduction therefore does not flow immediately via the pilot control groove 33, but passes through the throttle bore 46 into the storage volume 45, in which the pressure increases.
  • the opening cross section increases the control slot 27 and the low pressure control port 30 so far that the pressure in the cylinder chamber 26 almost equal to the pressure in the Nieder Kunststoffsteu- erö Anlagen 30 (see Figure 8).
  • the storage volume 45 is connected via the throttle bore 46 and the control slot 27 with the low-pressure control port 30, and the pressure in the storage volume 46 is reduced.
  • the orifice 47 of the throttle bore 46 is located closer to the top than the low-pressure control opening 30 and closer to the pilot control groove 34 of the high-pressure control opening 29 before a dead center.
  • Part of the fluid quantity for the pressure reduction in the cylinder chamber 26 from high pressure to low pressure now does not flow directly between the cylinder chamber 26 and the low pressure control port 30, but is temporarily stored in the storage volume 45 via the throttle bore 46 (see FIGS. 10 and 11).
  • the pressure in the storage volume reaches the high-pressure level and, when the connection between the storage volume and the cylinder space 26 is separated, has not yet dropped to the low-pressure level, ie does not even drop to the low-pressure level during operation (see FIG ).
  • a piston engine according to FIGS. 9 to 13 is also particularly suitable for changing the use of the respective control opening in the control plate as a high-pressure control opening and as a low-pressure control opening, that is to say at a fixed speed High pressure side and fixed low pressure side to work with changing direction of rotation. It is adjustable over zero.
  • a first storage volume is used in a reversing area and a second storage volume is used in the second reversing area, the opening of a throttle bore being positioned before the dead point in the movement of the pistons.
  • one of the two storage volumes is then effective in the reversal of high pressure to low pressure and the other in the reversal of low pressure to high pressure.
  • a particular advantage of this variant of an embodiment is that during operation of the piston engine as a motor and / or as a pump with changing direction and fixed pressure side, a significantly lower volume and / or pressure pulsation in the system over a significantly extended operating range can be realized.
  • the exemplary embodiment according to FIGS. 13 to 17 also has a control plate 28 which can be seen except in FIGS. 14 to 17 with a kidney-shaped high-pressure control opening 29 with a pilot control groove 34 and with a kidney-shaped low-pressure control opening 30 and a connection plate 40 with one High-pressure channel 41 and with a low-pressure channel 42.
  • a cavity 45 of defined size which forms a fluid capacity or a storage volume and from which a through the connection plate 40 and the control plate 28 passing bore 46 with an opening 47 in the
  • Um Kunststoff Kunststoffmaschine 32 goes out. Through the bore 46 a throttled connection between the storage volume and the orifice 47 is formed.
  • the orifice 47 is now located in the pilot control groove 34, which, as in the exemplary embodiments already described, is a triangular groove with a continuously decreasing cross section away from the control opening 29.
  • the position of the orifice in the pilot groove 34 is selected so that the cross section of the pilot groove in the region of the orifice is smaller than the cross section of the throttle bore 46.
  • there is 47 between the mouth and the outgoing end of the pilot control groove 34 is still a longer distance, in which the cross section of the pilot control groove is substantially smaller than the cross section of the throttle bore 46.
  • the control slot 27 of a considered cylinder chamber 26 sweeps the pilot groove from its end remote from the high pressure control port 29 until its leading edge is above the orifice 47 (see FIG. 15). In this way, the pressure build-up in the cylinder chamber 26 begins. In this case, due to the above-described cross-sectional ratios, the amount of fluid required for the pressure build-up is taken from the storage volume 45.
  • control slot 27 continues to sweep the pilot groove 34 to a position where it reaches the high pressure pilot port 29 (see Figure 16).
  • the further pressure buildup proceeds as in a standard reversing, which has only the pilot control groove 34.
  • the hydrostatic axial piston machine according to FIG. 18 has two storage volumes, one for reversing from a high-pressure control opening to a low-pressure control opening and one for reversing from the low-pressure control opening to the high-pressure control opening of a control plate.
  • the two storage volumes are formed in a separate, pressure-resistant, for example, metallic housing 50, which is fastened outside the actual housing of the hydrostatic piston machine to a connection plate 51 which closes a pot-shaped housing part 52 and to which the high-pressure connection and the low-pressure connection (tank connection ) of the piston engine are formed. Only a schematically leading to a storage volume connecting line 53 and a leading to the other storage volume connecting line 54 are indicated.
  • connecting lines continue in the interior of the piston machine up to the Um Kunststoff Kunststoffen on a control plate.
  • a throttle cross section in the connecting line is close or formed directly on the control surface of the control plate.
  • the connecting lines can be at least on a part of their length as sufficiently pressure-resistant
  • connecting lines Be executed hose lines.
  • the connecting lines it is also conceivable to design the connecting lines as tubes for at least part of their length.
  • the length of the connecting line to the storage volume without malfunctioning can be up to ten times to fifteen times the hydraulic diameter of the connecting line.
  • the filling volume of the connecting line is to be added to the storage volume.
  • the length of the connecting line to the storage volume can be extended almost without any impairment of function.
  • the filling volume of the connecting line is to be added to the storage volume.
  • a storage volume can be freely positioned. It is not necessary to install the storage volume directly in or on the connection plate of the hydrostatic piston engine. It may, for example, also be located apart from the piston engine or be integrated into free spaces of a housing part of the piston engine which is closed by the end plate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne une machine à pistons hydrostatique, notamment une machine à pistons axiaux, comportant une partie à cylindres rotative pourvue de plusieurs chambres à cylindres dans lesquelles sont disposés des pistons décrivant un mouvement de course en fonctionnement. En fonctionnement, chaque chambre à cylindres est reliée alternativement au moyen d'une ouverture de chambre à cylindres à une ouverture de commande basse pression et à une ouverture de commande haute pression sur une surface de commande d'un élément de commande au repos sur lequel se trouvent deux zones d'inversion entre l'ouverture de commande basse pression et l'ouverture de commande haute pression, dans lesquelles un piston inverse son sens de déplacement au niveau d'un point mort. L'invention vise à améliorer l'inversion en terme de fonction sur une telle machine à pistons hydrostatique. A cet effet, une zone d'inversion comporte une embouchure au moins approximativement recouverte par les ouvertures de chambres à cylindres sur toute la longueur, un volume fluidique de grandeur définie est prévu et l'embouchure est reliée au volume fluidique au moyen d'une liaison fluidique à étranglement.
PCT/EP2012/070529 2011-11-12 2012-10-17 Machine à pistons hydrostatique Ceased WO2013068210A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201290000972.5U CN204283776U (zh) 2011-11-12 2012-10-17 静液压活塞机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011118400 2011-11-12
DE102011118400.0 2011-11-12

Publications (1)

Publication Number Publication Date
WO2013068210A1 true WO2013068210A1 (fr) 2013-05-16

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CN (1) CN204283776U (fr)
DE (1) DE102012218879A1 (fr)
WO (1) WO2013068210A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223492A1 (de) * 2014-11-18 2016-05-19 Robert Bosch Gmbh Axialkolbenmaschine
DE102017222354A1 (de) * 2017-12-11 2019-06-13 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
DE102018218548A1 (de) * 2018-10-30 2020-04-30 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
DE102019213675A1 (de) * 2019-09-10 2021-03-11 Robert Bosch Gmbh Hydrostatische Kolbenmaschineneinheit
DE102021203902A1 (de) 2021-04-20 2022-10-20 Robert Bosch Gesellschaft mit beschränkter Haftung Axialkolbenmaschine mit hoher Betriebsdrehzahl und geringer Druckpulsation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3700573A1 (de) 1987-01-10 1988-07-21 Bosch Gmbh Robert Kolbenmaschine, insbesondere axial- oder radialkolbenmaschine
DE19706116A1 (de) 1997-02-17 1998-08-20 Linde Ag Vorrichtung zur Pulsationsminderung an hydrostatischen Verdrängereinheiten
DE4229544C2 (de) 1991-09-06 2001-11-22 Parker Hannifin Ab Ulricehamn Verfahren und Vorrichtung zur Dämpfung von Strömungspulsationen bei hydrostatischen Hydraulikmaschinen des Verdrängungstyps
DE102008061349A1 (de) 2008-09-08 2010-03-11 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit Pulsationsminderungsvorrichtung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3700573A1 (de) 1987-01-10 1988-07-21 Bosch Gmbh Robert Kolbenmaschine, insbesondere axial- oder radialkolbenmaschine
DE4229544C2 (de) 1991-09-06 2001-11-22 Parker Hannifin Ab Ulricehamn Verfahren und Vorrichtung zur Dämpfung von Strömungspulsationen bei hydrostatischen Hydraulikmaschinen des Verdrängungstyps
DE19706116A1 (de) 1997-02-17 1998-08-20 Linde Ag Vorrichtung zur Pulsationsminderung an hydrostatischen Verdrängereinheiten
DE102008061349A1 (de) 2008-09-08 2010-03-11 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit Pulsationsminderungsvorrichtung

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Publication number Publication date
DE102012218879A1 (de) 2013-05-16
CN204283776U (zh) 2015-04-22

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