WO2013060576A1 - Machine à pistons hydrostatique - Google Patents

Machine à pistons hydrostatique Download PDF

Info

Publication number
WO2013060576A1
WO2013060576A1 PCT/EP2012/070103 EP2012070103W WO2013060576A1 WO 2013060576 A1 WO2013060576 A1 WO 2013060576A1 EP 2012070103 W EP2012070103 W EP 2012070103W WO 2013060576 A1 WO2013060576 A1 WO 2013060576A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
piston
opening
control
piston chamber
Prior art date
Application number
PCT/EP2012/070103
Other languages
German (de)
English (en)
Inventor
Andreas Beiter
Ruslan Rudik
Olof Schmitz
Timo Nafz
Lars MANNSDOERFER
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 EP12772109.0A priority Critical patent/EP2771571A1/fr
Priority to CN201280058300.4A priority patent/CN103958893B/zh
Publication of WO2013060576A1 publication Critical patent/WO2013060576A1/fr

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
    • 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
    • F04B2205/08—Pressure difference over a throttle

Definitions

  • the invention relates to a hydrostatic piston machine, in particular an axial piston machine, according to the preamble of patent claim 1.
  • DE 42 29 544 A1 discloses such a piston machine is disclosed, which is an axial piston machine.
  • This has a cylinder shaft arranged on a drive shaft with a plurality of piston chambers in each of which a piston is movably guided.
  • a respective piston chamber can in each case be alternately connected via a control opening introduced at the front side of the cylinder drum to a kidney-shaped low-pressure and high-pressure opening introduced in a control disk.
  • the cylinder drum slides on the front side of the control disk.
  • the low-pressure and high-pressure openings lie on a common pitch circle and are spaced apart in the circumferential direction, whereby two Um Kunststoff Kunststoffe are formed.
  • a respective piston is located in the one of these Um Kunststoff Kunststoffe in the region of its bottom dead center or bottom dead center (BDC) and in the other this Um Kunststoff Kunststoff in the region of its top dead center or Top Dead Center (TDC).
  • the Um Kunststoff Hoch in which a respective piston is in the region of its BDC, opens a channel with a channel mouth, which is connected to a Pre-Compression Volume (PCV).
  • the PCV 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 Tavern Scheme 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 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 is provided with a kidney-shaped low pressure and high pressure opening.
  • a respective Um Kunststoffmaschine Kunststoff between the low-pressure and the high-pressure port opens in each case a channel with a channel mouth.
  • 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 Kunststoffe a respective piston of a cylinder drum of the axial piston engine is in the region of its BDC is connected via a switching valve with the high-pressure port or a PCV.
  • the opening in the other Um Tavern Kunststoff Kunststofftechnik channel is connected via a switching valve with the low-pressure port or the PCV.
  • a respective working space of the cylinder drum is for this purpose when sweeping its control opening over the Um Kunststoff Kunststoff Kunststoff in which a respective ger piston in the area of its TDC is connected via the opening into this Um Kunststoffer Scheme channel and the control valve to the PCV, while the connection between the PCV and the other Um Kunststoffer Scheme is interrupted by the other control valve.
  • the channels thus takes place a gentle Druckauf- and pressure reduction, whereby the noise behavior of the piston engine is improved.
  • a disadvantage of this solution is the device technology extremely complicated design of the piston engine with the large number of pressure fluid channels and the two valves for controlling the PCV.
  • the invention has the object to provide a piston engine that eliminates the disadvantages mentioned.
  • a hydrostatic piston machine in particular an axial piston machine, has a plurality of piston chambers, in each of which a piston capable of executing a stroke movement is arranged.
  • a respective piston chamber is alternately connected via a control opening with a low-pressure and high-pressure opening of a control part, it being possible for the control part to be a control disk.
  • the low-pressure and the high-pressure opening are separated from one another via two reversing regions, which are in particular approximately in the region of a respective dead center position of the piston.
  • a respective mouth is provided, which is connected to a storage element (Pressure Recuperation Volume (PRV)).
  • PRV Pressure Recuperation Volume
  • the orifices, the low-pressure and high-pressure opening and the control openings of the piston chambers are arranged such that the PRV is charged by the piston chamber, which moves in the use of the piston engine from the high-pressure opening to the low-pressure opening, and that the PRV the piston chamber, the from the low-pressure opening to the high-pressure opening moves, recharges.
  • This solution has the advantage that, in contrast to the prior art, no additional valves and a plurality of pressure medium channels for pressure control of the PRV and the piston chambers in the Um Kunststoff Berlin are necessary, whereby such a piston machine is designed device extremely simple and inexpensive.
  • the accumulator is advantageously charged by the piston chamber moving from the high-pressure opening to the low-pressure opening via the reversing area. A pressure energy of this piston chamber then charges the PRV before the pressure of the piston chamber is reduced via the low pressure port. An additional energy for charging the PRV is thus no longer necessary, whereby the piston engine has a comparatively high efficiency.
  • the piston delimits, together with the piston chamber, a dead volume which is significantly less than a storage volume or recuperation volume of the PRV.
  • a dead volume which is significantly less than a storage volume or recuperation volume of the PRV.
  • the storage volume is at least 7.5 times as large as the dead volume.
  • control openings, the low-pressure and high-pressure opening and the orifices are designed such that a respective control port is not connected to a connection of the piston chamber with a respective orifice with the low-pressure and high-pressure opening, whereby a loss energy causing connection between Low pressure or high pressure opening and the PRV is avoided.
  • the PRV is thus only in fluid communication with the piston chambers.
  • the orifices may have different opening cross-sections compared to each other. In this case, they have, for example, a different length circumferential direction with respect to the axis of rotation and / or a different width in radial direction. direction.
  • the orifices and / or the control opening are preferably configured such that when overlapping a maximum possible pressure fluid flow between the PRV and the piston chamber is replaced due to the volume of the PRV and the piston chamber, whereby a maximum energy recovery is possible.
  • the orifices and / or the control orifice are in particular designed such that a respective orifice is connected as early as possible to the piston chamber, after the control orifice is no longer in communication with the low pressure or high pressure orifice.
  • connection between the orifices and the control opening is then separated when the pressure of the storage element and the piston chamber is approximately equal.
  • the orifices seen in the radial direction from a rotational axis of the piston engine, formed outside a maximum outer diameter of the low pressure and / or high pressure opening in the control part, it being assumed that the low-pressure and / or high-pressure opening having a substantially constant outer diameter
  • the control openings of the piston chambers also have an opening section lying outside the outer diameter.
  • the opening portion may in the circumferential direction of the control opening to a Seen, for example, be formed centrally of this axis of rotation and have a U-shape. Furthermore, the opening portion is advantageously much shorter in the circumferential direction of the control opening than the control opening.
  • the orifices may be slit-shaped and extend approximately in a circumferential direction with respect to the axis of rotation.
  • the orifices may be formed in a bearing sleeve of a sliding bearing of a cylinder drum having the piston chambers.
  • a respective piston chamber then has in addition to the control opening an alternately connectable with the orifices further control opening or reversal opening.
  • a respective Um Kunststoffö réelle is introduced in the radial direction in the cylinder drum.
  • FIG. 1 shows a plan view of a control disk of a piston engine according to the invention in accordance with a first exemplary embodiment
  • FIG. 2 is a bottom view of a cylinder drum of the piston engine according to FIG.
  • FIG. 3 shows a schematically represented section of the control disk of the piston engine according to the first exemplary embodiment
  • Figures 4 and 5 are each a simplified diagram with various parameters of the piston engine according to the first embodiment and 6 shows a schematic representation of a piston engine according to a second embodiment.
  • FIG. 1 shows a control part in the form of a control disk 1 is shown in a plan view for explaining the hydrostatic piston engine according to the invention.
  • the piston engine is an axial piston pump.
  • the basic structure of an axial piston pump is well known from the prior art, which is why a complete explanation can be omitted below.
  • the control disk 1 has a kidney-shaped low-pressure opening 2 and a kidney-shaped high-pressure opening 4, which is divided into three essentially identical sections by two webs 6 for the mechanical strength increase.
  • the low-pressure and high-pressure ports 2 and 4 extend in sections along a common circle.
  • the control disk 1 is designed annular and has a circular recess 8 centrally through which a drive shaft of the axial piston pump can be performed.
  • the low pressure port 2 is connected to a low pressure port and the high pressure port 4 is connected to a high pressure port of the axial piston pump.
  • a cylinder drum 10 of the axial piston pump is shown in a bottom view. This slides in the operation of the axial piston pump with its end face 12 on a sliding surface 14 of the control disk 1 of Figure 1.
  • the end face 12 open a plurality of control openings 16, which are each designed kidney-shaped and extending along a common circle in sections.
  • a respective control opening 16 is connected to a parallel spaced from the axis of rotation of the cylinder drum 10 introduced piston chamber, not shown, in which a piston is movably guided and limits a working space.
  • control openings 16 in a direction of rotation in the counterclockwise direction in FIG. 1, alternate with the low-pressure opening 2 and the high-pressure opening 4.
  • a lifting movement of the pistons arranged in the cylinder drum 10 takes place in such a way that they are in the region of high pressure. 4, a pressure stroke and a suction stroke in the region of the low-pressure opening 2.
  • Um Kunststoff Kunststoff 20 provided.
  • the Um Kunststoff Schemee lie here in the dead zones of the piston movement.
  • the piston In the first reversing region 18, the piston is in the region of its outer dead center and in the second reversing region 20 in the region of its inner dead center.
  • the first Um Tavern Scheme 18 is therefore the one
  • the piston chamber is filled during the contact of its control opening 16 with the low-pressure opening 2 with pressure medium, wherein the pressure level in the piston chamber approximately coincides with the pressure level of the low-pressure opening 2.
  • pressure medium is displaced from the piston chamber, in which case the pressure level in the piston chamber corresponds approximately to the pressure level of the high pressure port 4.
  • Um Kunststoff Kunststoffmaschinefeld Schlue 18 and 20 comes into contact with the low-pressure or high-pressure port 2 or 4, in a respective Um Tavern Anlagen 18 and 20, an orifice 22 and 24 are introduced into the control disk 1.
  • the respective reversing region 18 or 22 is in this case via the respective orifice 22 or 24 and connected via a pressure medium line 26 or 28 directly to a storage element 30.
  • the storage element 30 is here introduced as a recess in a closing plate of the axial piston pump, wherein the recess can be easily produced together with the end plate in the casting process.
  • the orifices 22 and 24 are shown schematically in FIG. 1 and are shown enlarged in FIG. It can be seen in FIG. 3 that the orifices 22 and 24 are slot-shaped and extend in sections along a common circle. In FIG.
  • control openings 16 from FIG. 2 are illustrated schematically next to an end section of the high-pressure opening 4 and two end sections of the low-pressure opening 2.
  • the orifices 22 and 24 are formed outside a maximum outer diameter of the low-pressure and high-pressure ports 2 and 4 in the control disk 1 of Figure 1.
  • control openings 16 have substantially the same width in the radial direction as the low-pressure and high-pressure openings 2, 4 and extend along the same circle as the low-pressure and high-pressure openings 2, 4. So that the control openings 16 and the outlets 22, 24 overlap in FIG. 3 during a rotation of the cylinder drum 10, the control openings 16 additionally have a U-shaped opening cross-section 32, see also FIG. This is formed at a respective control opening 16 in the circumferential direction approximately centrally and extends radially outward. Its length in the circumferential direction is substantially less than the main portion of the control port 16th
  • control port 16 is shown in a position in which it is arranged at a rotation of the cylinder drum 10 in the counterclockwise direction, which is illustrated by the arrow 34, immediately after the low pressure opening 2 and in this case the opening cross section 32 directly from the right outlet 22 is located.
  • the opening cross-section 32 would intersect with the orifice 22.
  • control port 16 which is located immediately after the high-pressure port 4 with its opening cross section 32 in front of the orifice 24.
  • this control opening 16 thus only after the high-pressure opening 4 with the recess 24 in overlap. This overlap ends before the control opening 16 comes into contact with the low-pressure opening 2.
  • the storage element 30 is thus connected to the rotary valve principle with the piston chambers.
  • FIG. 4 is an example based on various parameters
  • FIG. 5 shows by way of example on the basis of the various parameters a shut-off process in which a respective piston chamber passes from the high-pressure opening 4 from FIG. 1 via the reversing region 20 to the low-pressure opening 2, wherein pressure in the piston chamber is reduced in the reversing region and used to charge the storage element 30.
  • a lower curve 36 in FIG. 4 schematically illustrates the contact time between the opening cross-section 32 and the orifice 22 of FIG. 3, where high values of the curve 36 indicate an overlap which occurs approximately in the contact time between 0.08 and 0.08102 ,
  • a curve 38 arranged approximately centrally in FIG. 4 qualitatively shows a delivery flow of a pressure medium which reaches the storage element 30 from the piston chamber via the opening cross section 32 arranged on the right in FIG. 3, the outlet 22 and the pressure medium line 26 from FIG. It can be seen that 0.08 to 0.08102 pressure medium is exchanged only in the contact time, wherein the flow increases sharply at the beginning of the overlap between the control port 16 and the orifice 22 and then slowly decreases. Just before the contact or the overlap between the control port 16 and the orifice 22 ends and the flow is substantially zero.
  • a curve 40 and a curve 42 indicate pressure profiles.
  • the numerical values given on the y-axis and the specified parameter "pressure" only apply to these two curves.
  • the curve 40 shows the pressure curve in the piston chamber over the contact time. At 0.08 seconds, so at the beginning of the overlap between control port 16 and the orifice 22, the pressure in the piston chamber is about zero and then increases to the end of the contact time at 0.08102 seconds to about 1 10 bar. After the contact time, the pressure increases even further, since the control opening 16 intersects with the high-pressure opening 4 from FIG. The pressure then rises in the piston chamber to about 300 bar, which corresponds to the pressure in the high-pressure opening 4.
  • a curve 42 in the diagram in FIG. 4 represents the pressure in the storage element 30 from FIG. 1.
  • the pressure in the storage element 30 amounts to approximately 130 bar before the control orifice 16 is divided by the orifice 22 in FIG.
  • the pressure in the storage element 30 drops slightly, while at the same time the pressure in the piston chamber, see curve 40, rises sharply.
  • the pressures of the piston chamber and the storage element 30 thus equal to each other in the contact time. At the end of the contact time, the pressures are substantially balanced at about 1 10 bar.
  • the pressure drop in the storage element 30 from FIG. 1 is significantly lower than the pressure increase in the piston chamber.
  • a volume of the storage element is significantly larger than a working space bounded by the piston chamber and piston. It has proved to be advantageous if the volume of the storage element 30 is about 7.5 times as large as a dead volume in a respective piston chamber. The storage element 30 is thus not completely discharged in conjunction with a piston chamber to be charged.
  • control openings 16 of the cylinder drum 10 are designed and arranged such that in each case only one control opening 16 with the Um Kunststoff Kunststoff Society 18 or 20 is in contact. This is illustrated by a curve 44 in FIG. 4, which is used as a straight line. the line is drawn. This represents the flow through the orifice 24 on the left in FIG. 3. Since, in the case of an overlap of the right-hand control orifice in FIG. 3 with the orifice 22, there is no overlap of a control orifice 16 with the orifice 24 in FIG zero during contact time.
  • the pressure in the piston chamber see curve 40, is about 300 bar before an overlap with the orifice 24 and then drops approximately during the contact time to 130 bar. After the overlap, the pressure in the piston chamber continues to decrease because the control opening 16 in FIG. 3 overlaps the low-pressure opening 2, whereby pressure in the piston chamber is reduced to the low-pressure opening 2. While the pressure in the piston chamber drops in the contact time, the pressure in the storage element 30, see FIG. 1, increases, which represents the curve 42 in FIG. The pressure increases here, for example from 1 10 bar to 130 bar, whereby the pressures in the piston chamber and in the storage element 30 at the end of the contact time are approximately equal. The storage element 30 is thus filled again with pressure medium from the piston chamber during the contact time, whereby an energy recovery is possible.
  • the pressure medium in the piston chamber thus serves to charge the storage element 30 and does not flow unused to the low-pressure opening 2.
  • an efficiency of the piston engine is comparatively high, since the loss energy arising during the Abêtvorgang is stored by the storage element 30 and is used in the Auf confusevorgang.
  • a contact time of the control opening 16 with the orifice 22 or 24 in Figure 3 can be adjusted by the configuration thereof.
  • a length of the orifice 22 and 24 in the circumferential direction in this case affects the contact time, with a larger Length increases accordingly the contact time.
  • a width of the overlap region or a width of the orifices 22 and 24 in the radial direction and a width of the opening cross section 32 are selected such that in the contact time, the pressures in the piston chamber and in the storage element 30, see Figure 1, substantially equalize.
  • control port 16 and the orifice 22 and 24 are preferably carried out shortly after an overlap between this control port 16 ends with the low-pressure or high-pressure port 2 and 4 respectively.
  • the contact sides are designed such that a maximum possible flow between the piston chamber and storage element 30 can be replaced, resulting in maximum energy recovery.
  • the storage element 30 is thus connected to the rotary valve principle with the piston chambers.
  • FIG. 6 shows, in a schematic view, a piston machine in the form of an axial piston pump according to a second exemplary embodiment.
  • outlets 46 and 48 are not formed in a control disk but in a bearing bush 50 in which a cylindrical drum 52 is slidably mounted.
  • the cylinder drum 52 is fixedly connected to a drive shaft 54 which is mounted in its end portions via pivot bearings 56 and 58 in a machine housing, not shown.
  • a plurality of piston chambers are introduced at a parallel distance from the axis of rotation 60, wherein in the figure 6, an upper piston chamber 62 and a lower piston chamber 64 are shown.
  • a piston is guided in each case movable, wherein in the figure 6, a piston 66 in the piston chamber 62 and a piston 68 in the piston chamber 64 is shown.
  • a respective piston 66 and 68 is pivotally connected on its side facing away from the cylinder drum 52 with a piston foot 70 and 72 via which the piston 66 and 68 slide on a swash plate 74 upon rotation of the cylinder drum 52.
  • the cylinder drum 52 is slidably mounted with its outer circumferential surface 76 in the bearing bush 50.
  • the outer lateral surface 76 of the cylindrical drum 52 and an inner lateral surface 78 of the bearing bush 50 are shown clearly spaced from one another.
  • the upper outlet 46 in FIG. 6 is connected via a pressure medium line 80 to a storage element or PRV 82, and the lower outlet 48 is connected to the PRV 82 via a pressure medium line 84.
  • the orifices 46 and 48 are arranged in a Um Kunststoff Kunststoff the piston engine.
  • the upper opening 46 in FIG. 6 serves to build up a pressure in a piston space between a low-pressure opening and a high-pressure opening, while the lower opening 48 serves to reduce a pressure in a piston space between a high-pressure opening and a low-pressure opening. This is illustrated by arrows 86 and 88, which represent a flow from or to the PRV 82.
  • a flow from the PRV 82 flows to a piston chamber via the upper orifice 46, while a flow from a piston chamber to the PRV 82 flows via the lower orifice 48.
  • a piston chamber with an orifice 46 and 48 is introduced radially into the cylinder drum 52 each have a further control opening or reversing opening to a respective piston chamber.
  • a reversal opening 90 leads to the piston chamber 62 and to a reversing opening 92 to the piston chamber 64 in FIG.
  • FIG. 6 additionally shows the cylindrical drum 52 in a plan view.
  • a multiplicity of circular-cylindrical piston spaces 94 can be seen, to each of which a reversing opening 96 is assigned, which are illustrated by dashed lines.
  • FIG. 6 shows the piston engine, in which the lower piston 68 is arranged approximately in the region of its top dead center (top dead center) and the upper piston 66 in the region of its bottom dead center (bottom dead center).
  • the geometries of the outlets 46, 48 and the Um Kunststoffö Stammen 96 are preferably designed such that the PRV 82 is loaded and unloaded according to the first embodiment.
  • a hydrostatic piston engine in particular an axial piston machine, which has a plurality of piston chambers, in which piston perform a lifting movement.
  • a respective piston chamber is in this case alternately connectable via a control opening in each case with a low-pressure and high-pressure opening.
  • Um Tavern Schemee are provided between the low-pressure and the high-pressure opening, via which a respective piston chamber is moved in the transition between the low-pressure and the high-pressure opening.
  • an orifice is provided, via which a respective piston chamber with a storage element (PRV) when its control port overlaps with one of the orifices during operation of the piston engine.
  • PRV storage element

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne une machine à pistons hydrostatique, en particulier une machine à pistons axiaux, comprenant une pluralité de chambres de pistons dans lesquelles des pistons effectuent un mouvement alternatif. Selon l'invention, chacune des chambres de piston peut être reliée en alternance respectivement à une ouverture basse pression et à une ouverture haute pression par l'intermédiaire d'une ouverture de commande. Entre l'ouverture basse pression et l'ouverture haute pression sont ménagées des zones d'inversion, par l'intermédiaire desquelles chacune des chambres de piston est déplacée dans l'espace de transition entre l'ouverture basse pression et l'ouverture haute pression. Dans chacune des zones d'inversion est ménagé un débouché, par l'intermédiaire duquel chacune des chambres de piston peut être reliée à un élément d'accumulation, en particulier un volume de pré-compression, lorsqu'une ouverture de commande coïncide avec un des débouchés pendant le fonctionnement de la machine à pistons.
PCT/EP2012/070103 2011-10-27 2012-10-11 Machine à pistons hydrostatique WO2013060576A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12772109.0A EP2771571A1 (fr) 2011-10-27 2012-10-11 Machine à pistons hydrostatique
CN201280058300.4A CN103958893B (zh) 2011-10-27 2012-10-11 静液压柱塞机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011117081.6 2011-10-27
DE201110117081 DE102011117081A1 (de) 2011-10-27 2011-10-27 Hydrostatische Kolbenmaschine

Publications (1)

Publication Number Publication Date
WO2013060576A1 true WO2013060576A1 (fr) 2013-05-02

Family

ID=47016712

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/070103 WO2013060576A1 (fr) 2011-10-27 2012-10-11 Machine à pistons hydrostatique

Country Status (4)

Country Link
EP (1) EP2771571A1 (fr)
CN (1) CN103958893B (fr)
DE (1) DE102011117081A1 (fr)
WO (1) WO2013060576A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10371781B2 (en) 2009-05-04 2019-08-06 Schlumberger Technology Corporation Gain-corrected measurements

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6267598B2 (ja) * 2014-08-01 2018-01-24 川崎重工業株式会社 液圧回転機
EP3020968B1 (fr) * 2014-11-14 2016-08-24 Danfoss A/S Machine hydraulique, en particulier un échangeur de pression hydraulique
EP3591224A1 (fr) * 2018-07-05 2020-01-08 Dana Motion Systems Italia S.R.L. Dispositif hydraulique à piston
DE102019213675A1 (de) * 2019-09-10 2021-03-11 Robert Bosch Gmbh Hydrostatische Kolbenmaschineneinheit

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE4229544A1 (de) 1991-09-06 1993-03-11 Voac Hydraulics I Trollhaettan Verfahren und vorrichtung zur daempfung von stroemungspulsationen bei hydrostatischen hydraulikmaschinen des verdraengungstyps
DE4396844C2 (de) * 1992-12-22 1998-05-07 Komatsu Mfg Co Ltd Vorrichtung zur Steuerung von Druck in den Zylinderkammern von hydraulischen Pumpen und Motoren
DE19706116A1 (de) * 1997-02-17 1998-08-20 Linde Ag Vorrichtung zur Pulsationsminderung an hydrostatischen Verdrängereinheiten
DE19818721A1 (de) * 1998-04-27 1999-10-28 Mannesmann Rexroth Ag Hydrostatische Maschine
DE102008061349A1 (de) 2008-09-08 2010-03-11 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit Pulsationsminderungsvorrichtung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3362576B2 (ja) * 1995-02-10 2003-01-07 ダイキン工業株式会社 可変容量形ピストン機械

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE4229544A1 (de) 1991-09-06 1993-03-11 Voac Hydraulics I Trollhaettan Verfahren und vorrichtung zur daempfung von stroemungspulsationen bei hydrostatischen hydraulikmaschinen des verdraengungstyps
DE4396844C2 (de) * 1992-12-22 1998-05-07 Komatsu Mfg Co Ltd Vorrichtung zur Steuerung von Druck in den Zylinderkammern von hydraulischen Pumpen und Motoren
DE19706116A1 (de) * 1997-02-17 1998-08-20 Linde Ag Vorrichtung zur Pulsationsminderung an hydrostatischen Verdrängereinheiten
DE19818721A1 (de) * 1998-04-27 1999-10-28 Mannesmann Rexroth Ag Hydrostatische Maschine
DE102008061349A1 (de) 2008-09-08 2010-03-11 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit Pulsationsminderungsvorrichtung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10371781B2 (en) 2009-05-04 2019-08-06 Schlumberger Technology Corporation Gain-corrected measurements

Also Published As

Publication number Publication date
EP2771571A1 (fr) 2014-09-03
CN103958893B (zh) 2016-09-28
DE102011117081A1 (de) 2013-05-02
CN103958893A (zh) 2014-07-30

Similar Documents

Publication Publication Date Title
DE4138313C2 (de) Radialkolbenpumpe
DE19706114C9 (de) Vorrichtung zur Pulsationsverminderung an einer hydrostatischen Verdrängereinheit
EP2761180B1 (fr) Pompe volumétrique
EP2324245B1 (fr) Machine à piston hydrostatique équipée d'un dispositif de réduction de pulsations
EP2771571A1 (fr) Machine à pistons hydrostatique
DE102010006895A1 (de) Axialkolbenmaschine und Steuerspiegel
DE3042328C2 (de) Kolbenpumpe
DE10209805A1 (de) Elektronische Bohrungsdruckoptimierungseinrichtung
DE102008062483A1 (de) Axialkolbenmaschine mit Pulsationsminderung
WO2013068210A1 (fr) Machine à pistons hydrostatique
EP1672215B1 (fr) Pompe hydraulique à pistons
DE102009021833A1 (de) Hydraulischer Antrieb und Drehschieberventil für einen hydraulischen Antrieb
DE102007007288A1 (de) Antriebsvorrichtung, insbesondere für ein bewegbares Bauteil an einer Kunststoffspritzgieß- oder einer Blasformmaschine
WO2008046544A1 (fr) Machine hydraulique de travail
EP0509077B1 (fr) Pompe a pistons, notamment pompe a pistons radiaux
DE1211943B (de) Einrichtung zur Geraeuschminderung bei einer als Pumpe oder Motor verwendbaren, drehschiebergesteuerten hydraulischen Axial- oder Radialkolbenmaschine
DE102012009794A1 (de) Hydrostatische Radialkolbenmaschine und Kolben für eine hydrostatische Radialkolbenmaschine
WO2012168083A2 (fr) Machine à piston axial dans un mode de construction à disque incliné
DE19804374B4 (de) Axialkolbenmaschine mit Mitteldrucköffnung
WO2013068211A1 (fr) Machine à piston hydrostatique
DE102017222354A1 (de) Hydrostatische Kolbenmaschine
DE102006044294B3 (de) Radialkolbenpumpe
DE3627375C2 (fr)
DE102020212630A1 (de) Hydrostatische Axialkolbenmaschine
EP2776713B1 (fr) Machine à pistons hydrostatique

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12772109

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2012772109

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2012772109

Country of ref document: EP