EP1013927A2 - Machine à pistons hydrostatique - Google Patents

Machine à pistons hydrostatique Download PDF

Info

Publication number
EP1013927A2
EP1013927A2 EP99124217A EP99124217A EP1013927A2 EP 1013927 A2 EP1013927 A2 EP 1013927A2 EP 99124217 A EP99124217 A EP 99124217A EP 99124217 A EP99124217 A EP 99124217A EP 1013927 A2 EP1013927 A2 EP 1013927A2
Authority
EP
European Patent Office
Prior art keywords
housing
piston machine
wall
machine according
piston
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.)
Granted
Application number
EP99124217A
Other languages
German (de)
English (en)
Other versions
EP1013927A3 (fr
EP1013927B1 (fr
Inventor
Josef Beck
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1013927A2 publication Critical patent/EP1013927A2/fr
Publication of EP1013927A3 publication Critical patent/EP1013927A3/fr
Application granted granted Critical
Publication of EP1013927B1 publication Critical patent/EP1013927B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F04B11/0033—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a mechanical 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
    • F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure
    • 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
    • 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
    • F04B1/2064—Housings

Definitions

  • the invention relates to a hydrostatic Piston machine according to the preamble of claim 1.
  • a Pressure increase in the interior of the housing can also be caused by a Expansion of the hydraulic fluid when heated are caused.
  • DE-AS 1 951 234 shows a hydrostatic one in FIG Transmission described with a pump and a motor, wherein to the interior of one of the two machines a connecting line a surge tank is connected, which is located outside the housing and through the connecting line with the housing interior is connected, which penetrates the casing wall of the housing.
  • the fluid in the transmission expands due to heating off, the increase in volume is achieved by squeezing a Gas cushion added in the expansion tank.
  • the invention has for its object a Piston machine of the type specified above design that while ensuring a small Construction harmful pressure increases can be avoided.
  • Damping device arranged in the housing so that it from is unassailable from the outside and therefore neither by knocks or the like can be damaged, manipulated on it can be. It is also the possibility of one Leaking in the area of the damping device locked out.
  • the configuration according to the invention to none Enlargement of the construction leads.
  • the Design according to the invention by a simple and inexpensive to build, because it is only needs an elastically resilient wall part, which at a Pressure increase above a certain pressure value after yields on the outside and thereby the volume of the interior of the housing enlarged and with a subsequent pressure drop returns elastically to its starting position.
  • the wall part on the inside the housing wall or arranged in its inner region his. This can create an existing housing interior area be used for the arrangement of the damping device, without requiring a special arrangement space or the Piston machine is enlarged.
  • the elastic flexibility of the wall part can thereby be realized that the wall part as a separate component in Sense of a piston in a receiving room guided against one elastic restoring force is arranged movably.
  • the intake space behind the wall part be vented or be ventilated.
  • a ventilation or ventilation can, for. B. to the outside through a the housing wall penetrating channel.
  • An advantageous arrangement for the wall part is the wall of the Housing on which a so-called control disc is mounted, which is most of the designs Front wall or closure wall of a pot-shaped housing acts, and in the suction channel and the pressure channel are arranged.
  • the receiving space of the wall part for Suction channel vented or vented from this is required it with a piston engine that is set up so that the input and output can optionally be determined, two damping devices according to the invention on each Side, each with the damping device, the purpose Venting and ventilation with each as a suction channel functioning line is connected automatically Function occurs while the other damping device automatically by the working or discharge pressure Function is set.
  • FIG. 1 it is an example of such in Swashplate design, consisting of a housing 1, one Input or output shaft 2, a cylinder block or one Cylinder drum 3, a z. B. screwed housing cover 4 with a control disk 5 arranged on the inside thereof, a swash plate 6 and several pistons 7 in Cylinder bores 8 of the cylinder drum are thereby movable are that they are on sliding shoes 9 on the swash plate 6th support.
  • the inclination of the swash plate 6 can by an adjusting device 10 to be described enlarged or be reduced, which increases the displacement of the Piston 7 and the throughput volume of the machine accordingly can change.
  • the axial piston machine is so far from usual design and function, so that it is closer Description does not need.
  • the pistons 7 are in the embodiment shown Hollow piston, consisting of a piston shaft 11 with pressure-effective hollow cylindrical piston face 12.
  • the Piston shaft 11 has a cylindrical outer surface, which on the hollow cylindrical wall 13 of the associated bore 8 slides.
  • the piston skirt 11 in the embodiment of FIG. 1 by means of a tapered piston neck 14 into a spherical Piston head 15, which in the associated slide 9th is pivotally mounted on all sides.
  • the shoe 9 can Receiving the piston head 15 have a recess 16, which is open on the side facing the piston 15 and has a hemispherical recess base on which the Front side of the ball head 15 abuts.
  • the sliding shoe 9 engages over the equator 17 of the recess 16 and engages behind with little movement play the ball head 15 with a Edge region of the peripheral wall 18 surrounding the recess 16, which can basically be hollow cylindrical and the Surrounding recess 16 in the region of its opening. So far The joint connection described is generally 19 designated.
  • the Adjustment device 10 for adjusting the throughput volume the axial piston machine by one or the present Embodiment two diametrically opposite each other opposite hydraulic cylinders 10a, 10b with pistons 10c, 10d formed, each also by a Sliding shoe 9 and an articulation 19 on the Swashplate 6 are supported, but is in these Articulated connections 19 of the ball head 15 part of a Bolt shaft 20, with which it is preferably in one piece molded ball head 15 in a hole of the swash plate 6 is used firmly and is therefore stored.
  • the articulation 19 regarding the position of the piston head 15 and the Recess 16 may be reversed so that the Piston head 15 on the shoe 9 and the recess 16 with the Edge area 18 on the pin shaft 20 or piston shaft 11 is arranged.
  • both cylinders 10a, 10b or only one cylinder can be actuated hydraulically, while the other cylinder is a guide cylinder for one Return spring device with a compression spring 10g can be and optionally also hydraulically can be acted upon.
  • the cylinder 10a is hydraulic acted upon, it is fixed in the housing cover 4 screwed-in and thus immovable piston 10c, to which the cylinder housing 10e is longitudinally displaceable and on the swash plate 6 is supported as described above.
  • an axial channel 10f is provided which connects to a Pressure line or control pressure line is connected.
  • the diameter D of Piston 10c dimensioned larger than the diameter d of Piston 10d.
  • the axial piston machine is one in FIGS. 2 and 3 Damping device 21 shown for the Functional operation in the interior of the housing 1a, which with the hydraulic fluid is filled.
  • the Damping device 21 is in the housing 1, preferably with respect to the housing wall surrounding the housing interior 1a 1b arranged inside.
  • the damping device 21 be arranged on the inside of the housing wall 1b and in protrude the free housing interior 1a or at least be partially sunk inside the housing wall 1b.
  • the damping device 21 has a wall part 22, whose inner surface 22a is a part of the housing interior 1a limiting housing inner surface 1c, and that to the outside is resilient.
  • the wall part is 22 a separate component that in a receiving space 23 in the Housing wall 1b is at least partially sunk.
  • the receiving space 23 is preferably dimensioned deeper, see the depth t, as the associated depth t1 of the wall part 22, so that the preferably formed by a bore Receiving space 23 form a guide 24 for the wall part 22 in which there is little movement in the Recording space 23 is movable into it.
  • the aforementioned elastic flexibility of the wall part 22 can be achieved by a Be generated spring force that the wall part 22 in one of the Receiving space 23 moved out starting position acted upon, in which the movement of the wall part 22 in Direction of the housing interior 1a through a stop 26 is limited.
  • the spring force can e.g. B.
  • This spring force is like that large that when the housing pressure is one certain operating pressure value, which is due to the Inner surface 22a of the wall part 22 effective compressive force
  • the wall part 22 yields, here the wall part 22 in moved the receiving space 23 into it.
  • Housing interior 1a by the size of a storage space increases, in which the pressure in the housing interior 1a can relax.
  • the hydraulic fluid is a liquid acts and the compressibility of liquids low a small storage space is sufficient, i.e. H. a slight compliance of the wall part 22, from a substantial pressure increase in the interior of the housing 1a avoid.
  • This will cause harmful pressure increases or Avoided pressure peaks that are particularly harmful are when they suddenly appear and suddenly the parts load the axial piston machine, e.g. B. the housing 1 in total or a sealing ring 27, in particular a Lip sealing ring, which the input or output shaft 2 or Seals drive shaft with respect to the associated housing wall and in the area of a round hole 28 in the housing wall sits through which the drive shaft 2 extends outwards.
  • a Pressure increase in the interior of the housing 1a may only be as large as it is predetermined by the restoring force of the wall part 22 is because this is at a certain operating pressure value yielding pressure increases and therefore a pressure increase beyond this value is not can impact.
  • the pressure value at which the damping device 21 in Function should occur, and about this pressure value should dampen additional pressure increases, by the Elasticity of resilience, here the preload the spring 25, can be selected or determined.
  • the causes of the pressure value Pressure increases in an existing axial piston machine can be of different types. If the Housing interior 1a with a leakage fluid drainage system or with the return line of the axial piston machine is connected, then can be in functional mode due to of backflow accumulation result in different pressure values that under heavy loads on the axial piston machine, especially when their throughput volume is adjustable is and in particular abruptly adjusted, for. B. enlarged or is reduced to abnormal pressure increases come that are limited by the damping device 21 become. In the present exemplary embodiment, this results in when the drive pulley 6 swings back or in, a Pressure increase due to the different Cross-sectional sizes of the pistons 10c, 10d. The in Functional pressure increases or peaks are limited to about 2 to 3 bar.
  • the receiving space 23 through a guide bushing 29 with a circular cross section formed in a recess 31 in the housing wall 1b is used and in which the wall part 22 as a disc or Piston or as a cup-shaped body with little Movement play slidably guided and by between the recess base 32 and the wall part 22 clamped Compression spring 25 is biased against the stop 26, the by an angular indented edge 33 of the Guide bushing 29 can be formed.
  • the embodiment has the recess 23 Housing wall 1b formed by the housing cover 4, the Damping device 21 arranged next to the control disc 5 is, preferably within an annular seal 30 in the Housing joint.
  • the guide bush 29 can partially or be completely recessed in the housing wall 1b, for which the depth t1 of the recess 31 increases accordingly is measured. If the guide bush 29 in radial Direction is positioned so that it from the jacket wall 1d of the housing 1 is partially covered, then this at the same time created a fuse that the guide bush 29 prevents it from migrating out of the recess 31. At such a configuration, the guide bushing 29 in the recess 31 sit with a little movement sit easily displaceable, which makes assembly easier is. If, however, there is no overlap of the guide bush 29 a different backup is required Guide bushing 29 in the recess 31, for. B. by a Press fit, which is achieved by pressing the guide bush into the Recess 31 can be created. In the present Embodiment, the recess 31 extends partially in Housing cover 4 and partially in the jacket wall 1d of the pot-shaped housing part.
  • the damping device 21 works both when the receiving space 23 is closed as even if it is vented or ventilated, e.g. B. by a channel penetrating the housing wall 1b to the outside (not shown). If the receiving space 23 is tight is closed, then builds up when moving the wall part 22 in the receiving space 23 an increased pressure therein, wherein the damping device 21 is functional as long remains until the increased pressure in the receiving space 23 Pressure increase in the interior of the housing corresponds to 1a. If on the other hand, the receiving space 23 is vented or ventilated, does not build up when the wall part 22 is moved in Pressure in the receiving space 23, so that there is a larger Storage space can be achieved.
  • Connection channels 35, 36 each have a damping device 21 assign the purpose with the associated connection channel Venting and ventilation is connected so that everyone Connection channel either as a suction channel or as a pressure channel can work.
  • a damping device 21 is shown in a hint in FIG. 2.
  • the damping device 21 on the inside Sheath wall 1d arranged with regard to a description of the design features in detail on the 1 is referred to, the 3 is essentially only differs by the offset to the jacket wall 1d.
  • the receiving space 23 through one along the jacket wall 1d and the housing cover 4 penetrating channel also to the associated connecting channel be ventilated. If the axial piston machine too 3 should be suitable for a connection change, a second damping device 21 is required on the other machine side, as indicated in principle has already been described with reference to FIG. 2 is.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
EP99124217A 1998-12-22 1999-12-03 Machine à pistons hydrostatique Expired - Lifetime EP1013927B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19859442A DE19859442C1 (de) 1998-12-22 1998-12-22 Hydrostatische Kolbenmaschine
DE19859442 1998-12-22

Publications (3)

Publication Number Publication Date
EP1013927A2 true EP1013927A2 (fr) 2000-06-28
EP1013927A3 EP1013927A3 (fr) 2000-11-29
EP1013927B1 EP1013927B1 (fr) 2005-02-09

Family

ID=7892250

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99124217A Expired - Lifetime EP1013927B1 (fr) 1998-12-22 1999-12-03 Machine à pistons hydrostatique

Country Status (2)

Country Link
EP (1) EP1013927B1 (fr)
DE (2) DE19859442C1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2767713A1 (fr) * 2013-02-19 2014-08-20 Innas B.V. Système de positionnement de bloc oscillant hydraulique
WO2019097093A1 (fr) 2017-11-15 2019-05-23 Pandrol Iberica S.A.U. Système de fixation et d'alignement du patin d'un rail
CN111472955A (zh) * 2020-03-26 2020-07-31 浙江大学 一种外置的斜盘柱塞泵预压紧力与变量调节装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009006909B4 (de) 2009-01-30 2019-09-12 Robert Bosch Gmbh Axialkolbenmaschine mit reduzierter Stelldruckpulsation

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE32924C (de) * WUNDERLICH in Magdeburg - Sudenburg , Breite Weg 119 Luftbuffer für Druckpumpen
US1506893A (en) * 1922-12-13 1924-09-02 Egersdorfer Fritz Pump, compressor, or blower
DE441952C (de) * 1925-06-26 1927-03-17 Fritz Egersdoerfer Einrichtung zur Abdichtung der Kolbentrommel an der Steuerflaeche fuer Kolbenmaschinen mit umlaufender Kolbentrommel und parallel der Hauptwelle verschiebbaren Kolben
DE1951234A1 (de) * 1969-10-10 1971-04-22 Linde Ag In geschlossenem Kreislauf arbeitende hydrostatische Maschine
EP0402585A1 (fr) * 1989-06-12 1990-12-19 Tecumseh Products Company Réservoir d'expansion de l'huile dans le carter d'une transmission hydrostatique
DE19522168A1 (de) * 1995-06-19 1997-01-02 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3912937A1 (de) * 1989-04-20 1990-10-25 Teves Gmbh Alfred Daempfungseinrichtung fuer hydraulische verdraengerpumpen

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE32924C (de) * WUNDERLICH in Magdeburg - Sudenburg , Breite Weg 119 Luftbuffer für Druckpumpen
US1506893A (en) * 1922-12-13 1924-09-02 Egersdorfer Fritz Pump, compressor, or blower
DE441952C (de) * 1925-06-26 1927-03-17 Fritz Egersdoerfer Einrichtung zur Abdichtung der Kolbentrommel an der Steuerflaeche fuer Kolbenmaschinen mit umlaufender Kolbentrommel und parallel der Hauptwelle verschiebbaren Kolben
DE1951234A1 (de) * 1969-10-10 1971-04-22 Linde Ag In geschlossenem Kreislauf arbeitende hydrostatische Maschine
EP0402585A1 (fr) * 1989-06-12 1990-12-19 Tecumseh Products Company Réservoir d'expansion de l'huile dans le carter d'une transmission hydrostatique
DE19522168A1 (de) * 1995-06-19 1997-01-02 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2767713A1 (fr) * 2013-02-19 2014-08-20 Innas B.V. Système de positionnement de bloc oscillant hydraulique
WO2014128024A1 (fr) * 2013-02-19 2014-08-28 Innas Bv Système de positionnement de bloc oscillant hydraulique
CN105339656A (zh) * 2013-02-19 2016-02-17 英纳斯有限公司 液压斜块定位系统
US10961991B2 (en) 2013-02-19 2021-03-30 Innas B.V. Hydraulic swash block positioning system
WO2019097093A1 (fr) 2017-11-15 2019-05-23 Pandrol Iberica S.A.U. Système de fixation et d'alignement du patin d'un rail
CN111472955A (zh) * 2020-03-26 2020-07-31 浙江大学 一种外置的斜盘柱塞泵预压紧力与变量调节装置
CN111472955B (zh) * 2020-03-26 2021-02-23 浙江大学 一种外置的斜盘柱塞泵预压紧力与变量调节装置

Also Published As

Publication number Publication date
DE19859442C1 (de) 2000-10-26
EP1013927A3 (fr) 2000-11-29
EP1013927B1 (fr) 2005-02-09
DE59911596D1 (de) 2005-03-17

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