EP1769157A1 - Machine a pistons axiaux pourvue d'une couche resistant a l'usure - Google Patents

Machine a pistons axiaux pourvue d'une couche resistant a l'usure

Info

Publication number
EP1769157A1
EP1769157A1 EP05761738A EP05761738A EP1769157A1 EP 1769157 A1 EP1769157 A1 EP 1769157A1 EP 05761738 A EP05761738 A EP 05761738A EP 05761738 A EP05761738 A EP 05761738A EP 1769157 A1 EP1769157 A1 EP 1769157A1
Authority
EP
European Patent Office
Prior art keywords
layer
axial piston
piston machine
sliding side
control plate
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.)
Withdrawn
Application number
EP05761738A
Other languages
German (de)
English (en)
Inventor
Georg Jacobs
Herbert Kurz
Bernd Emrich
Sascha Henke
Alexander Schattke
Thomas 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.)
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
Publication of EP1769157A1 publication Critical patent/EP1769157A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0804—Non-oxide ceramics
    • F05C2203/0808—Carbon, e.g. graphite
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the invention relates to a designed as an axial piston hydrostatic machine.
  • DE 102 23 844 A1 describes an axial piston machine with a control plate and a cylinder drum sliding on the control plate. On the paired, mutually rubbing surfaces, a plastic layer is arranged on one side and a carbon-containing layer on the other side.
  • the areas of the facing surfaces of the control plate and the cylinder drum are subjected to increased loads. This includes the notches normally present to avoid rapid pressure fluctuations at the control ports of the control plate.
  • the mutually facing surfaces are also claimed by a falling back of the cylinder drum or the pressure plate on the control plate.
  • a disadvantage of the axial piston machine mentioned above is that in the case of oil-containing pumped media, the plastic layer can react unfavorably with the pumped medium and the plastic layer is thereby exposed to increased wear.
  • vapor bubble formation and subsequent pressure pulses so-called cavitation, can occur in the hydraulic medium, and the already mentioned falling back of the cylinder drum or the pressure plate occur, wherein the plastic layer is only insufficiently resistant to such stresses and therefore wears out quickly, with the plastic layer peels off only in places, resulting in uneven loading and faster wear.
  • the axial piston machine according to the invention with the features of claim 1 has the advantage of increased wear resistance, in particular against beating loads of successive sliding parts, against cavitation and against the biaxial load.
  • the axial piston machine according to the invention is easier to manufacture and can be operated except with water with oil-containing fluids.
  • the measures carried out in the dependent claims relate to advantageous developments of the axial piston according to the invention.
  • the other, not coated with the layer sliding side consists of hardened by nitriding steel.
  • the carbon layer opposite sliding side can be made simplified.
  • the use of environmentally harmful non-ferrous metals can be dispensed with.
  • the layer is applied on the first sliding side or on the sliding side of the control plate. Since the control plate of an axial piston machine is smaller in size than the cylindrical drum, the layer can be applied to the control plate easier and cheaper.
  • control plate and / or the cylinder drum essentially consist of metal in the region of its sliding sides and the layer is applied directly on the metal surface of the sliding sides.
  • the layer adheres more consistently to the respective sliding side.
  • the functional layer can be applied either directly or preferably by mediation of an adhesive layer.
  • the layer is a diamond-like amorphous carbon layer, in particular a tetrahedral hydrogen-free amorphous carbon layer, ta-C.
  • the ta-C layer has excellent advantageous properties over conventional carbon layers used in an axial piston machine.
  • the fatigue resistance of the friction and wear-reducing layer is significantly increased in particular against adhesive flaking and cohesive removal, in particular with regard to the burden of cavitation and impact forces, which occur especially at elevated working pressure and fast, heavy load changes.
  • the wear resistance, especially at elevated load and dirty fluids is improved.
  • FIG. 1 is a schematic representation of an axial piston according to the invention
  • FIG. 2 shows the detail II shown in Fig. 1 in an enlarged form
  • Fig. 3 shows a preferred embodiment of a control plate of the invention
  • Axial piston machine in a plan view of the sliding side of the control plate
  • Fig. 4 shows a preferred embodiment of a cylinder drum of the invention
  • Axial piston machine in a plan view of the sliding side of the cylinder drum.
  • the axial piston machine shown in Fig. 1 is in swash plate design with adjustable
  • Displacement volume and a flow direction includes in a known manner as essential components a hollow cylindrical housing 1 with a frontally open
  • Connection plate 2 a lifting or swash plate 3 a
  • Control plate 4 which also control body or
  • Control mirror is called a drive shaft 5 and a
  • the swash plate 3 is formed as a so-called pivoting cradle with a semi-cylindrical cross-section and is supported by two bearing surfaces extending at a mutual distance parallel to the pivoting direction hydrostatic relief on two correspondingly shaped bearing shells 8, which are fixed to the inner surface of the connecting plate 2 opposite housing end wall 9.
  • the hydrostatic discharge takes place in a known manner via pressure pockets 10 which are formed in the bearing shells 8 and are supplied via connections 11 with pressure medium.
  • An accommodated in a bulge of a cylindrical housing wall 12 adjusting device 13 engages over an extending in the direction of the terminal plate 2 arm 14 on the swash plate 3 and serves to pivot the same about a pivot axis perpendicular to the pivot axis.
  • the control plate 4 is centered on the outer ring of the bearing 18 and is positioned in the starting direction at the inner surface of the housing facing the housing
  • the control plate 4 is provided with two through openings 15 in the form of kidney-shaped
  • Control slots provided, which are connected via a pressure channel 16D and suction channel 16S in the connection plate 2 to a pressure and suction line, not shown.
  • Pressure channel 16D has a smaller flow area than the suction channel 16S.
  • the housing interior facing and spherically formed control surface of the control plate 4 serves as a bearing surface for the
  • the drive shaft 5 protrudes through a through hole in the housing end wall 9 in the housing 1 and is rotatably supported by a bearing 17 in this through hole and by means of another bearing 18 in a narrower bore portion of a laterally enlarged blind bore 19 in the connection plate 2.
  • the drive shaft 5 passes in the interior of the housing 1 further through the central through hole 20 in the control plate 4, a central through hole 21 in the swash plate 3, and a central through hole in the cylinder drum 6 with two bore sections.
  • One of these bore sections is formed in a sleeve-shaped extension 23 projecting beyond the swashplate 3 facing the cylinder drum 6, via which the cylinder drum 6 is connected in a rotationally fixed manner to the drive shaft 5 by means of a keyway connection 24.
  • the remaining bore portion is formed with a conical shape. It tapers from its cross section of greatest diameter near the first bore section to its cross section of smallest diameter near the abutting on the control plate 4 end or bearing surface of the cylinder drum 6.
  • the defined by the drive shaft 5 and this conical bore portion annular space is denoted by the reference numeral 25 denotes.
  • the cylinder drum 6 has generally axially extending, stepped cylinder bores 26 which are arranged uniformly on a coaxial to the drive shaft axis pitch circle.
  • the cylinder bores 26 open on the cylinder drum end face 22 directly and on the control plate 4 facing cylinder drum bearing surface on MündungskanäIe 27 on the same pitch circle as the control slots.
  • the cylinder bores 26 including the liners 28 are referred to herein as cylinders.
  • piston 29 are provided at their swash plate 3 facing the ends with ball heads 30 which are mounted in sliding blocks 31 and are hydrostatically mounted on this attached to the swash plate 3 annular sliding disk 32.
  • Each slide shoe 31 is provided on its sliding surface 32 facing the sliding surface, each with a pressure pocket, not shown, which via a through hole 33 in the shoe 31 to a stepped axial Through passage 34 is connected in the piston 29 and connected in this way with the delimited by the piston 29 in the cylinder bore 26 working space of the cylinder.
  • a throttle is formed in the region of the associated ball head 30.
  • An axially displaceable means of the spline connection 24 arranged on the drive shaft 5 and acted upon by a spring 35 in the direction of the swash plate 3 hold-down device 36 holds the sliding blocks 31 in abutment against the sliding disk 32nd
  • the axial piston machine 1 is provided for operation with oil as the pumped medium.
  • the cylinder drum 6 is rotated together with the piston 29 in rotation.
  • the swashplate 3 is pivoted into an inclined position relative to the cylinder drum 6 by actuation of the adjusting device 13, all pistons 29 perform lifting movements.
  • each piston 29 passes through a suction and a compression stroke, with corresponding oil flows are generated, the supply and discharge via the MündungskanäIe 27, the control slots 15 and the pressure and suction channel 16D, 16S done.
  • each piston 29 pressure oil from the cylinder in question via the axial passage 34 and the through hole 33 in the associated shoe 31 in the pressure pocket and builds a pressure field between the sliding disk 32 and the respective shoe 31, as a hydrostatic bearing for the latter serves. Furthermore, pressurized oil is fed via the connections 11 to the pressure pockets 10 in the bearing shells 8 for the hydrostatic support of the swashplate 3.
  • the control plate 4 has the first sliding side 44 and the cylinder drum 6, the second sliding side 45. Between the two sliding sides 44, 45, a friction and wear-reducing layer 46 shown in greater detail in FIG. 2 is applied on the first sliding side 44.
  • Fig. 2 shows the detail II shown in Fig. 1 in an enlarged form, whereby the area around the layer 46, the control plate 4 and the cylinder barrel 6, as well as around the first sliding side 44, the second sliding side 45 and the opening 15 thereby enlarged is.
  • the layer 46 is arranged on the first sliding side 44, that is to say on the control plate 4.
  • the layer 46 preferably consists of a tetrahedral hydrogen-free amorphous diamond-like carbon, which is known by the abbreviation ta-C from the group of DLC layers (Diamond Like Carbon layers).
  • the friction-reducing and wear-protecting layer 46 is, for example, by a PVD process (Physical Vapor Deposition) or the specialized arc PVD process (arc discharge process) or a CVD process (Chemical Vapor Deposition), but preferably by a PECVD process (US Pat. Plasma Enhanced Chemical Vapor Deposition) evenly applied to the first sliding side 44.
  • the layer 46 is formed as a so-called. Thin film, for example, with a thickness of up to about 15 micrometers, with the range 1 to 3 micrometers is desired.
  • a metallic adhesive layer in particular of Cr, Ti, Zr is used.
  • the layer 46 opposite the second sliding side 45 of the likewise completely made of steel cylinder drum 6 is preferably hardened by nitriding.
  • the rotational movement between the layer 46 and the second sliding side 45 forms a hydrodynamic sliding film, which is formed by the conveying medium.
  • the layer rubs 46 on the second sliding layer 45. Due to the hydraulic pressure fluctuations occurring in the axial piston 1, especially when the axial piston is very stressed, the second sliding side 45 abruptly fall back on the layer 46 again. This creates a beating load which depends in particular on the working pressures and the pressure fluctuation curve in terms of their strength.
  • Fig. 3 shows a preferred embodiment of a control plate 4 of the axial piston machine 1 according to the invention in a plan view of the sliding side 44 of the control plate 4.
  • the approximately kidney-shaped openings 15 which serve to control the filling and emptying of the cylinder bores 26.
  • both openings 15 each have a notch 47 on their ends arranged in the direction of rotation.
  • the notches 47 cause a soft reversing and are known as such from the prior art.
  • the sliding side 44 of the control plate 4 is completely covered with the layer 46, wherein in the context of the invention, the surfaces of the notches 47 and the areas of the inner sides of the openings 15 are included.
  • not shown notches may be arranged on the opposite direction of rotation end or holes in the control plate 4 introduced, according to the invention thereby also the surface of these not shown notches and the inner surfaces of the holes, not shown would be coated with the layer 46.
  • Material loads due to cavitation preferably occur in axial piston machines in a region 48, which is exemplified by a circular ring.
  • Fig. 4 shows a preferred embodiment of a cylinder drum 6 of the axial piston machine 1 according to the invention in a plan view of the sliding side 45 of the cylinder drum 6, which is referred to as the second sliding side 45.
  • the outlined in this figure with circular rings areas 48, which characterize the endangered by cavitation areas are approximately between the mouth channels 27 formed as a slot, the ends of the mouth channels 27 are outlined with.
  • the second sliding side 45 may be coated with the layer 46, wherein then preferably the inner surfaces of the mouth channels 27 are coated with the layer 46.
  • the invention is not limited to the embodiments and embodiments.
  • the features of the embodiment and the embodiments may be combined with each other in any manner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

Machine (1) à pistons axiaux qui comporte une plaque de commande (4) et un tambour cylindrique (6) rotatif pour rapport à la plaque de commande (4). Une première face de glissement (44) de la plaque de commande (4) frotte ou glisse contre une seconde face de glissement (45) du tambour cylindrique (6). L'une des faces de glissement (44, 45) possède une couche (46) contenant du carbone.
EP05761738A 2004-07-09 2005-06-08 Machine a pistons axiaux pourvue d'une couche resistant a l'usure Withdrawn EP1769157A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004033321A DE102004033321B4 (de) 2004-07-09 2004-07-09 Axialkolbenmaschine mit Verschleißschutzschicht
PCT/EP2005/006156 WO2006005399A1 (fr) 2004-07-09 2005-06-08 Machine a pistons axiaux pourvue d'une couche resistant a l'usure

Publications (1)

Publication Number Publication Date
EP1769157A1 true EP1769157A1 (fr) 2007-04-04

Family

ID=34972701

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05761738A Withdrawn EP1769157A1 (fr) 2004-07-09 2005-06-08 Machine a pistons axiaux pourvue d'une couche resistant a l'usure

Country Status (5)

Country Link
US (1) US20100000401A1 (fr)
EP (1) EP1769157A1 (fr)
CN (1) CN101002019A (fr)
DE (1) DE102004033321B4 (fr)
WO (1) WO2006005399A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006039719A1 (de) 2006-08-24 2008-02-28 Sms Demag Ag Breitseitenplatte einer Kokille
DE102008060067B4 (de) 2008-12-02 2017-11-02 Robert Bosch Gmbh Axialkolbenmaschine mit einer Steuerplatte, die in einem Teilbereich des äußeren Dichtstegs eine erhöhte Elastizität aufweist
DE102008060491A1 (de) 2008-12-04 2010-06-10 Robert Bosch Gmbh Axialkolbenmaschine und Steuerplatte mit Verschleißschutzschicht
JP5425722B2 (ja) * 2010-06-23 2014-02-26 日立建機株式会社 斜軸式液圧回転機
US9447686B2 (en) * 2010-06-23 2016-09-20 Robert Bosch Gmbh Axial piston machine having an insert ring and an insert ring for an axial piston machine
DE102012104923A1 (de) * 2012-06-06 2013-12-12 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Verdrängermaschine
JP6276911B2 (ja) * 2012-08-13 2018-02-07 Ｋｙｂ株式会社 液圧回転機
WO2014129926A1 (fr) * 2013-02-21 2014-08-28 Fomin Vladimir Fjodorovich Pompe axiale à plongeur avec récupération d'énergie
DE102014223564A1 (de) 2014-11-19 2016-05-19 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102015200310A1 (de) * 2015-01-13 2016-07-14 Robert Bosch Gmbh Kolbeneinheit und hydrostatische Radialkolbenmaschine
DE102015107343A1 (de) * 2015-05-11 2016-11-17 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Axialkolbenmaschine in Schrägachsenbauweise

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Also Published As

Publication number Publication date
WO2006005399A1 (fr) 2006-01-19
CN101002019A (zh) 2007-07-18
US20100000401A1 (en) 2010-01-07
DE102004033321B4 (de) 2006-03-30
DE102004033321A1 (de) 2006-02-02

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