EP2094980A2 - Coquille de coussinet pour machine hydrostatique et machine hydrostatique pourvue de cette coquille de coussinet - Google Patents

Coquille de coussinet pour machine hydrostatique et machine hydrostatique pourvue de cette coquille de coussinet

Info

Publication number
EP2094980A2
EP2094980A2 EP07846755A EP07846755A EP2094980A2 EP 2094980 A2 EP2094980 A2 EP 2094980A2 EP 07846755 A EP07846755 A EP 07846755A EP 07846755 A EP07846755 A EP 07846755A EP 2094980 A2 EP2094980 A2 EP 2094980A2
Authority
EP
European Patent Office
Prior art keywords
bearing shell
bearing
recess
axial piston
shell according
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Withdrawn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
EP07846755A
Other languages
German (de)
English (en)
Inventor
Dino MÜLLER
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 EP2094980A2 publication Critical patent/EP2094980A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/20—Sliding surface consisting mainly of plastics
    • 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
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
    • 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
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/40—Imides, e.g. polyimide [PI], polyetherimide [PEI]
    • F16C2208/42—Polyamideimide [PAI]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps

Definitions

  • the invention relates to a bearing shell for a hydrostatic machine or a hydrostatic machine with this bearing shell.
  • the bearing shells each with a fixing element, e.g. with a threaded screw, thereby ensuring that the threaded bolt engages peg-shaped in a prefabricated hole in the bearing shell.
  • the invention has for its object to improve a bearing shell and a hydrostatic machine of the type specified in particular with respect.
  • the simplification is to be a simple and inexpensive
  • the bearing shell as a plastic injection-molded part, can not only be produced simply and quickly, and therefore cost-effectively, but also with precision.
  • the latter also makes it possible to prefabricate the bearing shell by injection molding in its final form.
  • the bearing shell can also be manufactured with a plastic of sufficient hardness, whereby a sufficient wear resistance and durability is achieved.
  • Another advantage is that plastic has a lower specific gravity than bronze and therefore the bearing shell according to the invention is relatively easy and contributes to weight savings.
  • Lubricant in particular for the hydraulic fluid, opens.
  • This embodiment which is particularly suitable for a sliding bearing, improves the lubricant supply between the bearing sliding surfaces.
  • the lubrication recesses are preferably formed by lubrication grooves, which at the same time form the feed channels for the lubricant when they open laterally on at least one side of the bearing shell.
  • the embodiments with lubrication recesses is particularly suitable for the bearing shell, which is located on the pressure side of the axial piston machine.
  • FIG. 1 shows an axial piston according to the invention in axial section.
  • FIG. 2 shows the partial section II-II in Figure 1 in an enlarged view.
  • Fig. 3 is a visible in Figure 2 bearing shell in plan view.
  • FIG. 4 shows the bearing shell in the plan view of Figure 4 in a modified embodiment.
  • FIG. 5 shows the bearing shell in section V-V according to FIG. 2 in a further modified embodiment
  • FIG. 6 shows the bearing shell in section V-V according to FIG. 2 in a further modified embodiment
  • FIG. 7 shows the axial piston machine or the bearing shell in a further modified embodiment in a section VV corresponding section.
  • Fig. 8 the bearing shell of FIG. 7 in a perspective view with a view towards their Lagert. sliding surface;
  • FIG. 10 the bearing shell of FIG. 9 in a perspective view with a view towards their Lagertial. Sliding surface.
  • the axial piston machine denoted by 1 in its entirety in Fig. 1 is a hydrostatic machine which, when using a hydraulic fluid, in particular hydraulic oil, can be operated in one or more types of operation, e.g. as a pump or motor, which is well known.
  • the main parts of the Axialkolbenmaschme 1 are a housing 2, in which a drive shaft 3 in, for example. two, an axial distance from each other having rotary bearings 4, 5 is rotatably mounted and a fürstattungsloch 6 in an end wall 2a of the housing 2 extends outwardly and is rotatably mounted on the end wall 2a in the pivot bearing 4.
  • the drive shaft 3 is sealed in the region of the end wall 2a by a sealing ring, which is preferably inserted into a ring carrier, which is attached to the end wall 2a.
  • the housing 2 is preferably a cup-shaped housing, wherein the end wall 2 a forms the bottom of the pot shape, the is detachably closed by a lid 2b, which bears sealed against the free edge of the peripheral wall 2c of the housing 2 and is attached thereto, for example by means arranged distributed on the circumference and indicated by dashed lines fastening screws. 7
  • the following axially successively arranged functional parts of an engine are arranged, namely a drive plate 9 with respect to the longitudinal axis 11 of the axial piston 1 normally obliquely extending drive plane 12, in which a plurality preferably arranged on a pitch circle and in particular approximately Axially extending piston 13 are axially or indirectly supported axially, with their drive disc 9 facing away from the piston shafts 13a in piston holes 14 of a cylinder block 15 axially displaceable, which is rotatably connected to the drive shaft 3 and on its drive plate 9 side facing away axially on a control disc 16 is applied, in their cylinder block 15 facing control surface control openings 17, eg two kidney-shaped and opposing control openings 17, which correspond to extending from the piston holes 14 control channels 18 in the cylinder block 15.
  • control surface control openings 17 eg two kidney-shaped and opposing control openings 17
  • Control openings 17 extend in the cover 2c each have a supply or discharge line 19, 21 for the hydraulic fluid.
  • the drive disk 11 is formed by a swash plate with a cylinder block 15 facing and the drive plane 12 forming oblique sliding surface on which the piston 13 with spherical piston heads 13b and pivotable thereon mounted so-called sliding shoes 22 slidably abut.
  • the piston heads 13b are secured in the sliding position on a sliding surface 9a of the drive plate 9 by means of a retaining device with a sliding disc 22 engaging behind the retaining plate 23.
  • the drive plate 9 is pivotally mounted in a pivot bearing 24 with a transverse to the longitudinal axis 1 extending pivot axis 24a and pivoting to increase or decrease the flow volume of the hydraulic fluid by a pivoting device 25, the pivoting movements are preferably controlled automatically.
  • the two pivot bearings 24b, 24c as shown in Fig. 2, formed by so-called. Schwenkwiegen, i. they each have two sliding or bearing surfaces 2 ⁇ a, the circular arc or zylinderabwithstandformig are curved concavely about the pivot axis 24a, wherein the curvature is open to Zylmderblock 15 out and the drive plate 9 can be mounted from this axial side.
  • the bearing surface 2 ⁇ a is in each case attached to a bearing shell 26 formed, which is formed by a corresponding arc of a circle curved bearing strip 26c extending in cross-section preferably parallel to the pivot axis 24a and has a width b, which, taking into account their arcuate length L results in a sufficiently large storage area to achieve the lowest possible surface pressure ,
  • the length L of the bearing strip 26c extends through an angle W which is less than 180 °, e.g. may be about 110 ° to 150 °.
  • the bearing shells 26 thus have inside a bearing surface 26a extending at right angles to the radial plane E2 of the concave curvature and externally a contact surface 26d extending parallel thereto, with which they rest against a correspondingly curved contact surface 2e of the housing 2 and are radially supported.
  • bearing shells 26 each form a plain bearing. But it can also be at least one of the pivot bearings 24b, 24c, for example, arranged on the suction side of the axial piston pivot bearing as rolling bearings with cylindrical or barrel-shaped Wälzrollen Wr be formed, as illustrated in Fig. 2 as a particular detail.
  • the Wälzrollen Wr roll on the bearing surface 26a of the bearing shell 26, wherein the radius of the bearing surface 26b on the pivot body is smaller than the radius of the bearing surface 26a. Therefore, between the bearing surfaces 26a, 26b there is a gap in the size of the cross-sectional dimension of the rolling rollers Wr, which are arranged in this gap and roll on the bearing surfaces 26a, 26b in the pivoting mode.
  • Fixing device 27 is provided, which is preferably effective at the same time in the transverse direction.
  • the fixing device 27 has a fixing element 27a arranged on the bearing shell 26 which interacts with a corresponding fixing element 2f on the housing 2 in a form-fitting manner.
  • the fixing element 27a is formed by a protruding from the bearing shell 26 fixing pins, which preferably protrudes from the abutment surface 26d, in particular in a middle position with respect.
  • the corresponding fixing element 2f is preferably formed by a fixing hole in a cross-sectional shape and size corresponding to the fixing pin, which is preferably arranged in the corresponding bearing surface 2e, preferably also in its middle position.
  • the Fixierlocher are preferably blind holes, which auseunden on the contact surface 2e.
  • the existing fit between these parts may be formed as a press fit.
  • clamping rings 27b which are formed diametrically with an oversize and therefore when pressed into the fixing hole yield elastically and press with an elastic clamping voltage against the wall of the fixing hole.
  • the one or more clamping rings 27b are, for example, sawtooth-shaped and facing away from the free end of the fixing pin, whereby they easy insertion into the
  • one or more lubrication recesses 28 are preferably located, into each of which a lubricant supply channel opens.
  • the lubricating recesses 28 are preferably formed by lubrication grooves, which open on at least one side of the bearing shell 26.
  • the lubrication grooves preferably extend obliquely to the associated pivot plane E2, wherein the at least one lateral groove opening 28a is arranged in particular on the end of the associated lubrication groove facing away from the direction of rotation. It is particularly advantageous to allow the lubrication grooves to open out on both sides, so that groove openings 28a are present on both sides.
  • the oblique extent of the lubrication grooves leads to the advantage that the lubricant, preferably the hydraulic fluid, is entrained by frictional contact with the associated bearing surface 26b and thereby conveyed between the bearing surfaces 26a, 26b, whereby the lubrication is improved and the bearing wear is reduced.
  • the lubricant preferably the hydraulic fluid
  • the loads of the bearing surface 26a or are particularly large on the high pressure side of the axial piston machine 1 it is advantageous to form the lubrication recesses 28 or lubrication grooves in the bearing surface 26a of the bearing shell 26, which is arranged on the pressure side. It but may also be arranged on the suction pressure side bearing shell 26, which has at least one lubrication recess 28.
  • the bearing shells 26 have on one or both lateral edges a marginal web 26g projecting beyond the bearing surface 26a, the inner surface of which forms a circular-arc-shaped radial shoulder surface 26h which can serve for the associated bearing shell or another part of
  • mirror-inverted bearings 26 are preferably made of a plastic with a hardness and strength, which is sufficiently large, taking into account the surface pressure occurring to accommodate the bearing loads can. It is z.
  • Example to the known plastic TORLON 4301, in particular to a plastic which is moldable by injection molding into moldings, here the bearing shells 26, in an associated molding device.
  • Plastic parts produced by injection molding have a so-called spray lug 29 at the point at which the liquid plastic is injected into the mold, and at which forms after the solidification of the plastic, a small approach that interferes in many cases.
  • a spray attachment 29 may be arranged on the end face of the fixing pin (not shown).
  • One of the Face possibly protruding spray tip 29 may be included in a correspondingly deep-trained fixing hole without disturbing.
  • the fixing pin In order to avoid larger wall thicknesses in the region of the fixing pin, it is advantageous to design the fixing pin as a hollow pin. In particular, in this embodiment, it is advantageous to spray the sprue 29, e.g. To arrange at the bottom of the cavity 27c of the hollow pin, so that the spray lug 29 projects into the depth of the fixing hole, without having to be made with a large depth.
  • 26 26 a recess 31 are respectively disposed in the bearing surface 2 ⁇ a or sliding surface of the at least a lubrication recess 28 differs in that its edge 32 has a distance a from the edge 26i of the bearing surface 2 ⁇ a.
  • the recess 31 has a closed edge 32 on its entire circumference, and it is closed when the drive disk 9 abuts against the bearing surface 2 ⁇ a, so that there is no connection to the interior 8 of the housing 2.
  • the recess 31 is located in the middle region of both the length L extending in the direction of curvature and the width b of the bearing shell 26 or its bearing surface 26a extending transversely thereto or parallel to the pivot axis 24a.
  • the recess 31 may also form a lubricating recess in its training described so far, the the lubrication improved by the fact that the lubricant in the recess 31, preferably the hydraulic fluid, taken by a frictional contact with the bearing surface 26b of the drive plate 9 and thereby between the bearing surfaces 2 ⁇ a, 26b is promoted or even wetted only.
  • the filling of the recess 31 with the lubricant takes place automatically during operation due to the pressure in the interior 8, which allows the lubricating fluid to seep into the recess 31 due to the sliding clearance existing between the bearing surfaces 26a, 26b.
  • Axial piston machine 1 is connected.
  • unloading force 34 generated during operation of the axial piston 1 in the recess 31 under pressure fluid effective against the drive plate 9 and shown as an arrow unloading force 34, which relieves the drive plate 9 and thus forms a hydrostatic pressure relief.
  • the area size of the recess 31 is only so great form, that the unloading force 34 is less than an on the drive plate 9 oppositely directed loading force 35, which in operation due to the
  • the pressure supply to the recess 31 may extend in channels, not shown, through the piston sliding shoes 22 and the drive disk 9 or through the housing 2.
  • a pressure channel 33 extends through the fixing element 27a or the
  • the recess 31 is preferably formed with a plurality of mutually transversely extending and interconnected Nutenabêten 31 a, 31 b, between which bearing disk sections 26 k arranged with associated bearing surface portions 26 a, z. B. as a dock or as an island.
  • a groove section 31a extending in the direction of curvature with the length L1 can be provided, from which a plurality of groove sections 31b each having a spacing c extending from each other in the direction of curvature extend transversely or parallel to the pivot axis 24a. In between are the bearing surface sections 26al.
  • two mutually extending in the direction of curvature groove portions 31a are provided, which have a distance x from each other, wherein the transverse thereto extending groove portions 31b with two groove portions 31a are connected.
  • the groove portions 31b may extend obliquely.
  • the depth t of the recess 31 may be low and z. B. only about 1 mm or more.
  • the recess 31 In the area of located on the suction side of the axial piston machine 1 bearing shell 26 shown in FIG. 9 and 10, because of the lower load during operation, the recess 31 only needs to be formed as a lubrication recess, d. H. the pressure channel 33 need not be present, as shown in FIG. 9.
  • the length Ll of the recess 31 may be less than in the bearing shell 26 of FIG. 7 and 8 on the pressure side. It is within the scope of the invention, however, also possible in the
  • Bearing shell 26 which is located on the suction side, no recess 31 or no lubrication recesses 28 to be arranged.
  • a further simplification can be achieved in that the two bearing shells 26 are of the same design, whereby they fit into positions rotated through 180 ° and therefore only one type of bearing shell 26 needs to be manufactured and stored or even distributed, around a pivot bearing 24 to realize with two bearings 26 according to the present embodiment. All described and / or drawn features can be combined with each other in the context of the invention.

Landscapes

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

Abstract

L'invention concerne une coquille de coussinet (26) qui est destinée à une machine hydrostatique, en particulier une machine à pistons axiaux (1), et qui présente un élément de fixation (27a) servant à fixer la coquille de coussinet (26), courbée en forme de section d'arc de cercle, dans la position de montage. L'objectif de l'invention est d'améliorer cette coquille de coussinet afin de simplifier sa structure, ainsi que son montage et son démontage. À cet effet, la coquille de coussinet (26) se compose de plastique, l'élément de fixation (27a) étant formé en une seule pièce avec celle-ci.
EP07846755A 2006-11-22 2007-11-22 Coquille de coussinet pour machine hydrostatique et machine hydrostatique pourvue de cette coquille de coussinet Withdrawn EP2094980A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006055161A DE102006055161A1 (de) 2006-11-22 2006-11-22 Lagerschale für eine hydrostatische Maschine und hydrostatische Maschine mit dieser Lagerschale
PCT/EP2007/010153 WO2008061768A2 (fr) 2006-11-22 2007-11-22 Coquille de coussinet pour machine hydrostatique et machine hydrostatique pourvue de cette coquille de coussinet

Publications (1)

Publication Number Publication Date
EP2094980A2 true EP2094980A2 (fr) 2009-09-02

Family

ID=39301147

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07846755A Withdrawn EP2094980A2 (fr) 2006-11-22 2007-11-22 Coquille de coussinet pour machine hydrostatique et machine hydrostatique pourvue de cette coquille de coussinet

Country Status (3)

Country Link
EP (1) EP2094980A2 (fr)
DE (1) DE102006055161A1 (fr)
WO (1) WO2008061768A2 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010032651A1 (de) 2010-07-29 2012-02-02 Robert Bosch Gmbh Verstellbare Axialkolbenmaschine
JP4934749B1 (ja) * 2011-02-23 2012-05-16 株式会社小松製作所 可変容量型油圧ポンプ・モータ
JP5472340B2 (ja) * 2012-02-10 2014-04-16 株式会社デンソー 燃料供給ポンプ
GB2502824A (en) * 2012-06-08 2013-12-11 Water Hydraulics Company Ltd Axial piston variable stroke hydraulic machine
DE102012022999A1 (de) 2012-11-24 2014-05-28 Robert Bosch Gmbh Einstellbare Axialkolbenmaschine in Schrägscheibenbauweise mit entlastetem Wiegenlager
DE102013218203A1 (de) 2013-09-11 2015-03-12 Robert Bosch Gmbh Schrägscheibenmaschine
DE102013220229A1 (de) 2013-10-08 2015-04-09 Robert Bosch Gmbh Schrägscheibenmaschine
DE102013227067A1 (de) 2013-12-23 2015-06-25 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine und Lagerschale dafür
DE102014204898A1 (de) * 2014-03-17 2015-09-17 Robert Bosch Gmbh Schrägscheibenmaschine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020179780A1 (en) * 2001-05-31 2002-12-05 Benoit Thomas A. Clip assembly with positive locating features

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3244463A (en) * 1961-12-06 1966-04-05 Torrington Co Hardened liner for anti-friction bearing and split housing
US4043255A (en) * 1970-09-02 1977-08-23 National Research Development Corporation Cam follower piston
DE3023317A1 (de) * 1980-06-21 1982-01-14 Kunststoffverarbeitungsbetrieb Hochgreef & Krahnen GmbH & Co KG, 4178 Kevelaer Lager insbesondere aus kunstharzpressstoff
CH684343A5 (de) * 1990-08-21 1994-08-31 Rieter Ag Maschf Textilmaschine mit einer Einrichtung zum Verstrecken von faserförmigem Material.
DE19613609C2 (de) 1996-04-04 2000-02-17 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit internem Spülkreislauf
JP2000346045A (ja) * 1999-06-01 2000-12-12 Daido Metal Co Ltd エンジン用主軸受
DE10150654C5 (de) * 2001-10-13 2008-07-10 Ks Gleitlager Gmbh Lagerelement

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020179780A1 (en) * 2001-05-31 2002-12-05 Benoit Thomas A. Clip assembly with positive locating features

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2008061768A2 *

Also Published As

Publication number Publication date
WO2008061768A2 (fr) 2008-05-29
WO2008061768A3 (fr) 2008-09-25
DE102006055161A1 (de) 2008-05-29

Similar Documents

Publication Publication Date Title
EP2094980A2 (fr) Coquille de coussinet pour machine hydrostatique et machine hydrostatique pourvue de cette coquille de coussinet
EP0320822B2 (fr) Pompe à pistons axiaux
EP1886035B1 (fr) Palier pivotant a disques obliques
DE4424670B4 (de) Hydraulische Kolbenmaschine
EP2038890A2 (fr) Moteur à pistons axiaux comportant un disque appendice sur un disque de retenue, disque de retenue correspondant et disque appendice correspondant
WO2012034619A1 (fr) Machine à pistons axiaux
DE202013102506U1 (de) Innenzahnradmaschine mit Schrägbohrungen zur Verbindung hydrostatischer Lager für ein Hohlrad mit einem Druck-Hauptkanal
EP1929154B1 (fr) Pompe a piston
DE102017212521A1 (de) Selbstausrichtende Nockenfolgerollenvorrichtung
DE2001484A1 (de) Hyd?atische Eno? fuer Pumpen und Motoren
DE202013103826U1 (de) Innenzahnradmaschine mit Füllstück-Rückhalteeinrichtung
DE102010032056B4 (de) Kolbeneinheit
DE19844326A1 (de) Radialkolbenpumpe
DE102018205010A1 (de) Hydrostatische Axialkolbenmaschine
EP2464853B1 (fr) Pompe à haute pression
DE102006044294B3 (de) Radialkolbenpumpe
DE69838260T2 (de) Hydraulische pumpe oder motor
DE202015103379U1 (de) Wasserhydraulische Maschine
EP0469135B1 (fr) Pompe ou moteur a engrenages
DE102018205884A1 (de) Axialkolbenmaschine mit Druckentlastung in den Durchtriebsraum
DE19816926C2 (de) Axialkolbenmaschine mit einer in einem Schwenklager schwenkbar gelagerten Schrägscheibe
DE102004026584A1 (de) Kolbenpumpe mit verringertem Verschleiß
DE957804C (de) Schiefscheibentriebwerk
EP1798415B1 (fr) Pompe à haute pression
DE102015222289A1 (de) Axialkolbenmaschine mit verstellbarem Cross-Angle

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20090129

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

RIN1 Information on inventor provided before grant (corrected)

Inventor name: MUELLER, DINO

17Q First examination report despatched

Effective date: 20091120

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20140603