EP0675286A1 - Machine à pistons axiaux avec décharge hydrostatique du palier du plateau d'impulseur - Google Patents

Machine à pistons axiaux avec décharge hydrostatique du palier du plateau d'impulseur Download PDF

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Publication number
EP0675286A1
EP0675286A1 EP95101841A EP95101841A EP0675286A1 EP 0675286 A1 EP0675286 A1 EP 0675286A1 EP 95101841 A EP95101841 A EP 95101841A EP 95101841 A EP95101841 A EP 95101841A EP 0675286 A1 EP0675286 A1 EP 0675286A1
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston machine
machine according
pressure
bearing surface
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
EP95101841A
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German (de)
English (en)
Other versions
EP0675286B1 (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
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Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0675286A1 publication Critical patent/EP0675286A1/fr
Application granted granted Critical
Publication of EP0675286B1 publication Critical patent/EP0675286B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/007—Swash plate
    • F01B3/0073—Swash plate swash plate bearing means or driving or driven axis bearing means
    • 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

Definitions

  • the invention relates to an axial piston machine of adjustable displacement with at least hydrostatic relief of its sliding surface-mounted control lens or lifting disk according to the preamble of claim 1.
  • Axial piston machines of this type are known in practice, for example, in a swashplate design, in which the respective lifting or swashplate, which is pivotally mounted on both sides of the axis of rotation of the cylinder drum for the purpose of adjusting the displacement volume, is hydrostatically supported by means of a pressure field supplied by the fluid source with pressure oil.
  • the recesses are elongated rectangular cutouts in the slide bearings in the swivel direction of the swash plate.
  • the inlet channels for supplying pressure oil to the pressure fields open into the cutouts and run through the swash plate up to the support surface that supports the pistons via sliding shoes.
  • the slide shoes are also mounted hydrostatically and for this purpose are provided in their sliding surfaces facing the support surface with a circular recess, also called a pressure pocket, which is acted upon by an axial bore in the associated piston with the piston pressure prevailing in the respective cylinder bore.
  • the inlet channels open out on the support surface in the slideway of the pressure pockets.
  • the recesses of the slide bearings are alternately under the low leakage oil pressure prevailing in the housing and the high piston pressure prevailing in the cylinder bores, so that the pressure fields pulsate at a frequency corresponding to the speed of the cylinder drum.
  • the swash plate can lift so far from the bearing surfaces that are fixed to the housing that the fluid drain from the pressure fields exceeds their fluid supply via the inlet channels and thus leads to a collapse of the pressure fields until metallic contact of the displaceable swash plate bearing surfaces with the housing-fixed bearing surfaces leads; the one that occurs The decrease in gap height between these bearing surfaces immediately results in a correspondingly rapid and high pressure build-up, which in turn can cause the swash plate to be lifted off completely.
  • resonant vibrations can occur in certain frequency ranges, which, like pressure fluctuations that occur in accordance with the load behavior of a consumer driven by the swashplate machine, lead to high dynamic loads and correspondingly high structure-borne noise levels, as well as possible jet cavitation due to the pulsating flow reversal in the supply channels, the functionality of the affect the hydrostatic bearing of the swash plate.
  • shaped recesses are e.g. Known from DE-OS 21 00 028: they are designed as self-contained ring grooves, each of which surround an island-shaped bearing surface portion of rectangular shape, in which a recess of a corresponding rectangular shape is formed. Furthermore, it is known from the aforementioned DE-OS 21 00 028 to form a number of parallel grooves in the two housing-fixed slide bearings for the swash plate of the swash plate machine, which run transversely over the bearing surfaces fixed to the housing and end closed at a distance from their lateral edges.
  • Oil distribution grooves in hydrostatically relieved bearings are also described in the specialist literature (see Oil Hydraulics, Dr. Jean Thoma, 1970 edition, p. 65) with the note that they must not be carried out to the outer edge to prevent a short circuit of the fluid pressure .
  • the total volume of fluid flowing out of the pressure field is increased in comparison with the prior art by the drainage capacity of the relief groove arrangement. Since this drainage capacity remains essentially constant when there are changes in gap height, the size of the total fluid volume flow that is flowing changes when interference forces occur with a correspondingly smaller amplitude. The amplitude of the pressure changes in the pressure field caused by the change in the fluid volume flow is correspondingly smaller, as a result of which, in the prior art, the "excess" reaction to interference forces is largely prevented and instead a damped response behavior is achieved. When using a pressure source as a fluid source, this damped response is particularly pronounced compared to a power source.
  • the pressure field is used for hydrostatic relief or storage of the lifting disc of a swash plate machine and is supplied with fluid via the piston-supporting sliding shoes, then the constant fluid flow from the pressure field towards leakage oil in the direction of the leak oil prevents a reversal of flow in the inlet channel and via the relief groove arrangement according to the invention thus jet cavitation on the slide shoes and the lifting disc.
  • the drainage capacity and thus the damped response of the relief groove arrangement can be adjusted to the respective operating conditions by appropriate selection of the cross-sectional area and / or length and / or design with, for example, a zigzag, meandering or any other suitable course.
  • An inlet throttle in the inlet channel as is usually used when the pressure field is connected to a pressure source, can be dispensed with due to the throttling action of the relief groove arrangement which corresponds to its outlet capacity. It is of course also possible to use such an inlet throttle in order to achieve a hydrostatic bearing with a correspondingly higher stability.
  • the recess further comprises a recess, via which the relief groove connects to the inlet channel stands.
  • the area of this recess can be equal to or smaller than that of the recesses used in the prior art.
  • the recess is preferably designed as an extension of the mouth of the inlet channel in the bearing surface.
  • the lifting disk represents the pivotable support body, which is expediently pivotably mounted with a further bearing surface in a further slide bearing fixed to the housing with a further bearing surface on the side of the axis of rotation of the cylinder drum opposite the first bearing fixed bearing surface, in at least one of the a further relief groove arrangement is formed in both further bearing surfaces.
  • a further relief groove arrangement is formed in both further bearing surfaces.
  • the axial piston machine shown in Fig. 1 is designed as a swash plate pump with adjustable delivery volume and two flow directions and comprises in a known manner as essential components a hollow cylindrical housing, which is only indicated by its lower end wall 1 in Fig. 1 and at its upper end by a not shown Connection plate is closed, a drive shaft 2, a control body 3, a cylinder drum 4 and a swash plate 5th
  • the drive shaft 2 protrudes through a through hole 6 in the lower end wall 1 into the housing and is rotatably supported in this through hole 6 and in a blind hole in the connecting plate by means of bearings, not shown.
  • the drive shaft 2 passes through a central through bore 7 in the swash plate 5 and two further central through bores in the control body 3 and in the cylinder drum 4 in the interior of the housing.
  • the control body 3 is attached to the connection plate and provided with two through openings in the form of kidney-shaped control slots (not shown), each of which is connected to a suction or pressure port of the swash plate pump, not shown.
  • the spherical control surface 8 of the control body 3 facing away from the connecting plate also serves as a bearing surface for the cylinder drum 4.
  • the cylinder drum 4 is rotatably connected by means of a keyway connection 9 connected to the drive shaft 2 and has generally axially extending cylinder bores 10, which are arranged uniformly on a partial circle coaxial with the drive shaft axis, directly on the cylinder drum end face facing the housing end wall 1 and on the radial cylinder drum bearing surface facing the control body 3 via outlet channels 11 Open out on the same pitch circle as the control slots.
  • Pistons 12, which are displaceably arranged within the cylinder bores 10, are provided at their ends facing the housing end wall 1 with ball heads 13 which are mounted in slide shoes 14 and are supported by them on an annular slide disk 15 which is penetrated by the drive shaft 2 and on the swash plate 5 is attached.
  • the sliding blocks 14 are provided on their sliding surfaces facing the sliding plate 15 each with a pressure pocket 16 in the form of a circular recess, which is connected via a through hole 17 in the sliding block 14 to a stepped axial through channel 18 in the respective piston 12 and in this way with the cylinder bore 10 connected is.
  • Each axial through channel 18 is formed in the area of the associated ball head 12 with a throttle 19.
  • a merely indicated actuating device 22 engages an arm 23 of the swash plate 5 which extends in the direction of the connecting plate and serves to pivot it about a swivel axis 24 which is perpendicular to the drive shaft axis 24.
  • the swash plate 5 is designed as a so-called swivel cradle with a semi-cylindrical cross section and with two on both sides Drive shaft 2 pivotally mounted in parallel to one another in the pivoting direction, that is to say perpendicular to the pivot axis 24, of the partially cylindrical bearing surfaces 25 in two housing-fixed slide bearings 26, each with a correspondingly shaped bearing surface 27.
  • Each slide bearing 26 is designed as a bearing shell, which forms part of a hollow cylinder wall, the inner wall surface of which is curved inwards and forms the bearing surface 27.
  • the slide bearings 26 are fastened to a correspondingly shaped inner surface of the housing end wall 1 with fastening means 28 (not shown in more detail).
  • the distance between the longitudinal central axes 29 of the bearing surfaces 25 and which extend in the pivoting direction 27 is equal to the diameter of the pitch circle of the pressure pockets 16.
  • the bearing surfaces 25 and 27 are designed as elongated rectangles, the bearing surfaces 27 fixed to the housing each have a step 30 on their parallel end faces arranged at the same distance from the pivot axis 24 on both sides thereof. These steps 30 divide the bearing surfaces 27 fixed to the housing into two partial areas of different lengths, measured in the pivoting direction, the shorter partial areas of which face one another.
  • Each relief groove arrangement in the form of a zigzag relief groove 31.1 consisting of individual groove sections with the same reference number 31.1 is formed with a uniform distribution in the bearing surfaces 27 fixed to the housing and opens out with an open end at the respective step 30.
  • the groove sections 31.1 intersect the respective central longitudinal axis 29 of the bearing surface at an angle ⁇ and extend into the edge regions of the respective bearing surface 27 parallel to the longitudinal central axis 29, without opening there.
  • the relief groove 31.1 has the approximately semicircular cross section shown in FIG. 3.
  • a recess 32 is formed which extends into the housing end wall 1 and to which an inlet channel 33.1 is connected.
  • This consists of a blind bore 34 opening into the recess 32 in the housing end wall 1, into which the blind bore 34 an inlet throttle 35.1 in the form of a variable throttle valve is screwed, and an inlet line 36 which connects the inlet of the inlet throttle 35.1 in a manner not shown with the Pressure connector of the swash plate pump connects.
  • Each recess 32 opens into the associated relief groove 31.1 over half its length.
  • a pressure field is built up between these bearing surfaces 25, 27 on both sides of the drive shaft 2, which, due to the reduced inlet pressure in the respective inlet throttle 35.1 compared to the high pressure, represents a hydrostatic bearing in the recess 32 and relief groove 31.1, the load-bearing capacity of which is different determined from the size of the respective bearing surface 27 including the recess 32 and the relief groove 31.1, from the inlet pressure and from the inflowing pressure oil flow, which in turn depends on the gap height, which is chosen so that under normal loading by the piston pressure there is no metallic contact between the Bearing surfaces 25 and 27 occurs.
  • the swash plate pump according to FIGS. 4 and 5 differs from that according to FIGS. 1 to 3 by a hydrostatic bearing of the swash plate 5 which, with otherwise the same construction and unchanged damped response to disturbing forces in the bearing surfaces 27 on both sides of the drive shaft 2, has one each has meandering relief groove 31.2, which opens out on the two end faces in the area of the respectively shorter partial area of the bearing surface 27 and includes groove sections 31.2 'running at right angles to the pivoting direction and further groove sections 31.2''connecting them, running parallel to the pivoting direction, and over each an inlet channel 33.2 is in fluid communication with the pressure oil in the cylinder bores 10 under piston pressure.
  • each inlet channel 33.2 runs through the Swash plate 5 and the sliding plate 15 and on the one hand opens out on their slideway 14 facing the sliding shoes on the pitch circle of the pressure pockets 16 and on the other hand in the middle of the swash plate bearing surface 25.
  • An inlet throttle 35.2 is formed in each inlet channel 33.2 in the transition area from the swash plate 5 to the sliding plate 15.
  • the swash plate 5 is only loaded on the so-called high pressure side, i.e. on that side of the drive shaft 2 on which the pistons 12 perform their compression stroke. If the swash plate 5 is pivoted upward, for example, from the zero position shown in FIG. 5, in which no piston stroke takes place, then when the cylinder drum 4 is rotated clockwise, the left side is the high-pressure side, which is hydrostatically supported by the pressure field which is between builds up the bearing surfaces 25, 27 on the left as a result of the pressure oil supply from the cylinder bores 10, in which the pistons 12 perform their compression stroke. On the so-called low-pressure side in FIG.
  • the swash plate 5 is only hydrostatically relieved from the cylinder bores 10, in which the pistons 12 perform their suction stroke, due to the lack of sufficient pressure oil supply to the bearing surfaces 25, 27 located there, this being due to the Pivotal movement of the swash plate 5 entrained and stored in the relief groove 31.2 trailing oil ensures sufficient lubrication of the two bearing surfaces 25, 27.
  • the discharge capacity of the meandering relief groove 31.2 on the high-pressure side determines the degree of damping with which the high-pressure-side hydrostatic bearing according to FIGS. 4 and 5 responds to disturbing forces.
  • the steady oil drain via this relief groove 31.2 with an essentially constant pressure drop to the leak oil also prevents the flow reversal occurring in the prior art due to the pulsating pressure fields in the pressure pockets 16 in the inlet channel 31.2 and thus jet cavitation on the sliding shoes 14 and the sliding disk 15.
  • the relief groove arrangement is formed in this housing-fixed and / or the associated control body bearing surface.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP95101841A 1994-03-18 1995-02-10 Machine à pistons axiaux avec décharge hydrostatique du palier du plateau d'impulseur Expired - Lifetime EP0675286B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4409370 1994-03-18
DE4409370A DE4409370C2 (de) 1994-03-18 1994-03-18 Axialkolbenmaschine verstellbaren Verdrängungsvolumens mit zumindest hydrostatischer Entlastung ihrer gleitflächengelagerter Steuerlinse bzw. Hubscheibe

Publications (2)

Publication Number Publication Date
EP0675286A1 true EP0675286A1 (fr) 1995-10-04
EP0675286B1 EP0675286B1 (fr) 1997-07-23

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Application Number Title Priority Date Filing Date
EP95101841A Expired - Lifetime EP0675286B1 (fr) 1994-03-18 1995-02-10 Machine à pistons axiaux avec décharge hydrostatique du palier du plateau d'impulseur

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EP (1) EP0675286B1 (fr)
DE (2) DE4409370C2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007030708A1 (de) * 2007-07-02 2009-01-08 Robert Bosch Gmbh Axialkolbenmaschine mit Drosselnut
DE102011121523A1 (de) 2011-12-16 2013-06-20 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise
DE102012214830B4 (de) 2012-08-21 2022-06-30 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit verstellbarer Schrägscheibe oder Schenkwiege und zugehörigem Gleitlager mit hydrostatischem Druckfeld, dessen Randkonturausbildung den Leckagestrom ins Gehäuse minimiert
DE102013210480A1 (de) 2013-06-06 2014-12-11 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102013218203A1 (de) * 2013-09-11 2015-03-12 Robert Bosch Gmbh Schrägscheibenmaschine
CH710829A1 (de) * 2015-03-06 2016-09-15 Liebherr Machines Bulle Sa Schwenkwiegenlagerung einer Axialkolbenmaschine.
DE102022201865A1 (de) 2022-02-23 2023-08-24 Robert Bosch Gesellschaft mit beschränkter Haftung Ventil und Axialkolbenmaschine mit einem Ventil

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2100028A1 (de) * 1970-04-03 1971-10-14 VEB Kombinat Orsta Hydraulik Be trieb Industriewerke Karl Marx Stadt, χ 9030 Karl Marx Stadt Hydrostatische Axialkolbenmaschine
FR2135776A5 (fr) * 1971-04-28 1972-12-22 Renault
DE3402634A1 (de) * 1983-01-27 1985-03-28 Linde Ag, 6200 Wiesbaden Einstellbare axialkolbenmaschine in schraegscheibenbauform
GB2207198A (en) * 1987-07-22 1989-01-25 Linde Ag Adjustable axial-piston machine of swash plate design

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD136285A1 (de) * 1978-12-28 1979-06-27 Wolfgang Tautenhahn Hydrostatische axialkolbenmaschine
DE4011737C2 (de) * 1990-04-11 1999-07-22 Linde Ag Verstellbare Axialkolbenmaschine in Schrägscheibenbauweise

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2100028A1 (de) * 1970-04-03 1971-10-14 VEB Kombinat Orsta Hydraulik Be trieb Industriewerke Karl Marx Stadt, χ 9030 Karl Marx Stadt Hydrostatische Axialkolbenmaschine
FR2135776A5 (fr) * 1971-04-28 1972-12-22 Renault
DE3402634A1 (de) * 1983-01-27 1985-03-28 Linde Ag, 6200 Wiesbaden Einstellbare axialkolbenmaschine in schraegscheibenbauform
GB2207198A (en) * 1987-07-22 1989-01-25 Linde Ag Adjustable axial-piston machine of swash plate design

Also Published As

Publication number Publication date
DE4409370C2 (de) 1997-04-17
EP0675286B1 (fr) 1997-07-23
DE4409370A1 (de) 1995-09-21
DE59500404D1 (de) 1997-08-28

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