EP0433730B1 - Axialkolbenmaschine in Schrägscheibenbauweise - Google Patents

Axialkolbenmaschine in Schrägscheibenbauweise Download PDF

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Publication number
EP0433730B1
EP0433730B1 EP90122886A EP90122886A EP0433730B1 EP 0433730 B1 EP0433730 B1 EP 0433730B1 EP 90122886 A EP90122886 A EP 90122886A EP 90122886 A EP90122886 A EP 90122886A EP 0433730 B1 EP0433730 B1 EP 0433730B1
Authority
EP
European Patent Office
Prior art keywords
swashplate
axial piston
piston machine
machine according
drive shaft
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.)
Expired - Lifetime
Application number
EP90122886A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0433730A1 (de
Inventor
Ludwig Wagenseil
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.)
Hydromatik GmbH
Original Assignee
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 Hydromatik GmbH filed Critical Hydromatik GmbH
Publication of EP0433730A1 publication Critical patent/EP0433730A1/de
Application granted granted Critical
Publication of EP0433730B1 publication Critical patent/EP0433730B1/de
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
    • 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
    • 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
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the invention relates to an axial piston machine in a swashplate design according to the preamble of claim 1.
  • Such an axial piston machine is known from DE-OS 37 33 083, the swash plate of which is pivotally supported on the housing via a pivot bearing off-center of the drive shaft axis.
  • the swivel bearing consists of housing support surfaces which are radial with respect to the drive shaft and convex projections supported by them on the rear of the swash plate, which is opposite the active surface supporting the pistons.
  • the contact surfaces between the convex projections and the housing support surfaces define the effective pivot axis about which the swash plate can be pivoted.
  • the swashplate swiveling Due to the arrangement of the swivel bearing off-center of the drive shaft axis and at the distance corresponding to the swashplate thickness from the swashplate effective surface, the swashplate swiveling has such a directed radial movement component that a reduction in distance between the inner swashplate edge of the swashplate part rising from the housing support surfaces and the drive shaft enters. The theoretically maximum achievable swivel angle is reached when the distance is reduced to 0.
  • An adjustable axial piston machine is known from GB-A 1 010 652, in which the swivel axis of the swash plate can be displaced radially with respect to the intersection of the drive shaft axis and the effective surface of the swash plate, but this radial displacement is possible at any time, arbitrarily feasible, ie not through the swiveling of the swash plate, and can be done both in the direction of the radial movement component of the swash plate effective surface and in the opposite direction by such an amount that in each desired swivel position of the swash plate, the resulting tilting moment exerted by the piston can be reduced to zero can.
  • the solution according to the invention is applicable to all swash plate type axial piston machines, i.e. on machines whose swash plates are mounted either outside the plane of their active surface in the center or off-center to the drive shaft axis and in the plane of their active surface off-center of the drive shaft axis.
  • the two opposite sections of the inner swashplate edge of the drive shaft cut from a straight line perpendicular to the effective swivel axis, approach the section further away from the swivel axis to a greater extent than the closer one.
  • the radial adjustment of the effective pivot axis takes place counter to the direction of the radial movement component of this section which is further away from the effective pivot axis.
  • the solution according to the invention is also applicable to axial piston machines, the swash plate in both directions, i.e. is pivotable from -V to + V.
  • the swash plate is pivotally supported on the housing of the axial piston machine via a swivel bearing arrangement defining the effective swivel axis, the swivel bearing arrangement being guided in a guide arrangement on the housing which extends radially in the direction of the radial movement component of the swash plate active surface.
  • the guide arrangement can comprise two guides arranged at a mutual distance and the swivel bearing arrangement two swivel hemispheres guided in one of the guides as well as two half-shells mounted on the swash plate and formed on them.
  • the swash plate is rotatable about two pivots parallel to the effective swivel axis in two formed on opposite housing parts, each running in a plane perpendicular to the effective swivel axis, which extend in such a way that they move along the swash plate pivoting of the pivot bearing arrangement Guide arrangement with the Forcing the direction of the radial movement component of the swashplate effective surface in the opposite direction.
  • the effective swivel axis is arranged outside the plane of the swashplate effective surface, it being able to cut the drive shaft axis when the swashplate is in the zero position.
  • the axis of rotation of the pivot pin can intersect the drive shaft axis when the swash plate is in the zero position, so that with positive guides running parallel to the drive shaft axis, the swash plate in both possible directions, i.e. both clockwise and counterclockwise, can be pivoted with the radial adjustment according to the invention of the effective pivot axis.
  • the axis of rotation when the swashplate is in the zero position is arranged to the side of the drive shaft axis and / or the positive guides run obliquely to the drive shaft axis at a guide angle, preferably in the direction of the effective swivel axis when the swashplate is in the zero position.
  • the guide angle can be substantially the same as the swivel angle of the swash plate that is fully swung out.
  • the effective swivel axis is arranged to the side of the drive shaft axis, as a result of which the swashplate is also preferably pivoted in one of the two directions, for example under the action of the hydraulic piston force.
  • Each pivot pin is advantageously mounted in a sliding block guided in each positive guidance.
  • the pivotable arrangement with hydrostatic support is mounted in the guide arrangement.
  • at least one through-channel connects through each swivel hemisphere a groove formed in its flat sliding surface with a groove formed in its spherical sliding surface.
  • At least one transverse channel can be provided in each swivel hemisphere, which connects a further groove formed in its spherical sliding surface with the through channel.
  • a lubricating oil line opening into the guides is advantageously provided in the housing.
  • the lubricating oil can also be supplied via a longitudinal bore in the adjusting device and connected transverse bores in the swash plate, the transverse bores opening into one of the grooves in the spherical sliding surfaces of the swivel hemispheres.
  • An intermittent supply of lubricating oil from the cylinder bores is preferably carried out via an axial bore through the pistons, the ball heads and the sliding shoes and a through bore leading to the swivel hemispheres in the swash plate, which is on the one hand in the half-shells in the area of the grooves and on the other hand in the swash plate Effective surface opens out on the slide shoe track.
  • the axial piston machine shown in the drawing comprises a cup-shaped housing 1, a drive shaft 2 with a drive shaft axis 3, a cylinder block 4, a swash plate 5 and a control or distributor body 6.
  • the housing 1 has an essentially square cross section and has a housing base 7 and four adjoining housing walls 8, on the free ends of which a housing cover 9 is detachably fastened.
  • the drive shaft 2 protrudes through a through hole in the housing base 7 into the interior of the housing 1 and is rotatably supported by a roller bearing 10 in this through hole and, not shown, in a blind hole in the housing cover 9.
  • the drive shaft 2 passes through a central through bore of the distributor body 6, the cylinder block 4 and the swash plate 5 in the interior of the housing 1.
  • the distributor body 6 is fastened to the housing cover 9 and is provided with two through openings in the form of kidney-shaped control slots 11, each of which is connected to a suction or pressure port, not shown, of the axial piston machine.
  • the spherical control surface 12 of the distributor body 6 facing away from the housing cover 9 also serves as an axial bearing surface for the cylinder block 4.
  • the cylinder block 4 is non-rotatably connected to the drive shaft 2 by means of a keyway connection 13 and has axially parallel cylinder bores 14 which are arranged uniformly on a partial circle coaxial with the drive shaft axis and open out freely via outlet channels 15 on the axial cylinder block bearing surface facing the distributor body 6.
  • the mouth channels 15 are arranged on the same pitch circle as the control slots 11.
  • Pistons 16, which are guided axially displaceably within the cylinder bores 14, are provided at their ends facing the housing base 7 with ball heads 17 which are mounted in sliding shoes 18 and are supported by these on an active surface 19 of the swash plate 5 supported on the housing base 7.
  • Channels 38 which run axially through the pistons 16 and the sliding shoes 18 and are only indicated in the latter, supply the sliding surfaces between the ball heads 17 and the sliding shoes 18 and the path of the latter on the swashplate active surface 19 with lubricating oil.
  • a compression spring 20 which is supported on the cylinder block 4 within its through bore and surrounds the drive shaft 2 presses via pressure pins 21, a print head 22 and an annular pressure disk 23 onto the sliding shoes 18 and thus holds them in contact with the active surface 19 of the swash plate 5.
  • the print head 22 of spherical cutout-like shape is attached to a sleeve-like extension of the cylinder block 4 and penetrated by the drive shaft 2.
  • the thrust washer 23 is movably supported with its inner edge on the outer surface of the print head 22 and is in contact with slide shoe projections 25 with holes 24 engaging around free end sections of the slide shoes 18.
  • the swash plate 5 is about a swivel bearing arrangement
  • Effective pivot axis 26 is pivotally supported on the housing base 7 off-center of the drive shaft axis 3, ie offset to the left in relation to the drawing.
  • the swivel bearing arrangement consists of two swivel hemispheres 27 and two half shells 28 mounted on them, which are formed in mutually opposite edge regions of the swashplate rear side opposite the swashplate active surface 19.
  • the effective pivot axis 26 is defined by the two centers of the pivot hemispheres 27.
  • swivel hemispheres 27 are each displaceably guided in a radial guide 29, which is radial with respect to the drive shaft 2 and perpendicular to the effective swivel axis 26 and is only indicated in the drawing, in the housing base 7.
  • a radial guide 29 which is radial with respect to the drive shaft 2 and perpendicular to the effective swivel axis 26 and is only indicated in the drawing, in the housing base 7.
  • the central through bore 30 of the swash plate 5 is arranged off-center of the drive shaft axis 3, ie shifted to the right in FIG. 1.
  • the central through bore 30 is essentially elliptical, its larger diameter extending perpendicular to the effective pivot axis 26 and allowing the swash plate 5 to be pivoted into the maximum pivot position shown in FIG. 2.
  • An adjusting device 31 in the form of a rod that can be displaced in the direction of the housing base 7 by a drive (not shown) is mounted in a nose attached to the swash plate 5 at the side.
  • the swashplate active surface 19 or a point P lying on it has a radially directed movement component R, which indicates the swashplate active surface, when the swashplate 5 is pivoted by an arrow V about the effective pivot axis 26 19 laterally to the right in FIG. 4 moves until the point S located on it, in which the larger diameter of the central through bore 30 intersects its inner edge 32, bears in position S 'on the drive shaft 2 and thus prevents further swiveling of the swash plate 5 beyond the swivel angle ⁇ obtained.
  • a positive guide arrangement which, when swashing the swivel plate of the effective swivel axis 26, has a radial movement RE with respect to the drive shaft 2 with a direction of the radial movement component R. the swashplate effective surface 19 forces opposite direction.
  • two parallel positive guides 33 are formed in the housing walls 8 cut by the effective pivot axis 26, in which the swash plate 5 is rotatably guided in a sliding block 35, each with a pivot pin 34 running parallel to the effective pivot axis 26.
  • the pivot pins 34 are located on the right-hand side of the drive shaft axis 3 in FIG. 4, both when the swash plate 5 is not swiveled out and when it is fully swiveled out extend into the fourth quadrant Q of an imaginary coordinate system xy, the coordinate origin of which lies on the axis of rotation 37 of the pivot pin 34 and the y axis of which runs parallel to the drive shaft axis 3.
  • the effective pivot axis 26 is arranged in the fourth quadrant Q.
  • the longitudinal center axes 36 of the constrained guides 33 run in the direction of the effective pivot axis 26. As shown in FIG.
  • the guide angle ⁇ 'of the constrained guides 33 is equal to the pivot angle ⁇ of the complete swung-out swash plate 5.
  • the positive guides 33 can also run parallel or in other directions obliquely to the drive shaft axis 3, for example in the direction of the first quadrant, the radial adjustment path of the effective swivel axis 26 being restricted depending on the size of the guide angle ⁇ '.
  • the ball heads 17 in the slide shoes 18 are supported hydrostatically on the active surface 19 of the swash plate 5.
  • the lubricating oil required for hydrostatic support is supplied from the cylinder bores 14 via axial bores 38 in the pistons 16, the ball heads 17 and the sliding shoes 18 (only shown in the latter).
  • the lubricating oil can be supplied to the swivel hemispheres 27 via lubricating oil lines 43 to the guides 29 and thus to the grooves 41 in the sliding surfaces of the swivel hemispheres 27.
  • the lubricating oil supply can take place through a longitudinal bore 44 in the adjusting device 31 and adjoining transverse bores 45 through the swash plate 5. The transverse bores 45 open out in the grooves 41 in the spherical surfaces of the swivel hemispheres 27.
  • the axial piston machine according to the invention can be known Be operated both as a motor and as a pump. Their function is described below only with reference to the radial adjustment of the effective swivel axis according to the invention:
  • the swivel axis 26 which is offset radially from the center of the pitch circle of the cylinder bores 14, the swash plate 5 is acted upon by the oil pressure pistons 16 and the force of the compression spring 20 on its right side in FIG. 1 more than on its left side and is acted upon on it 2 in the fully pivoted position.
  • the adjustment of the axial piston pump to a lower delivery volume up to the zero position with zero delivery shown in FIG. 1 takes place by applying force to the adjusting device 31 on the housing base 7.
  • the swash plate 5 pivots counterclockwise about the effective pivot axis 26, as indicated by the arrow V in FIG. 4.
  • a radial force component directed to the left in FIG. 4 is exerted on the swivel hemispheres 27 by the forced guides 33 via the swash plate 5 and this or the effective swivel axis 26 is thus subjected to a movement RE along the guides 29 with a sense of direction of the radial movement component R of the swashplate active surface 19 in the opposite direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP90122886A 1989-12-20 1990-11-29 Axialkolbenmaschine in Schrägscheibenbauweise Expired - Lifetime EP0433730B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3942189 1989-12-20
DE3942189A DE3942189C1 (ja) 1989-12-20 1989-12-20

Publications (2)

Publication Number Publication Date
EP0433730A1 EP0433730A1 (de) 1991-06-26
EP0433730B1 true EP0433730B1 (de) 1994-02-23

Family

ID=6395946

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90122886A Expired - Lifetime EP0433730B1 (de) 1989-12-20 1990-11-29 Axialkolbenmaschine in Schrägscheibenbauweise

Country Status (3)

Country Link
US (1) US5095807A (ja)
EP (1) EP0433730B1 (ja)
DE (2) DE3942189C1 (ja)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2626292B2 (ja) * 1991-03-30 1997-07-02 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
JPH05126029A (ja) * 1991-10-31 1993-05-21 Toyota Autom Loom Works Ltd 可変容量ピストンポンプ
US5251536A (en) * 1992-01-15 1993-10-12 Caterpillar Inc. Axial piston pump with off-center pivot
US5253576A (en) * 1992-02-07 1993-10-19 Bethke Donald G Swashplate assembly for an axial piston pump
US5364232A (en) * 1992-03-03 1994-11-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US5304042A (en) * 1992-04-10 1994-04-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
EP0697076B1 (en) * 1993-05-07 2001-02-21 Whisper Tech Limited Wobble yoke assembly
KR970002532B1 (ko) * 1993-12-30 1997-03-05 재단법인 한국기계연구원 사판식 유압모터의 변속기구
GB2287069B (en) * 1994-03-02 1997-10-22 Kubota Kk Swash plate type hydraulic motor switchable between high speed and low speed
JP3874308B2 (ja) * 1994-10-18 2007-01-31 株式会社小松製作所 斜板式ピストンポンプ・モータの斜板角度変更装置
US6027250A (en) * 1998-08-21 2000-02-22 The Torrington Company Roller bearing segment for swashplates and other limited-oscillation applications
DE10035630C1 (de) * 2000-07-21 2002-03-14 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit einer Rückzugeinrichtung
JP2004027862A (ja) * 2002-06-21 2004-01-29 Honda Motor Co Ltd 膨張機
US20050061143A1 (en) * 2003-01-28 2005-03-24 Koelzer Robert L. Modular swash plate compressor
US6883416B2 (en) * 2003-01-28 2005-04-26 Haldex Brake Corporation Swash plate containment assembly
DE10360452B3 (de) * 2003-12-22 2005-09-08 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit fixierbarem Gleitstein an der Schrägscheibe
DE102007048316B4 (de) * 2007-10-09 2010-05-27 Danfoss A/S Hydraulische Axialkolbenmaschine
FI20080053A0 (fi) * 2007-12-12 2008-01-22 Wallac Oy Laite ja menetelmä optisen komponentin paikan sovittamiseksi
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
CN104884796B (zh) * 2012-12-26 2017-03-15 纳博特斯克有限公司 斜板式液压马达或者斜板式液压泵
CA2913062C (en) * 2013-05-22 2020-06-02 Hydac Drive Center Gmbh Axial piston pump having a swash-plate type construction
DE102014219365A1 (de) * 2014-09-25 2016-03-31 Robert Bosch Gmbh Schrägscheibenmaschine

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GB1010652A (en) * 1961-01-06 1965-11-24 Council Scient Ind Res Improvements in swash plate type hydraulic pumps or motors
DE1232026B (de) * 1963-10-25 1967-01-05 Linde Ag Einrichtung zum Verstellen einer Axialkolbenmaschine
GB1303091A (ja) * 1970-08-29 1973-01-17
US3733963A (en) * 1971-03-29 1973-05-22 Abex Corp Method and apparatus for controlling displacement of a variable volume pump or motor
US4077269A (en) * 1976-02-26 1978-03-07 Lang Research Corporation Variable displacement and/or variable compression ratio piston engine
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FR2505398A1 (fr) * 1981-05-11 1982-11-12 Brille Maurice Embiellage pour une machine volumetrique a barillet
US4581980A (en) * 1984-05-23 1986-04-15 Brueninghaus Hydraulik Gmbh Hydrostatic axial piston machine with swivelling inclined disc
US4683804A (en) * 1985-01-18 1987-08-04 Taiho Kogyo Kabushiki Kaisha Swash plate type compressor shoe
DE3733083A1 (de) * 1987-09-30 1989-04-13 Linde Ag Verstellbare axialkolbenmaschine in schraegscheibenbauweise
DE3743125A1 (de) * 1987-12-18 1989-07-06 Brueninghaus Hydraulik Gmbh Axialkolbenpumpe
JPH0633769B2 (ja) * 1988-04-20 1994-05-02 本田技研工業株式会社 可変容量式圧縮機における始動時の容量設定装置
JPH0697034B2 (ja) * 1988-06-07 1994-11-30 松下電器産業株式会社 可動斜板式コンプレッサ

Also Published As

Publication number Publication date
DE59004684D1 (de) 1994-03-31
DE3942189C1 (ja) 1991-09-05
US5095807A (en) 1992-03-17
EP0433730A1 (de) 1991-06-26

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