EP2024638A1 - Machine à piston axial avec appui hydrostatique du serre-flan - Google Patents

Machine à piston axial avec appui hydrostatique du serre-flan

Info

Publication number
EP2024638A1
EP2024638A1 EP07725379A EP07725379A EP2024638A1 EP 2024638 A1 EP2024638 A1 EP 2024638A1 EP 07725379 A EP07725379 A EP 07725379A EP 07725379 A EP07725379 A EP 07725379A EP 2024638 A1 EP2024638 A1 EP 2024638A1
Authority
EP
European Patent Office
Prior art keywords
axial piston
sliding
piston machine
machine according
pressure
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Withdrawn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
EP07725379A
Other languages
German (de)
English (en)
Inventor
Rainer Stölzer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP2024638A1 publication Critical patent/EP2024638A1/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • 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
    • F01B3/0082—Details
    • F01B3/0085—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0602—Component parts, details
    • F03C1/0605—Adaptations of pistons
    • 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

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • the housing interior comprises a leakage space and a
  • DE 196 01 721 A1 discloses a weight-optimized, multi-part sliding shoe which is suitable for slidingly supporting the pistons of an axial or radial piston machine against an impact force. on a wobble, oblique or SchiefScheibe trained sliding surface is used.
  • the shoe includes a support body connected to the associated piston and a slide member abutting the sliding surface.
  • the shoe is made of materials that allow weight reduction of the shoe, so that the forces acting on the shoe centrifugal forces are reduced. As a result, the axial piston machine can be operated at an increased speed.
  • Lubricating film is formed, which is formed by the fact that a prevailing in a pressure chamber under the sliding shoes pressure over a connecting throttle a pressure which is exerted by the hold-down on the sliding shoes, partially compensated.
  • Fig. 1 shows an embodiment of a
  • Fig. 2 is a fragmentary view of a piston with shoe from an embodiment of an inventively designed axial piston machine
  • FIG. 3 shows a detail from FIG. 2 in the region designated III in FIG. 2.
  • Fig. 1 shows a better understanding of the measures according to the invention, first in a sectional view of an axial piston machine in Swash plate design with adjustable displacement volume and a current direction according to the prior art.
  • the axial piston machine comprises in a known manner as essential components a hollow cylindrical housing 1 with a frontally open end, which is in Fig. 1 above, a fixed to the housing 1, the open end occlusive terminal block 2, a lifting or swash plate 3, a control body 4th , a drive shaft 5, a cylinder drum 6. Further, in this embodiment, an optional cooling circuit 7 is provided.
  • the swash plate 3 is formed as a so-called pivoting cradle with a semi-cylindrical cross-section and is supported with two mutually spaced parallel to the pivot direction bearing surfaces under hydrostatic discharge to two correspondingly shaped bearing shells 8, which are fixed to the inner surface of the terminal block 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.
  • a positioning device 13 accommodated in a bulge of the cylindrical housing wall 12 engages over an arm 14 of the swashplate 3 extending in the direction of the connection block 2 and serves to pivot the same about a pivot axis perpendicular to the pivoting direction.
  • the control body 4 is fixed to the housing interior facing the inner surface of the terminal block 2 and provided with two through openings 15 in the form of kidney-shaped control slots, which are connected via a pressure channel 16D or suction channel 16S in the terminal block 2 to a pressure and suction line, not shown are.
  • the pressure channel 16D has a smaller flow cross-section than the suction channel 16S.
  • the housing interior facing and spherical Trained control surface of the control body 4 serves as a bearing surface for the cylinder drum. 6
  • the drive shaft 5 protrudes through a through hole in the housing end wall 9 in the housing 1 and is by means of a bearing 17 in this through hole and by means of another bearing 18 in a narrower bore portion of an end extended blind bore 19 in the terminal block 2 and one closer to this Bore portion adjacent region of a central through hole 20 in the control body 4 rotatably mounted.
  • the drive shaft 5 passes through in the interior of the housing 1 also has a central through hole 21 in the swash plate 3, the diameter of which is dimensioned according to the largest swing deflection of the swash plate or 3, and a central through hole in the cylinder drum 6 with two bore sections.
  • One of these bore sections is integrally formed on the cylinder drum 6, via the
  • Swash plate 3 facing end face 22 protruding sleeve-shaped extension 23 is formed, via which the cylinder drum 6 by means of a splined connection 24 rotatably connected to the drive shaft 5 is connected.
  • the remaining bore portion is formed with a conical shape. It tapers from its cross section of largest diameter near the first bore section to its cross section of smallest diameter near the control body 4 adjacent end face 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 25th designated .
  • the cylinder drum 6 has generally axially extending, stepped cylinder bores 26 which are arranged uniformly on a pitch circle coaxial to the drive shaft axis, on the cylinder drum end face 22 directly and on the control body 4 facing Zylindertrommel. Storage area via mouth channels 27 on the same pitch circle as the control slots open. In each of the cylinder drum end face 22 directly opening cylinder bore portions of larger diameter a bushing 28 is used.
  • the cylinder bores 26 including the liners 28 are referred to herein as cylinders.
  • pistons 29 are provided at their the swash plate or lifting disc 3 facing ends with ball heads 30, which are mounted in sliding blocks 31 and hydrostatically supported on a sliding surface 32 of the swash plate or lifting disc 3.
  • Each slide shoe 31 is provided on its the lifting disc 3 facing sliding surface, each with a pressure pocket, not shown in Fig. 1, which is connected via a through hole 33 in the shoe 31 to a stepped axial passage 34 in the piston 29 and in this way with the piston 29th in the cylinder bore 26 delimited working space of the cylinder is connected.
  • each axial passage 34 is in the region of the associated ball head 30 a
  • An axially displaceable by 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 contact with the lifting disc.
  • the axial piston machine is intended for operation with oil as a fluid.
  • the cylinder drum 6 is rotated together with the piston 29 in rotation. If the swashplate 3 is pivoted into an inclined position relative to the cylinder drum 6 by actuation of the adjusting device 13, then 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 orifice channels 27, the control slots 15 and the pressure and suction channel 16 D and 16 S done.
  • each piston 29 pressure oil from the respective cylinder 26, 28 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, which as hydrostatic Camp serves for the latter. 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.
  • Axial piston machines of this type have the disadvantage that the sliding shoes 31, irrespective of whether they are ball-shaped or dome-shaped sliding shoes 31, essentially act on the downholder 36 acted upon by the spring 35 with a mechanical pretension be pressed against the sliding disk 32 of the swash plate 3.
  • the contact point of the two parts is subject to a choice of good sliding and surface qualities of a mechanical friction, especially since the support surface should be kept as small as possible from a structural point of view, so that the
  • a pressure chamber 40 located below the sliding block 31 in the region of a relief surface 41 of the slide shoe 31 is formed at least one connection throttle 43 to one in the bearing surface on the hold-36.
  • the piston 29 is formed in the embodiment of a hollow cylinder with a recess 45.
  • the piston 29 has an integrally formed ball head 44, which in the
  • Fig. 3 is a highly schematic of a section of the shoe 31 is shown.
  • at least one bore 51 is provided, which has a
  • Has diameter D which is dimensioned relative to a gap d between a support bar 49 and the slide shoe 31 so that by a suitable choice of Ratio D / d of the pressure acting on the hold 36 is adjustable.
  • the inventively designed axial piston machine is thus characterized by a hydrostatic relief of the contact surfaces of the sliding blocks 31 on the hold-36, which is characterized mainly in lower manufacturing costs of the sliding partner, since the sliding blocks 31 and the hold-36 can be made due to the discharge of materials, which no longer have to be optimized with regard to the sliding properties. This also results in advantages in terms of the production of sliding partners or their strength.
  • Downholder 36 are transmitted without friction losses on the sliding blocks 31, whereby the reliability of the axial piston machine is improved.
  • the wear between the sliding blocks 31 and the hold-down 36 can also be reduced.
  • the invention is not limited to the illustrated embodiments, but also suitable for use in other types of axial piston machines. All features of the invention can be combined with one another as desired.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Machine à piston axial comprenant un boîtier (1) qui accueille une plaque (3) de levage ainsi qu'un tambour (6) cylindrique logé de manière à pouvoir tourner, comportant des cylindres (26, 28) et des pistons (29) pouvant effectuer un mouvement de va-et-vient à l'intérieur de ceux-ci, dont les extrémités faisant saillie hors des cylindres (26, 28) s'appuient sur la plaque (3) de levage par le biais d'une surface (31) de glissement d'une plaque (32) de glissement, ainsi qu'un serre-flan (36) par lequel la surface (31) de glissement est maintenue appliquée contre la plaque (32) de glissement. Une pression qui règne dans une chambre (40) de compression sous les patins (31) de glissement compense partiellement une pression exercée par le serre-flan (36) sur le patin (32) de glissement par le biais d'un obturateur (43) de liaison.
EP07725379A 2006-06-02 2007-05-18 Machine à piston axial avec appui hydrostatique du serre-flan Withdrawn EP2024638A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006025989 2006-06-02
DE102006046128A DE102006046128A1 (de) 2006-06-02 2006-09-28 Axialkolbenmaschine mit hydrostatischer Auflage des Niederhalters
PCT/EP2007/004471 WO2007140868A1 (fr) 2006-06-02 2007-05-18 Machine à piston axial avec appui hydrostatique du serre-flan

Publications (1)

Publication Number Publication Date
EP2024638A1 true EP2024638A1 (fr) 2009-02-18

Family

ID=38521338

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07725379A Withdrawn EP2024638A1 (fr) 2006-06-02 2007-05-18 Machine à piston axial avec appui hydrostatique du serre-flan

Country Status (7)

Country Link
US (1) US8167580B2 (fr)
EP (1) EP2024638A1 (fr)
JP (1) JP4979766B2 (fr)
KR (1) KR20090014332A (fr)
CN (1) CN101460741B (fr)
DE (1) DE102006046128A1 (fr)
WO (1) WO2007140868A1 (fr)

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Publication number Priority date Publication date Assignee Title
US9140244B2 (en) * 2011-08-31 2015-09-22 Caterpillar Inc. Piston pump with cam actuated valves
US10309380B2 (en) 2011-11-16 2019-06-04 Ocean Pacific Technologies Rotary axial piston pump
DE102013210416A1 (de) * 2013-06-05 2014-12-11 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine und Rückhalteplatte
JP6275502B2 (ja) * 2014-02-12 2018-02-07 川崎重工業株式会社 液圧回転装置のシューおよび液圧回転装置
US10094364B2 (en) 2015-03-24 2018-10-09 Ocean Pacific Technologies Banded ceramic valve and/or port plate
CN105201816B (zh) * 2015-09-07 2017-03-22 福州大学 一种斜盘式柱塞泵的缸体自冷却结构
CN105484684B (zh) * 2015-12-31 2018-06-01 中国石油天然气集团公司 柱塞式岩屑举升装置及举升方法
JP6854161B2 (ja) * 2017-03-16 2021-04-07 日立建機株式会社 斜板式液圧回転機械
JP6854160B2 (ja) * 2017-03-16 2021-04-07 日立建機株式会社 斜板式液圧回転機械
KR102368496B1 (ko) * 2017-07-31 2022-03-02 현대모비스 주식회사 전자제어식 브레이크 시스템용 펌프장치
DE102018205446A1 (de) * 2018-04-11 2019-10-17 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
CN109236597A (zh) * 2018-11-08 2019-01-18 四川航天烽火伺服控制技术有限公司 一种滑靴柱塞组件及一种柱塞泵
CN109611326A (zh) * 2019-01-23 2019-04-12 邓红革 一种带阻尼孔及均压环槽柱塞泵用柱塞

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GB913549A (fr) * 1900-01-01
JPS61118566A (ja) * 1984-11-14 1986-06-05 Honda Motor Co Ltd 斜板型油圧装置
JPS63150475A (ja) * 1986-12-12 1988-06-23 Honda Motor Co Ltd 斜板式油圧装置に於けるシユ−構造
DE3723988A1 (de) * 1987-07-20 1989-02-09 Hydromatik Gmbh Axialkolbenmaschine, deren kolben als stufenkolben ausgebildet sind
JPH0733820B2 (ja) * 1988-09-12 1995-04-12 川崎重工業株式会社 斜板式ピストンポンプモータ
DE4423023C2 (de) * 1994-06-30 1998-07-09 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit einem Kühlkreislauf für die Zylinder und Kolben
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US6406271B1 (en) * 1999-05-06 2002-06-18 Ingo Valentin Swashplate type axial-piston pump
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Also Published As

Publication number Publication date
US8167580B2 (en) 2012-05-01
CN101460741B (zh) 2011-09-28
CN101460741A (zh) 2009-06-17
JP4979766B2 (ja) 2012-07-18
KR20090014332A (ko) 2009-02-10
JP2009539009A (ja) 2009-11-12
DE102006046128A1 (de) 2007-12-06
US20090129949A1 (en) 2009-05-21
WO2007140868A1 (fr) 2007-12-13

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