EP1272735A1 - Machine a piston radiaux - Google Patents

Machine a piston radiaux

Info

Publication number
EP1272735A1
EP1272735A1 EP01927816A EP01927816A EP1272735A1 EP 1272735 A1 EP1272735 A1 EP 1272735A1 EP 01927816 A EP01927816 A EP 01927816A EP 01927816 A EP01927816 A EP 01927816A EP 1272735 A1 EP1272735 A1 EP 1272735A1
Authority
EP
European Patent Office
Prior art keywords
radial piston
control
piston machine
machine according
sections
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
EP01927816A
Other languages
German (de)
English (en)
Other versions
EP1272735B1 (fr
Inventor
Chris Shrive
Sinclair SUC Design Ltd. Cunningham
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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
Priority claimed from DE10033264A external-priority patent/DE10033264A1/de
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1272735A1 publication Critical patent/EP1272735A1/fr
Application granted granted Critical
Publication of EP1272735B1 publication Critical patent/EP1272735B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders

Definitions

  • the invention relates to a radial piston machine according to the preamble of patent claim 1.
  • a radial piston machine is known from DE 40 049 32 C2, in which a cylinder block with a plurality of cylinder spaces arranged in the radial direction is rotatably mounted in a housing. A piston is guided in each cylinder chamber, the end section protruding from the cylinder block is supported on a cam ring. This cam ring has a large number of control cams via which the pistons are radially displaced when the cylinder block rotates.
  • inlet and return channels for pressure medium are formed, which can alternately be overlapped with control openings in the cylinder block, via which the pressure medium supply and discharge to and from the cylinder chambers can be controlled.
  • control openings in the cylinder and the orifice cross sections in the housing are designed with a circular cross section.
  • a disadvantage of such a solution is that the connection to the cylinder chambers is opened or closed comparatively slowly due to the circular control cross sections, so that flow losses can occur.
  • EP 0 263 218 B1 overcome solution in which the control cross sections are not circular but approximately trapezoidal.
  • the side faces of this Trapezoidal cross sections can be arched inwards or flat.
  • the object of the invention is to create a radial piston machine which is subject to minimal flow losses and can be produced with minimal manufacturing outlay.
  • the openings for controlling the pressure medium supply and discharge are designed with curved end faces, with end faces being understood to mean the peripheral surface sections lying inside or outside in the radial direction.
  • curved end faces can be produced much more easily than the straight-line end face sections known from EP 0 263 218 A1, so that the manufacturing outlay is minimized.
  • Such a control cross section can be adjusted by extending the control opening in the radial direction without requiring an increase in the width (transverse to the radial direction).
  • the radius of curvature of the radially inner end face section is preferably made smaller than that of the radially outer end face section.
  • the control cross section could only be enlarged by increasing the diameter.
  • the control breakthroughs and the mouth cross sections are preferably designed with zero overlap, the maximum width of the control breakthroughs and mouth cross sections is limited, so that the bore diameter cannot be increased arbitrarily in the known solution.
  • the end face sections each have a constant radius of curvature so that they can be formed by bores. This enables the end face sections to be formed by two through holes.
  • the manufacture of the openings is particularly simple if the two bores overlap one another, so that the openings can be made solely by forming the two bores and then have an approximately eight-shaped cross section.
  • the curved end faces can be connected to one another via tangential surfaces.
  • the point of intersection of the two tangential surfaces lies in the axis of symmetry of the control cross section which tapers inwards in the radial direction.
  • the manufacture is particularly simple if the geometry of the control openings on the cylinder block side and the mouth cross sections on the housing side are selected identically. As already mentioned above, it is preferred that the mouth cross-sections and the control breakthroughs are designed with zero overlap with one another, so that the connection to the cylinder spaces is opened and closed as quickly as possible.
  • the manufacture of the control breakthroughs and the mouth cross-sections can be further simplified if they are each formed in a control disk which is attached to the cylinder block or to the housing.
  • FIG. 1 shows a cross section through a radial piston engine
  • FIG. 2 shows a detailed illustration of a control disk for controlling the pressure medium supply and discharge to cylinder spaces of the radial piston machine
  • FIG. 3 geometrical details of a control breakthrough of the control disk from FIG. 2;
  • FIG. 4 shows a simplified version of a control breakthrough for a control disk according to FIG. 2 and FIG.
  • FIGS. 5 and 6 further simplified versions of a tax breakthrough.
  • FIG. 1 shows a greatly simplified sectional view of a radial piston engine 1, which is constructed according to the multi-stroke principle.
  • This radial piston motor 1 has a housing 2 to which a cam ring 4 is screwed.
  • An output shaft 6 is mounted within the housing 2 and is connected via an external toothing to a cylinder block 8 designed as a rotor.
  • eight cylinder bores 10 are formed in the cylinder block 8, in each of which a piston 12 is guided radially displaceably.
  • a cylinder space 16 is delimited, into which pressure medium can be fed.
  • a roller 18 is mounted on the end section of each piston 12 that is distant from the cylinder space 16, and these rollers roll on a cam 20 of the cam ring 4 during the rotational movement of the cylinder block 8.
  • control cam 20 is designed with 6 radially projecting control cams 22.
  • the pistons 12 are moved radially inward in the direction of their inner dead center.
  • a valley 24 is formed between two adjacent control cams 22, so that the pistons 12 are at the apex of the valleys 24 at their outer dead center, in which the cylinder space has its maximum volume.
  • Each of the cylinder spaces 16 is assigned a control opening 26 formed in the cylinder block 8, through which the pressure medium is supplied or removed depending on the piston position.
  • eight control breakthroughs 26 are distributed on a pitch circle on the circumference in accordance with the number of pistons.
  • Inlet and outlet channels 32, 34 are formed in this control housing 30, which are also only indicated by dashed lines in the illustration according to FIG.
  • the number of control cams 22 six inlet channels 32 and six outlet channels 34 each open at the end, which are alternately evenly distributed over a pitch circle, the diameter of which corresponds to that of the pitch circle of the control cross sections 26. speaks.
  • the mouth cross sections of the inlet and outlet channels 32, 34 which are set at 45 ° to the horizontal or vertical, are covered by the control openings 26 shown with a solid line.
  • the inlet channels are open to a first ring channel which is located radially between the control housing 30 and the housing 2 and is connected to an inlet connection on the housing 2, and the outlet channels 34 are open to a second ring channel which is axially spaced from the first ring channel , is also located radially between the control housing 30 and the housing 2 and is connected to a drain connection on the housing 2.
  • control openings 26 and / or the mouth cross-sections of the inlet and outlet channels 32, 34 can be axial bores in the cylinder block 8 or in the control housing 30, which is only indicated, or - similarly to those in EP 0 263 218 AI mentioned in the introduction
  • the exemplary embodiments described - are located in control disks which are placed on the cylinder block 8 or the control housing and through which in each case only the front mouth areas of the assigned channels are formed.
  • Such control disks forming the mouth cross-sections are easier to produce than bores or cutouts in the housing 2 or in the cylinder block 8.
  • FIGS. 2 and 3 show the geometrical relationships of a control breakthrough 26 and the associated opening cross section of an inlet and an outlet channel 32, 34.
  • the mouth cross sections 36, 38 of the channels 32 and 34 as well as the control openings 26 are designed with an identical geometry, which is described with reference to FIG. 3.
  • the end face sections 40, 42 arranged diametrically to one another in the radial direction are each designed with a radius of curvature r2 or ri, the radius of curvature r2 of the radially outer end face section 40 being greater than the radius of curvature r ⁇ of the radially inner end face section.
  • both end faces 40, 42 can be designed with identical radii r.
  • Such an opening 26 is extremely simple to produce, since, for example, the two end face sections 42, 40 can be formed by bores, and then the tangential surfaces 44,
  • 46 can be manufactured by milling or the like.
  • the geometries and the distance between two adjacent mouth cross-sections 36, 38 are selected such that a control opening 26 with zero overlap can be arranged in between in the relative position shown.
  • the side faces 44, 46 of the control opening 26 are arranged in the axial direction in alignment with the adjacent side faces of the adjacent mouth cross sections 36, 38. That means that in this relative position there is neither a pressure medium supply nor a pressure medium discharge to or from the assigned cylinder space 16.
  • FIG. 4 shows a simplified exemplary embodiment, in which the production outlay for the control breakthroughs 26 or the mouth cross sections 36, 38 is further minimized compared to the previously described exemplary embodiment.
  • the end face sections 40, 42 are formed by two bores with the radius r ⁇ and T2, similarly to the previously described exemplary embodiment.
  • the axial distance d between the two bores is less than the sum r ⁇ + r2, so that the two bores overlap.
  • the result is an approximately eight-shaped mouth cross section, the inwardly projecting side surfaces not being reworked as in the exemplary embodiment described above.
  • the simplified manufacture is purchased with a slower opening and closing of the inlet and outlet channels 32, 34.
  • FIGS. 5 and 6 show two further variants of a tax breakthrough 26, which is even easier to produce than the previously described solutions.
  • the overlap of the two holes requires that the distance d is smaller than the dimension 2 r ⁇ (2 r 2 ).
  • This variant can be produced in a simple manner, for example, by drilling, with no reclamping of the drill as in the exemplary embodiment shown in FIG. 4 being necessary.
  • the distance d between the two bore centers is greater than the sum of the two radii 2 r ⁇ (2 r 2 ), so that there is no overlap area.
  • the two bore sections are then connected, as in the embodiment shown in FIG. 3, by tangentially extending side surfaces 44, 46, so that there is practically an elongated hole whose width is equal to the diameter r ⁇ _. That is, In the variants shown in FIGS. 5 and 6, the control breakthroughs 26 are therefore not youthful in the radial direction.
  • cross sections described above can also be produced by machining processes other than drilling, such as milling, wire or die sinking EDM.
  • the area of the opening cross sections can be adapted to different requirements by a suitable choice of the distance d between the end face sections, the bore diameter or diameters being practical remain unchanged so that zero coverage is guaranteed.
  • a radial piston machine with a plurality of radial pistons, each guided in a cylinder space, the cylinder spaces being connectable to supply and discharge channels for pressure medium via control breakthroughs.
  • the mouth cross sections of the control breakthroughs and the inlet and outlet channels are provided with curved end face sections.

Landscapes

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

Abstract

L'invention concerne une machine à pistons radiaux comprenant plusieurs pistons radiaux guidés dans les différentes chambres de cylindre, reliées par des passages de guidage avec des canaux d'admission et d'évacuation de fluide sous pression. Les sections d'ouverture desdits passages de guidage et des canaux d'admission et d'évacuation sont pourvues de parties de surfaces courbes.
EP01927816A 2000-04-11 2001-03-27 Machine a piston radiaux Expired - Lifetime EP1272735B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10017951 2000-04-11
DE10017951 2000-04-11
DE10033264A DE10033264A1 (de) 2000-04-11 2000-07-10 Radialkolbenmaschine
DE10033264 2000-07-10
PCT/EP2001/003480 WO2001077495A1 (fr) 2000-04-11 2001-03-27 Machine a piston radiaux

Publications (2)

Publication Number Publication Date
EP1272735A1 true EP1272735A1 (fr) 2003-01-08
EP1272735B1 EP1272735B1 (fr) 2004-11-10

Family

ID=26005271

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01927816A Expired - Lifetime EP1272735B1 (fr) 2000-04-11 2001-03-27 Machine a piston radiaux

Country Status (3)

Country Link
US (1) US6843162B2 (fr)
EP (1) EP1272735B1 (fr)
WO (1) WO2001077495A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2892775B1 (fr) * 2005-10-27 2010-11-05 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux avec refroidissement du bloc-cylindres
BR112012033399A2 (pt) * 2010-07-06 2017-12-05 Sydney Oliver Ampuero Larry motor de combustão interna
US8997627B2 (en) * 2011-04-29 2015-04-07 Paul Michael Passarelli Thermal engine with an improved valve system
FR3030645B1 (fr) * 2014-12-17 2019-10-11 Poclain Hydraulics Industrie Appareil hydraulique a pistons radiaux
CN105508166B (zh) * 2016-01-26 2018-02-06 机械科学研究总院 动外壳式空气弹簧径向柱塞泵
CN112576469B (zh) * 2020-11-16 2022-12-16 中国航发西安动力控制科技有限公司 内曲线径向柱塞马达的柱塞滚柱

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE263218C (fr) *
DE900530C (de) 1951-06-30 1953-12-28 Heinrich Ebert Dr Ing Steuerspiegel fuer die Kolbentrommel hydraulischer Axialkolbenmaschinen mit ungerader Kolbenanzahl
FR1594838A (fr) * 1967-11-23 1970-06-08
US3511131A (en) * 1968-06-24 1970-05-12 Deere & Co Hydraulic motor
DE2444040A1 (de) 1974-09-14 1976-04-01 Danfoss As Radialkolbenmaschine
DE3434350A1 (de) 1984-09-19 1986-03-27 A. Friedr. Flender Gmbh & Co Kg, 4290 Bocholt Hydrostatische radialkolbenmaschine
FR2587761B1 (fr) * 1985-09-20 1988-01-15 Poclain Hydraulics Sa Mecanisme hydraulique comportant des glace et contre-glace de distribution du fluide
FR2588616B1 (fr) * 1985-10-16 1988-01-08 Poclain Hydraulics Sa Mecanisme, moteur a pompe, a au moins deux cylindrees actives distinctes.
DE3668038D1 (de) * 1986-10-08 1990-02-08 Poclain Hydraulics Sa Fluessigkeitsmechanismus mit fluidverteilscheibe und gegenscheibe.
FI104014B1 (fi) * 1994-05-18 1999-10-29 Valmet Voimansiirto Oy Radiaalimäntähydraulimoottori ja menetelmä radiaalihydraulimoottorin säätämiseksi
SE506582C2 (sv) * 1996-04-03 1998-01-12 Kesol Production Ab Anordning vid en radialkolvmotor av rotationstyp

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0177495A1 *

Also Published As

Publication number Publication date
WO2001077495A1 (fr) 2001-10-18
US20030159578A1 (en) 2003-08-28
EP1272735B1 (fr) 2004-11-10
US6843162B2 (en) 2005-01-18

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