EP0180912A2 - Machine fluidique à pistons radiaux - Google Patents

Machine fluidique à pistons radiaux Download PDF

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Publication number
EP0180912A2
EP0180912A2 EP85113805A EP85113805A EP0180912A2 EP 0180912 A2 EP0180912 A2 EP 0180912A2 EP 85113805 A EP85113805 A EP 85113805A EP 85113805 A EP85113805 A EP 85113805A EP 0180912 A2 EP0180912 A2 EP 0180912A2
Authority
EP
European Patent Office
Prior art keywords
machine
longitudinal axis
mla
shaft section
radial piston
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
EP85113805A
Other languages
German (de)
English (en)
Other versions
EP0180912A3 (en
EP0180912B1 (fr
Inventor
Dieter Schneeweiss
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.)
G Duesterloh GmbH
Original Assignee
G Duesterloh 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 G Duesterloh GmbH filed Critical G Duesterloh GmbH
Publication of EP0180912A2 publication Critical patent/EP0180912A2/fr
Publication of EP0180912A3 publication Critical patent/EP0180912A3/de
Application granted granted Critical
Publication of EP0180912B1 publication Critical patent/EP0180912B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/0457—Controlling by changing the effective piston stroke
    • F03C1/046—Controlling by changing the effective piston stroke by changing the excentricity of one element relative to another element
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • 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
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/053—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders
    • F03C1/0538—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders the piston-driven cams being provided with inlets or outlets
    • 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
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • 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
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention is directed to a fluidic radial piston machine, in particular a hydraulic radial piston machine, according to the features in the preamble of claim 1.
  • a radial piston machine belongs to the prior art, which has an eccentric adjustment with hydraulically actuated adjusting pistons provided within the eccentric ring.
  • Such a design has proven itself wherever the eccentric ring could be dimensioned large enough due to the construction volume of the machine to accommodate adjusting pistons with a still satisfactory adjusting force.
  • it can only run reliably in the eccentricity end positions because the adjusting pistons cannot be fixed in intermediate positions. It is therefore a machine that can be switched in two stages.
  • Eccentric adjustments with continuously working adjusting pistons within an eccentric ring are known from DE-PS 26 54 526.
  • the stepless adjustability is therefore also limited: with stable intermediate positions to machine sizes, the volume (displacement volume of a radial piston motor, delivery volume of a radial piston pump) is limited to a minimum of approximately 500 cm 3 .
  • the invention has for its object to develop the hydraulic radial piston machine described in the preamble of claim 1 so that even with comparatively small sizes with a swallowing or delivery volume below about 500 cm 3, a continuous change in the swallowing or delivery volume can be ensured.
  • a longitudinal section of the machine shaft is now designed to be pivotable.
  • the pivoting is based on a force-actuated, translato- rically effective sliding member, the translatory force direction of which is converted into a radial force direction via the swivel arm gear arranged next to the common transverse plane of the working piston.
  • the adjustment mechanism is now next to the row of pistons. Consequently, the support member can now be made very small.
  • the support member shrinks to a size which allows radial piston machines with a swallowing or delivery volume below approximately 500 cm 3 to be continuously adjusted without difficulty.
  • claim 2 embody an embodiment in which no fixed connection is provided between the swivel link transmission and the hydraulic cylinder which can be acted upon on one side.
  • the hydraulic cylinder therefore does not need to be rotatable. Nevertheless, the return spring in the swivel link mechanism ensures that the swiveling shaft section is shifted into the longitudinal axis of the machine and thus swallows or swallows even when depressurized
  • a fixed connection of the double-acting hydraulic cylinder with the swivel link mechanism is provided.
  • a connection requires a rotatable connection between the hydraulic cylinder and the swivel link transmission.
  • This can e.g. B. the pivot axis between the piston rod and the compensating link.
  • the piston rod or the piston can also be rotatably supported, if necessary.
  • the piston rod space should always be acted upon by the pressure medium such that the pivotable shaft section is aligned in the longitudinal axis of the machine in the case of unpressurized working cylinders. This can also be brought about by a spring which is provided, for example, in the piston rod space.
  • the support member is arranged to be displaceable parallel to the machine longitudinal axis relative to the working piston. In this way, the fact is taken into account that the space hinge between the pivotable shaft section and the support member, when the shaft section changes in inclination to the machine longitudinal axis, travels an arcuate path which no longer runs in the common transverse plane of the central axes of the working pistons.
  • the pivotable shaft section itself is designed as a sliding member.
  • the telescopic cylinder can be acted upon on one side or on both sides. Since the cylinder housing also performs a pivoting movement about the articulation point on the axially non-displaceably mounted longitudinal section of the machine shaft, it is necessary to design the support member connected to the cylinder housing in such a way that the working pistons can be supported on the support member in a spatially articulated manner.
  • the support member can have spherical-segment-shaped surfaces, on which connecting rods connected in an articulated manner to the working pistons are supported.
  • the support member can also be used in the embodiments as described with reference to claims 2 to 4.
  • a force-actuated, translationally effective sliding member as has been previously described in the scope of a hydraulic cylinder that can be loaded on one or both sides.
  • the rigid or telescopic swivel shaft section passes through the abutment, which is designed, for example, in a disk or plate-like manner, that the abutment can be taken in the sense of rotation, - but it is still ensured that the shaft section in the abutment through- the desired radial relative displacement. can lead.
  • the angle between the pivot links is changed and in this way also the angle of inclination of the pivotable shaft section to the longitudinal axis of the machine.
  • the support member is shifted accordingly, thereby changing the swallowing or delivery volume.
  • the swivel link transmission can also have only a single swivel link, which is articulated on the one hand to the abutment and on the other hand to the end of the shaft section which can be pivoted out of the machine longitudinal axis.
  • This embodiment of a swivel link transmission is preferably used, for example, if the pivotable shaft section is designed as a hydraulic cylinder and a further hydraulic cylinder acts as a sliding member on the swivel link transmission, directly or indirectly. It can also be used with advantage if a further pivotable shaft section of a second row of pistons is also struck on the pivoting link. This can be a rigid or telescopic shaft section.
  • a compensating link is provided between the pivot link transmission and the hydraulic cylinder as a sliding member, which compensates for the spatial changes of the pivot link relative to the machine longitudinal axis.
  • the rotating abutment is arranged axially displaceable. This can be practiced both in an embodiment with only one row of pistons and in an embodiment with two rows of pistons.
  • the abutment itself forms the sliding link to a certain extent, the actuating means for displacing the sliding link being hydraulic, pneumatic, electrical or mechanical in nature.
  • the actuating means for displacing the sliding link being hydraulic, pneumatic, electrical or mechanical in nature.
  • this measure can be omitted if one of the shaft sections is designed to be telescopic.
  • Figures 1 to 6 show a schematic representation of various radial piston motors with swivel shaft adjustments.
  • the radial piston motor 1 illustrated in FIG. 1 comprises, for example, five working pistons 2, the central axes of which are arranged in a transverse plane QE common to the machine longitudinal axis MLA.
  • the working pistons 2 slide radially in working cylinders 3. They are supported on a supporting member 4 which is displaceable relative to the working pistons 2 parallel to the machine longitudinal axis MLA.
  • the support member 4 is connected via a space joint 5 to a rigid shaft section 6 which can be pivoted radially from the machine longitudinal axis MLA.
  • the end 9 of the pivotable shaft section 6 opening into the machine longitudinal axis MLA is hinged in space-like fashion to a longitudinal section 7 of the machine shaft 8 which rotates about the machine longitudinal axis MLA but is axially immovable.
  • the slot-like bushing 11 in the abutment 12 for the shaft section 6 is dimensioned such that the abutment 12 can be carried along perfectly in the direction of rotation by the shaft section 6 and the shaft section 6 can be radially displaced in the slot 11.
  • the pivot axis 15 runs at a distance next to the machine longitudinal axis MLA and perpendicular to this.
  • the swivel arm gear 14 comprises a further swivel arm 16 which is articulated on the one hand to a bracket 17 connected to the abutment 12 and on the other hand to the swivel arm 13.
  • Both the swivel axis 18 between the two swivel arms 13 and 16 and the swivel axis 19 between the bracket 17 and the swivel arm 16 extend next to the machine longitudinal axis MLA and perpendicular to it.
  • a slider 20 is further articulated, which is under the influence of a spring 21 arranged between the abutment 12 and the pivot axis 18.
  • the slider 20 is supported in an unconnected manner on a plunger 22 of a hydraulic cylinder 23 which can be acted upon on one side and whose longitudinal axis 24 coincides with the machine longitudinal axis MLA.
  • the return spring 21 presses the plunger 22 into the cylinder housing 25 and thus also shifts the shaft section 6 into the machine longitudinal axis MLA.
  • the swallowing volume is then zero.
  • the plunger 22 can now be pushed out, the pivotable shaft section 6 and thereby also the support member 4 being radially displaced via the slide 20 and the swivel link mechanism 14. In this way, the swallowing volume of the radial piston motor 1 can be varied continuously.
  • the hydraulic cylinder 23 which can be acted on on one side has been replaced by a hydraulic cylinder 26 which can be acted on on both sides.
  • the hydraulic cylinder 26 comprises a piston 27 with a piston rod 28, which is articulated via a compensating link 29 to a swivel link transmission 14 according to FIG.
  • the other components of this embodiment are designed in accordance with the embodiment of FIG. 1. A further explanation is therefore unnecessary.
  • the pivotable shaft section is designed as a hydraulically actuable telescopic cylinder 33.
  • the telescopic cylinder 33 can be acted on on one side or on both sides.
  • a support member 35 is attached to the housing 34 spherical segment-shaped surfaces.
  • Appropriately designed connecting rod shoes 36, which are articulated to the working pistons 2, are supported on these surfaces.
  • the end 9 of the shaft section 6 opening into the machine longitudinal axis MLA is connected in a spatially articulated manner to the axially immovable length section 7 of the machine shaft 8 rotating in the machine longitudinal axis MLA.
  • the telescopic longitudinal section 37 of the telescopic cylinder 33 passes through a disk-like abutment 38 which rotates about the machine longitudinal axis MLA, but is mounted immovably in the direction of the machine longitudinal axis MLA.
  • the abutment 38 has a slot 39 through which the telescopic part 37 passes so that the abutment 38 is carried in the direction of rotation and the telescopic part 37 can be displaced radially.
  • the abutment 38 forms part of a swivel arm gear 40 which has a swivel arm 41 which is connected on the one hand via a swivel axis 42 to a bracket 43 connected to the abutment 38 and on the other hand via a swivel axis 44 to the telescopic part 37 of the telescopic cylinder 33.
  • Both pivot axes 42 and 44 extend laterally next to the machine longitudinal axis MLA and perpendicular to it.
  • a bracket 45, to which a compensating link 46 is articulated, is fastened approximately in the middle of the swivel arm 41.
  • the other end section of the compensating link 46 is connected in an articulated manner via a joint 30 to a piston rod 28 of a hydraulic cylinder 26, as has been described, for example, with reference to FIG.
  • the hydraulic cylinder 26 forming the sliding member can also be acted upon mechanically by a spring 32 in the piston rod space 31 or hydraulically in the piston rod space 31 or, if appropriate, also in the piston space 47.
  • FIG. 4 shows an embodiment of a radial piston motor 2 ′ ′′ with two rows of working pistons 2.
  • An arrangement of the adjustment as shown in FIG. 3 is selected, but with the exception of the hydraulic cylinder 26.
  • This is in the embodiment of the figure 4 can be dispensed with, since the inclination of the telescopic cylinder 33 towards the longitudinal axis MLA of the machine can be changed via the swivel link mechanism 40 and thus the swallowing volume by appropriate loading.
  • FIG. 5 shows a radial piston motor 1 "" with a rigid pivotable shaft section 6 and a row of pistons according to the embodiments of FIGS. 1 and 2.
  • the end 10 of the shaft section 6 which is pivotable from the machine longitudinal axis MLA is coupled to a swivel arm gear 40, as has been explained with reference to FIG. 3.
  • the difference is further that the abutment 38 is now axially displaceable.
  • the actuating means required for this can be of a hydraulic, pneumatic, electrical or mechanical nature. It can be seen that by adjusting the abutment 38 parallel to the machine longitudinal axis MLA in the operating position with broken lines, the inclination of the pivotable shaft section 6 to the machine longitudinal axis MLA and thus the displacement volume of the radial piston motor 1 "" can be changed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
EP85113805A 1984-11-07 1985-10-30 Machine fluidique à pistons radiaux Expired EP0180912B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3440543 1984-11-07
DE3440543A DE3440543A1 (de) 1984-11-07 1984-11-07 Fluidische radialkolbenmaschine

Publications (3)

Publication Number Publication Date
EP0180912A2 true EP0180912A2 (fr) 1986-05-14
EP0180912A3 EP0180912A3 (en) 1987-04-15
EP0180912B1 EP0180912B1 (fr) 1989-04-12

Family

ID=6249634

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113805A Expired EP0180912B1 (fr) 1984-11-07 1985-10-30 Machine fluidique à pistons radiaux

Country Status (3)

Country Link
US (1) US4768421A (fr)
EP (1) EP0180912B1 (fr)
DE (1) DE3440543A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4122486A1 (de) * 1991-07-06 1993-01-07 Teves Gmbh Alfred Antriebsaggregat, insbesondere motor-pumpenaggregat fuer schlupfgeregelte bremsanlagen
DE10208586A1 (de) 2002-02-22 2003-09-11 Reinhard Sorg Antriebseinrichtung für eine Maschine, insbesondere Pumpe oder Motor
CN100482939C (zh) * 2003-12-15 2009-04-29 流体静力设计技术集团有限公司 液压马达/泵
US8413572B1 (en) 2006-11-22 2013-04-09 Westendorf Manufacturing, Co. Auto attachment coupler with abductor valve
FR2981703B1 (fr) * 2011-10-21 2013-11-22 Hydr Am Pompe hydraulique radiale a excentricite et debit variables

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR990841A (fr) * 1949-05-12 1951-09-26 Variateur de vitesse hydraulique automatique, progressif et asservi
GB962911A (en) * 1960-10-19 1964-07-08 Veb Zek Hydraulic control and compensating means for hydraulic pumps and motors
FR2472119A1 (fr) * 1979-12-18 1981-06-26 Wolff Rene Transmetteur mecanique de puissance a amplitude variable

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE525535C (de) * 1931-05-26 Hans Reisert & Co Akt Ges Kolbenpumpe mit regelbarer Foerdermenge
US1321086A (en) * 1916-10-03 1919-11-04 Hugo Centervall Variable-stroke pump.
DE380862C (de) * 1920-03-14 1923-09-13 Maschf Fluessigkeitsgetriebe
US1612883A (en) * 1923-12-24 1927-01-04 Leonadus C Porterfield Oil burner
FR641154A (fr) * 1926-10-01 1928-07-30 Pompe à piston à débit réglable
US3339460A (en) * 1965-05-07 1967-09-05 J C Birdwell Pressure fluid motor
US3492948A (en) * 1968-04-08 1970-02-03 Haviland H Platt Hydraulic pump/motor
DD69265A1 (fr) * 1968-05-29 1969-10-05
GB1385702A (en) * 1971-01-29 1975-02-26 Chamberlain Ind Ltd Hydraulic motors and the like
US3871268A (en) * 1972-12-30 1975-03-18 Shimazaki Mixing Equipment Co Combination pumping apparatus
DE2504693A1 (de) * 1975-02-05 1976-08-19 Tex Trans Inc Hydraulische kraftuebertragungs- und bremseinrichtung fuer fahrzeuge
DE2654526C3 (de) * 1976-12-02 1982-09-30 G. Düsterloh GmbH, 4322 Sprockhövel Hydrostatische Radialkolbenmaschine
JPS55146284A (en) * 1979-04-27 1980-11-14 Kayaba Ind Co Ltd Radial piston motor
DE3109706C2 (de) * 1981-03-13 1986-09-18 G. Düsterloh GmbH, 4322 Sprockhövel Volumenschaltbarer Hydromotor
US4548124A (en) * 1984-02-23 1985-10-22 Riva Calzoni S.P.A. Radial piston hydraulic motor with variable eccentricity

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR990841A (fr) * 1949-05-12 1951-09-26 Variateur de vitesse hydraulique automatique, progressif et asservi
GB962911A (en) * 1960-10-19 1964-07-08 Veb Zek Hydraulic control and compensating means for hydraulic pumps and motors
FR2472119A1 (fr) * 1979-12-18 1981-06-26 Wolff Rene Transmetteur mecanique de puissance a amplitude variable

Also Published As

Publication number Publication date
US4768421A (en) 1988-09-06
EP0180912A3 (en) 1987-04-15
DE3440543C2 (fr) 1989-05-03
EP0180912B1 (fr) 1989-04-12
DE3440543A1 (de) 1986-05-22

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