US3765252A - Hydraulic piston machine having radially disposed pistons - Google Patents

Hydraulic piston machine having radially disposed pistons Download PDF

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Publication number
US3765252A
US3765252A US00263755A US3765252DA US3765252A US 3765252 A US3765252 A US 3765252A US 00263755 A US00263755 A US 00263755A US 3765252D A US3765252D A US 3765252DA US 3765252 A US3765252 A US 3765252A
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US
United States
Prior art keywords
block
eccentric
axis
guide means
piston machine
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
US00263755A
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English (en)
Inventor
A Steiger
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Sulzer AG
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Sulzer AG
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Filing date
Publication date
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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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/062—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement the connection of the pistons with an actuating or actuated element being at the inner ends of the cylinders
    • 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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0644—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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0668—Supporting and guiding means for the piston
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated
    • 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
    • Y10T74/18248—Crank and slide

Definitions

  • ABSTRACT The block on which the radially disposed pistons bear is guided to rotate about the axis of the cam without rotating about its own axis in order to allow the hydrostatic pockets in the bottom of the pistons to be centrally located relative to the pistons. This avoids tilting of the pistons in their respective cylinders during a stroke.
  • Hydraulic piston machines have been known in which pistons are arranged radially and are provided with flat bearing surfaces transverse to their axes. Generally, the pistons have been reciprocated by means of an eccentric via a central block which has flat supporting surfaces cooperating with the bearing surfaces of the pistons. In addition, the bearing surfaces have been provided with pockets for a hydrostatic bearing arrangement.
  • a piston machine of this type has been described in copending U.S. patent applications Ser. No. 172,091 filed Aug. 16, 1971, now abancloned and Ser. No. 184,159 filed Sept. 27, 1971. This machine affords a compact construction which is robust and simple while at the same time providing for hydrostatic lubrication of the various machine parts in order to minimize friction and wear.
  • the .present invention is a further development of the piston machine according to the above two patent applications and is directed to an improvement in the hydrostatic lubrication of a piston machine of this kind.
  • a construction is obtained in which metal-to-metal contact of the parts and unsymmetric piston load of the machine outside its axis are avoided.
  • the piston machine is characterized by the fact that the central block is connected with a guide means which allows the block to move around the axis of the eccentric but prevents the block from revolving around its own axis.
  • the pockets for the hydrostatic bearings can be arranged centrally in each piston.
  • Each piston is consequently loaded by a force which passes through its axis without producing any tilting or bending movements, so that, practically, only insignificant guide forces result between the piston and the wall of the associated cylinder.
  • the guide means formed of two moving parts which are mounted in perpendicular relation to the eccentric axis.
  • One part is movably mounted on a casing of the machine so as to be guided in a plane, such as a vertical plane, perpendicular to the eccentric axis while the second part is guided in the first part at a right angle to this plane, i.e., in a horizontal plane, and is fixedly secured to the block.
  • the central block is disposed relative to the axis of the eccentric shaft to cause reciprocation of the pistons while at the same time being restrained from revolving about its own axis.
  • the guide means can be preferably locatedon an end face of the piston machine and dimensioned so that the external dimensions are essentially the same as those of the machine. A construction will consequently result which is supported on a large diameter on the periphery of the machine with corresponding small forces being produced as a result.
  • the mutually supporting areas of the parts of the guide means are provided with pockets for a hydrostatic bearing. These pockets are connected via connection bores with a duct of the machine for the pressure medium, the duct being under pressure at a corresponding direction of rotation.
  • the guide means can also be lubricated hydrostatically so that friction and wear therein are minimized.
  • the guide means is formed with at least one crank located outside the eccentric axis and frictionally connected with the eccentric shaft.
  • the crank which is connected with the block, carries out a rotary motion of the same phase and same eccentricity as the eccentric.
  • a construction of this kind is especially advantageous is cases where the piston machine must be provided with an output gearing.
  • This guide means preferably contains two gear wheels connected with the eccentric shaft and diametrically disposed to its axis. Each of these gear wheels has a crank with the arms of both cranks pointing in the same direction. The cranks are also connected pivotally with the block. With a construction of this kind, optimum guidance of the block with minimum play is obtained.
  • FIG. 1 illustrates a view taken on line I-l of FIG. 2 of a piston machine utilizing a guide means according to the invention
  • FIG. 2 illustrates a view taken on line IIII of FIG.
  • FIG. 3 illustrates a part section with a partial view of the machine shown in FIGS. 1 and 2 as viewed in the direction of the arrow X in FIG. 2;
  • FIG. 4 illustrates a view taken on line lV-IV of FIG. 5 of a modified guide means according to the invention.
  • FIG. 5 illustrates a view taken on line V-V of FIG. 4.
  • the piston machine comprises a ring-shaped cylinder block 1 containing cylinder bores 2 arranged radially of the axis of the block 1.
  • the cylinder bores 2 serve to guide pistons 3 therein which are each supported on flat surfaces 4 of a block 5.
  • the block 5 is mounted on an eccentric 6 of an eccentric shaft 7, or may be supported on a crankpin formed on a crankshaft (not shown).
  • the cylinder bores 2 are closed by cylinder covers 8.
  • Each piston 3 is provided with grooves 16 running in an axial direction of the piston 3. These grooves 16 lead from the front surface of each piston 3 to communicate with the cylinder chamber of the cylinder bore 2 and end in an intermediate area of the piston length.
  • the grooves 16 are positioned for cooperation with control ports 19 situated in the periphery of each cylinder bore 2 on either side of each groove 16.
  • the ports 19 are formed by the mouth of ducts 21 serving to supply and discharge pressure medium, respectively.
  • a hydrostatic lubrication pocket 43, communicating via bores 41, 42 with the cylinder chamber above the piston 3, is formed at the bottom end of the piston 3.
  • the bottom ends of the pistons 3 are also provided with flange-like projections 23 on one side to form a lever arm 24 which contains a guide slot.
  • This slot guides a stud 26 which is fixed to the block 5.
  • a guide shoe (not shown) may also be arranged between the stud 26 and the guide slot.
  • annular ducts 32, 33, 34 and 35 are fixed on either side of the cylinder block 1.
  • These ducts 32, 34 serve to discharge the pressure medium, while the other pair, i.e., ducts 33 and 35 serves to supply the pressure medium through the control ports (not shown) situated close to the control ports 19.
  • the annular ducts are connected with the associated control ports by means of pockets 36, 37.
  • the piston machine illustrated in FIGS. 1 to 3 is provided with a guide means containing two parts 50 and 51 which are movable perpendicularly to each other within a plane transverse to the axis of the eccentric 6.
  • part 50 is guided in a vertical direction on two projections 52 which are formed on cover 31.
  • part 50 is provided with corresponding gooves and as shown in FIG. 3, encloses the projections 52 so as to slide thereon.
  • Part 50 is also provided laterally with grooves in which arms of part 51 are movable horizontally.
  • Part 51 contains a ring-shaped area in the middle which is connected with the block by means of bolts 53.
  • bushings 54 are located between part 51 and block 5 to enclose the bolts 53. This results in a rigid connection of part 51 with block 5.
  • the bushings 54 which carry out a rotary motion together with the block 5, are located in recesses 55 of the lateral cover 31 which allow this motion.
  • Part 50 is held in an axial direction by means of threaded bolts 56 with flat heads screwed into the projections 52.
  • the threaded bolts 56 pass through slots 57 in part 50, so that the heads of the threaded bolts 56 prevent the part 50 from being separated from cover 31.
  • bolts 58 are screwed into the threaded bolts 56 to secure an end cap 60 over the guide parts 50, 51.
  • part 50 can move along the projections 52 in a vertical direction.
  • part 51 moves in part 50 in a horizontal direction. Both movements combined allow a rotary motion of part 51 and consequently also a rotary motion of the block 5 which encloses the eccentric 6 of the eccentric shaft 7.
  • the rotary motion of the block 5, i.e., the rotation of the axis of the block 5 about the axis of the eccentric shaft 7, guided by the guide means, allows each hydrostatic pocket 43 to be located centrally, i.e., axially, on a piston 3.
  • the block 5 is prevented from revolving around its axis, which would otherwise occur except for the guide means with parts 50 and 51.
  • part 50 is provided with hydrostatic lubrication pockets 61, 62 in the sliding surfaces as well as with symmetrically formed lubrication pockets 61' and 62'.
  • the lubrication pockets 61 and 62 are connected by means of bores 65 and 66 in the part 50 and projections 52 with a connection bore 67 in the projections 52 which lead into the duct 34 of the cover 31.
  • Lubrication pockets 61' and 62 communicate via bores 65 66' with connection bores 67 which lead into the duct 35 of the cover 31.
  • the respective loaded lubrication pockets are connected in this manner with the duct of the cover 31 which is under pressure. Hydrostatic lubrication of the guide means is consequently obtained, and friction and wear are thus reduced to a minimum.
  • the guide means with parts 50 and 51 is located on the end face of the piston machine.
  • the guide means can be dimensioned so that the external dimensions are essentially the same as those of the machine.
  • the bearing surfaces cooperating with the pockets 61 and 62 lie radially on a great radius. This results in a corresponding reduction of the bearing forces and consequently allows the block 5 to be guided accurately.
  • the hydraulic piston machine can alternatively be provided with a guide means which uses a reduction gearing having a gear wheel 102 with internal teeth mounted on a shaft 101.
  • the gear wheel 102 meshes with two gear wheels 103 which are pivoted on pins 104 fixed in the lateral cover 31.
  • the gear wheels 103 also mesh with toothing 105 of the eccentric shaft 7.
  • a mounting plate 106 with pivots 107 is fixed on pins 104 while gear wheels 108 meshing with the gear wheels 103 and having pins 110 are supported on pivots 107.
  • the pins 110 are pivoted in parts 111 which are firmly connected with the block 5.
  • both gear wheels 108 are arranged diametrically to the axis of the eccentric shaft 7.
  • the crank arms of the cranks formed by the two pins 110 point in the same direction as the eccentric of the eccentric shaft 7.
  • the crank arm of pins 110 is as large as the eccentricity of the eccentric 6, which is determined in FIG. 4, by the distance of the eccentric axis 112 from the axis 112' of the eccentric shaft 7.
  • cranks formed by the pins 110 would be sufficient to prevent the block from turning and to guide the block parallelly during the rotary motion, provided that the axis of this crank, as illustrated, lies outside the axis of the eccentric 112.
  • becuase two pins 110 are provided, the block 5 can be guided more accurately.
  • a hydraulic piston machine comprising a plurality of radially disposed pistons, each piston having a flat bearing surface at one end perpendicular to the longitudinal axis thereof and a pocket in said end within said bearing surface for a hydrostatic bearing;
  • each supporting surface being disposed in opposition to a respective bearing surface of a respective one of said pistons;
  • said guide means includes two parts, said parts being disposed in perpendicular relation to the axis of said eccentric, one of said parts being movably mounted in a first plane perpendicular to said axis of said eccentric and the second of said parts being guidably mounted in said one part for movement in a plane disposed at a right angle to said first plane, said second part being fixedly secured to said block to move therewith.
  • a hydraulic piston machine as set forth in claim 1 which further includes a shaft connected to said eccentric for rotating said eccentric and wherein said guide means includes at least one crank located outside the axis of said eccentric and frictionally connected to said shaft, said crank being connected with said block for carrying out a rotary motion of the same phase and said eccentricity as said eccentric.
  • said guide means further includes two gear wheels connected to said shaft in diametrically disposed relation to the axis of said shaft, and a crank mounted on each gear wheel and pivotally connected to said block, each crank having a crank arm disposed in the same direction as the other crank arm;

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US00263755A 1971-06-21 1972-06-12 Hydraulic piston machine having radially disposed pistons Expired - Lifetime US3765252A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH900771A CH539772A (de) 1971-06-21 1971-06-21 Hydraulische Kolbenmaschine mit radial angeordneten Kolben

Publications (1)

Publication Number Publication Date
US3765252A true US3765252A (en) 1973-10-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00263755A Expired - Lifetime US3765252A (en) 1971-06-21 1972-06-12 Hydraulic piston machine having radially disposed pistons

Country Status (4)

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US (1) US3765252A (de)
CH (1) CH539772A (de)
DE (1) DE2131496C3 (de)
NL (1) NL7110205A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GR1003473B (el) * 1999-10-14 2000-11-03 Υδραυλικο συστημα μετατροπης & μεταφορας ενεργειας
EP1111234A2 (de) * 1999-12-20 2001-06-27 Hydraulik-Ring GmbH Kraftstoffpumpe

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK155959C (da) * 1984-02-29 1989-10-16 Niels Andersen Ekscentrikring og ekscentrik, hvor ekscentrikringen har polygonformet tvaersnit
DE19844272C2 (de) * 1998-09-26 2002-07-18 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung
DE19933570A1 (de) * 1999-07-16 2001-02-01 Siemens Ag Radialkolbenpumpe, insbesondere zur Förderung von Kraftstoff in einer Einspritzanlage

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2576175A (en) * 1949-08-11 1951-11-27 Gerald Burns Rotary piston pump
US3160073A (en) * 1961-02-03 1964-12-08 Lucien Rene Hydraulic motor
US3276275A (en) * 1964-12-11 1966-10-04 Ebbert Engineering Company Motion transfer mechanism
US3492948A (en) * 1968-04-08 1970-02-03 Haviland H Platt Hydraulic pump/motor
US3641828A (en) * 1970-08-28 1972-02-15 John J Ryan Rotary-linear motion converter

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2576175A (en) * 1949-08-11 1951-11-27 Gerald Burns Rotary piston pump
US3160073A (en) * 1961-02-03 1964-12-08 Lucien Rene Hydraulic motor
US3276275A (en) * 1964-12-11 1966-10-04 Ebbert Engineering Company Motion transfer mechanism
US3492948A (en) * 1968-04-08 1970-02-03 Haviland H Platt Hydraulic pump/motor
US3641828A (en) * 1970-08-28 1972-02-15 John J Ryan Rotary-linear motion converter

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GR1003473B (el) * 1999-10-14 2000-11-03 Υδραυλικο συστημα μετατροπης & μεταφορας ενεργειας
EP1111234A2 (de) * 1999-12-20 2001-06-27 Hydraulik-Ring GmbH Kraftstoffpumpe
EP1111234A3 (de) * 1999-12-20 2002-12-18 Hydraulik-Ring GmbH Kraftstoffpumpe

Also Published As

Publication number Publication date
DE2131496A1 (de) 1973-01-11
NL7110205A (de) 1972-12-27
DE2131496B2 (de) 1973-10-31
CH539772A (de) 1973-07-31
DE2131496C3 (de) 1974-05-30

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