US3807282A - Radial piston machine intended for use as a pump, compressor or motor - Google Patents

Radial piston machine intended for use as a pump, compressor or motor Download PDF

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Publication number
US3807282A
US3807282A US00314239A US31423972A US3807282A US 3807282 A US3807282 A US 3807282A US 00314239 A US00314239 A US 00314239A US 31423972 A US31423972 A US 31423972A US 3807282 A US3807282 A US 3807282A
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United States
Prior art keywords
rotor
roller
piston
end faces
pistons
Prior art date
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Expired - Lifetime
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US00314239A
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English (en)
Inventor
G Gransten
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Haegglund and Soener AB
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Haegglund and Soener AB
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    • 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
    • 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
    • F01B13/062—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 cylinder block and actuating or actuated cam both rotating

Definitions

  • ABSTRACT A radial piston machine having a valve slide'shaft upon which is journalled a rotor with radial cylinders within which pistons are movable inwards/outwards relative to said shaft, and around the rotor a ring arranged for rotation about an axis excentric to the slide shaft. Rollers are arranged between the pistons outer [30] Foreign Application Priority Data Dec. 22 1971 Sweden 16480/71 end faces and a mile race on the inside of said ring serving to transmit motion between the ring and rotor [52 U.S. Cl. 91/496 during H1der elements having fixed [51] Int. Cl.
  • the present invention relates to a radial piston machine intended for use as a pump, compressor or motor, with a centrally arranged fixed valve slide shaft upon which is journalled a rotor with radial cylinders within which are pistons movable inwards and outwards relative to the slide shaft, and around the rotor a rotor ring arranged for rotation about an axis excentric to the slide shaft, and roller elements arranged between the pistons outer end faces and a roller path (race) on the inside of the rotor ring serving to transmit motion between the rotor ring and the rotor during rolling, caused by the excentricity, to and fro
  • a rotary machine of the aforesaid radial piston type is known to the art from, for example, Swedish Pat. No. 325,479.
  • a feature peculiar to this type of rotary machine is that no external torque is either taken from or put into the machines rotor. Instead, the torque is transferred via the rotor ring.
  • roller elements roll to and fro on the piston end faces over a distance corresponding to the excentricity.
  • a definite roller position determined by the geometry of the machine and by the current load conditions obtaining.
  • the rollers are held in their seatings by contact pressure against the rotor ring on one side and the piston end faces on the other.
  • the main parameters governing the machines geometry of motion are the excentricity, diameter of rotor ring and diameter of rollers.
  • the loading conditions are determined by the ratio between the piston forces obtaining in that part of the machine where the pressure medium (working medium) is at a high pressure level and the corresponding piston forces in the part where the pressure level is low.
  • piston forces we here mean the hydraulic forces and forces of piston resilience operative in the cylinder chamber plus the forces of intertia in'the form of centrifugal forces. All these forces are directioned so as to assist in increasing the contact forces on the rollers.
  • the term hydraulic force will henceforth be deemed to 'cover not only liquid pressure but also gas pressure in possible applications where the working medium is a gas.
  • acting on the pistons is yet another force determined by the hydraulic pressure and obtaining in the machine casing surrounding the rotor and slide shaft. This hydraulic pressure, hereinafter called the draining pressure, arises through flow of pressure medium into the machine casing through split seals between pistons and cylinders and between rotor and slide shaft.
  • the pressure level is there determined by the inflow and by the restrictions in the way of outflow from the machine casing.
  • Another efi'ect experienced in certain conditions is displacement variations of rotor plus pistons due to torsional vibrations.
  • the force exerted on the pistons due to the drainage pressure acts in opposition to the forces-previously mentioned and thus tends to reduce the contact forces on the rollers.
  • the margins for said contact forces thus depend on the drainage pressure and are in general least for the pistons/rollers working on the machines LP side and especially on the outer end faces of these pistons where the forces of piston resilience are least. If the margins are reduced to such an extent that the contact forces are nullified, the rollers may be caused to shift from their geometrically appointed positions under the action of accelerations.
  • the purpose of the present invention is to allow operation with a higher drainage pressure than hitherto, i.e., with smaller contact force margins, while at the same time fully ensuring proper positioning of the roller with respect to the pistons end face.
  • the invention likewise aims to allow application of so high a drainage pressure that the to and fro motion of the pistons is eliminated with the result that the machines pump action ceases or, in other words, disengagement occurs.
  • the aforesaid problem is resolved by providing the machine with holder elements that hold the roller elements in position before the piston end faces, in contact with or near the roller path (race) on the rotor ring, even if the pistons are so far within the cylinders that contact between the roller elements and pistonend-faces is lost.
  • the holder elements need have no moving parts that would suffer wear in normal continuous operation, only liquid friction being involved;
  • the holder elements include fixed stop devices on the rotor face sides, which stop devices have bearing edges on either side of each piston serving to limit movement of the roller elements on the piston end faces.
  • the roller elements are in turn preferably provided with axial guide pins fitting into circumjacent grooves located in end faces joined to'the rotor ring.
  • the roller elements are further preferably designed as rollers with end flanges coacting with circumscribing guide surfaces on the rotor ring.
  • the terminal positions of the roller element on the piston end face is determined by coaction between the end flanges of the roller element and the edges of the stop devices, the stop point in each outer position being so located that in such position the contact force between roller i element and piston gives rise to a moment about the centerline of the slide shaft which moment tendsto shift the roller element from the outer position further inwards on the pistons end face.
  • the characteristic feature of the embodiments is that the position of the roller relative to the pistons outer end face (hereinafter called the piston roller path or race) is determined partly by coaction between the axial guide pins of the roller elements and the circumjacent grooves in the rotor ring faces, whereby the rollers are prevented from shifting from the rotor rings contact surface under the action of radial accelerations, and partly by the stop devices fitted on the rotor faces serving to prevent the rollers from leaving the zone in theway of the piston roller path (race) and the cylinder opening under the action of tangential accelerations.
  • the need for special positioning of the roller elements arises only in cases where the contact forces on the rollers are nullified.
  • FIG. 1 shows a radial section of the machine through one of its cylinders
  • FIG. 2 is a view of the machine seen from the end of the slide shaft with one end of thecasing removed
  • FIG. 3 illustrates schematically the design principle adopted in order to minimize the effect of the holder elements on the machines overall dimensions.
  • FIG. 1 illustrates the construction of the machine.
  • the slide shaft 1 carries the hydrostatically journalled rotor 2 as well as the machine casing comprising the rotor ring 3 and end faces 4, 5.
  • the machine casing is excentrically journalled with respect to the rotor by means of roller bearings (Sand 7 at either end of the slide shaft.
  • the end plane 8 of the slide shaft is designed as a mechanical and hydraulic coupling plane for the machine. From this plane are led the main axial ducts to the two slide ports and 9 for the machines HP and LP sides, respectively. Ports 9 and 10 communicate cyclically with the several cylinder chambers. From end plane 8 there is also led a further duct 32 which is in direct communication with the interior of the machine casing. It is through this duct that the leakage flow is drained.
  • the piston 12 moves to and fro in consequence of the bearing point on the rotor ring varying its distance from the rotors axial centerline 30 (FIG. 2) during the course of rotation, depending in turn on the excentricity distance between the said axial centerline and the rotor rings centerline axis 27.
  • the plane 13, in which both central axes 30 and 27 lie, is called the plane of excentricity. This plane has a dual functional significance: firstly it is the plane in which the pistons both turning points in the cylinder chambers are reached, and secondly it is the plane which divides the machines piston/cylinder equipment into one side woring with working medium at a low pressure level and one side working with the working medium at high pressure.
  • Piston 12 is loaded in the cylinder chamber by two concentric compression springs which in the exemplary embodiment here illustrated consist of two helical springs 14 and 15 of opposite lays.
  • the reason for having two springs is firstly that by this means the maximum possible spring force can be got into the space available and secondly the risk is minimized of the piston tending to twist in the cylinder chamber in the event of contact with the roller being lost.
  • the main task of these springs is to provide a mechanical back-up force on piston 12 in addition to the hydraulic and inertial forces that act upon it.
  • hydraulic forces may assume values ranging from complete vacuum (in the pressure medium) to full working pressure, depending inter alia on the compressibility of the pressure medium and pressure fluctuations caused thereby in the hydraulic system, it is easy to see why there is a need for the aforesaid superposed spring forces in order to maintain, in most operating conditions, positive contact forces between piston 12, roller 16 and rotor ring 3.
  • the cylindrical roller 16 is provided at its ends with concentric flanges 17 and 18 which are slightly tapered towards the roller surface and coact with corresponding chamfers on the inner edges of the rotor ring.
  • concentric flanges 17 and 18 which are slightly tapered towards the roller surface and coact with corresponding chamfers on the inner edges of the rotor ring.
  • One function of these flanges is toguide the movement of the roller suchwise that its generatrices remain parallel to those of the rotor ring. 7
  • rollers movement is secured by contriving that, in the zone axially beyond the said flanges, the roller is designed with cylindrical pins 19 and 20 that engage in the mutually concentric grooves 21 and 22 on the inside of end faces 5 and 4, respectively.
  • a radial piston machine intended for use as a pump, compressor or motor, with a centrally arranged fixed valve slide shaft upon which is journalled a rotor with radial cylinders within which are pistons movable inwards and outwards relative to the slide shaft, and around the rotor a rotor ring arranged for rotation about an axis eccentric to the slide shaft, and roller elements arranged between the pistons outer end faces and a roller path on the inside of the rotor ring serving to transmit motion between the rotor ring and the rotor during rolling, caused by the eccentricity, to and fro on roller paths formed on the said piston end faces, characterized by provision of holder elements whichho'ld the roller elements in position for the piston end faces, in contact with or near the roller path on the rotor ring, even if the pistons are withdrawn so far into their cylinders that contact between the roller elements and the piston end faces is lost, the roller elements having axial guide pins fitting into circumjacent grooves located in
  • a radial piston machine characterized in that the holder elements include, on the rotor end face sides, fixed stop devices having bearing edges on either side of each piston, serving to limit the movements of the roller elements on the piston end faces.
  • roller elements are formed as rollers having end flanges which coact with circumjacent guide surfaces on the rotor ring.
  • a radial piston machine intended for use as a pump, compressor or motor, with a centrally arranged fixed valve slide shaft upon which is journalled a rotor with radial cylinders within which are pistons movable inwards and outwards relative to the slide shaft, and
  • a rotor ring arranged for rotation about an axis eccentric to the slide shaft, and roller elements arranged between the pistons outer end faces and a roller path on the inside of the rotor ring serving to transmit motion between the rotor ring and the rotor during rolling, caused by the eccentricity, to and fro on roller paths formed on the said piston end faces, characterized by provision of holder elements which hold the roller elements in position for the piston end faces, in contact'with or near the roller path on the rotor ring, even if the pistons are withdrawn so far into their cylinfaces.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US00314239A 1971-12-22 1972-12-11 Radial piston machine intended for use as a pump, compressor or motor Expired - Lifetime US3807282A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE16480/71A SE359147B (enrdf_load_stackoverflow) 1971-12-22 1971-12-22

Publications (1)

Publication Number Publication Date
US3807282A true US3807282A (en) 1974-04-30

Family

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Family Applications (1)

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US00314239A Expired - Lifetime US3807282A (en) 1971-12-22 1972-12-11 Radial piston machine intended for use as a pump, compressor or motor

Country Status (8)

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US (1) US3807282A (enrdf_load_stackoverflow)
JP (1) JPS4870902A (enrdf_load_stackoverflow)
DE (1) DE2262776A1 (enrdf_load_stackoverflow)
FR (1) FR2165586A5 (enrdf_load_stackoverflow)
GB (1) GB1355280A (enrdf_load_stackoverflow)
IT (1) IT970661B (enrdf_load_stackoverflow)
NL (1) NL7217282A (enrdf_load_stackoverflow)
SE (1) SE359147B (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3998133A (en) * 1974-11-14 1976-12-21 Sanwa Seiki Mfg. Co. Ltd. Radial type hydraulic pump motor

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2504987B1 (fr) * 1981-05-04 1986-04-18 Poclain Hydraulics Sa Mecanisme a fluide sous pression comportant des galets de reaction portes par des pistons
EP2213878B1 (de) 2009-02-02 2012-09-26 MavelTech AG Drehkolbenmaschine
FR2956461B1 (fr) * 2010-02-18 2012-09-21 Poclain Hydraulics Ind Dispositif de transmission hydraulique permettant un crabotage/decrabotage rapide.

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2103314A (en) * 1935-12-31 1937-12-28 Elek K Benedek Variable delivery pump or motor
US2115296A (en) * 1935-05-28 1938-04-26 Elek K Benedek Rotary radial plunger hydraulic apparatus
US2977891A (en) * 1956-10-29 1961-04-04 Arthur E Bishop High pressure radial piston pump
US3106167A (en) * 1958-06-24 1963-10-08 Dentatus Ab Machine adapted to operate as pump, compressor or motor
US3583286A (en) * 1967-11-21 1971-06-08 Consiglio Nazionale Ricerche Improvements in radial-type hydraulic machines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2115296A (en) * 1935-05-28 1938-04-26 Elek K Benedek Rotary radial plunger hydraulic apparatus
US2103314A (en) * 1935-12-31 1937-12-28 Elek K Benedek Variable delivery pump or motor
US2977891A (en) * 1956-10-29 1961-04-04 Arthur E Bishop High pressure radial piston pump
US3106167A (en) * 1958-06-24 1963-10-08 Dentatus Ab Machine adapted to operate as pump, compressor or motor
US3583286A (en) * 1967-11-21 1971-06-08 Consiglio Nazionale Ricerche Improvements in radial-type hydraulic machines

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3998133A (en) * 1974-11-14 1976-12-21 Sanwa Seiki Mfg. Co. Ltd. Radial type hydraulic pump motor

Also Published As

Publication number Publication date
DE2262776A1 (de) 1973-07-05
FR2165586A5 (enrdf_load_stackoverflow) 1973-08-03
IT970661B (it) 1974-04-20
JPS4870902A (enrdf_load_stackoverflow) 1973-09-26
GB1355280A (en) 1974-06-05
SE359147B (enrdf_load_stackoverflow) 1973-08-20
NL7217282A (enrdf_load_stackoverflow) 1973-06-26

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