US3520233A - Low friction radial piston pump or motor - Google Patents

Low friction radial piston pump or motor Download PDF

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Publication number
US3520233A
US3520233A US795325*A US3520233DA US3520233A US 3520233 A US3520233 A US 3520233A US 3520233D A US3520233D A US 3520233DA US 3520233 A US3520233 A US 3520233A
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United States
Prior art keywords
piston
pistons
cylinder
reaction ring
motor
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Expired - Lifetime
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US795325*A
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English (en)
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Jaromir Tobias
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    • 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
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0438—Particularities relating to the distribution members to cylindrical distribution members
    • 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

  • a radial piston pump or motor including a cylinder block rotatable about a pintle shaft, a reaction ring assembly rotatable about an axis parallel to and displaced from the axis of said pintle shaft, pistons reciprocable in the bores of said cylinders and link means comprising at least one pair of parallelogram links connecting the pistons to the reaction ring, for transmitting forces be- H tween said assembly and pistons.
  • connection between the link means and piston is effected along a line perpendicular to the piston axis, the assembly thus being characterized by a force transmission between pistons and reaction ring which precludes the application to the pistons of forces which tend to cock or tilt the pistons relative to the cylinder bores.
  • This invention is in the field of radial piston pumps and motors.
  • the prior art It is well known to provide a radial piston pump or motor in which a block having radially directed cylinders rotates about a pintle shaft.
  • the pintle shaft includes outwardly directed high and low pressure distribution chambers sequentially communicated to the cylinders as they rotate about the shaft by fluid passages extending radially from the cylinders and opening onto the distribution chambers.
  • a reaction ring surrounds the pistons and the outermost ends of the pistons, either directly or through an interposed piston shoe, are pressed against the reaction ring.
  • the axis of the reaction ring is displaced from the axis of the pintle shaft in normal operation and thus, in the course of rotation of the cylinder block, pressure is exerted by the pistons against reaction ring portions which are not precisely perpendicular to the axes of the cylinder bores.
  • the present invention relates to a radial piston pump or motor wherein the forces exerted between the pistons and the reaction ring are channeled through a parallelogram link connector assembly comprising a pair of relatively movable arms or links pivotally connected at spaced points to the piston assembly, which points are normal to the axis of the cylinder bore. The other ends of the links are connected to spaced points on the reaction ring.
  • the parallel links assure that at all positions of the block relative to the reaction ring, the piston axis is maintained parallel with the axis of the cylinder and, thus, there is no cocking or tilting forces exerted on the piston.
  • the device above described may be, but is not necessarily, combined with a further refinement incorporating a piston stabilizer which functions to prevent the piston axis, although maintained parallel with the cylinder axis by the link assembly, from tending to be displaced transversely with respect to the cylinder axis. More specifically, the parallel link assembly prevents any cocking of the piston and the stabilizer assembly maintains the parallel oriented piston centralized within the cylinder bore.
  • the linkage also permits a far greater piston travel than heretofore practicable, with little increase in overall Sue.
  • a further advantage lies in the fact that, since the engagement of the piston within the cylinder is not relied on as the means for stabilizing the piston, it is possible, for the first time in a hydraulic device of this type, to make effective use of piston rings, thus greatly reducing the cost of fabrication by increasing permitted tolerances and facilitating repair and replacement of parts.
  • An additional advantage lies in the fact that no sliding or slipping movement between the pistons and/or piston shoes relative to the reaction ring is experienced, all relative movements being effected through bearing linkages between the link arms and the piston and reaction ring.
  • the radial movement of the pistons is a double harmonic function, resulting from the superimposition of the movement imparted to the piston by the pivoting of the links about the reaction ring on the harmonic (sine) function generated by the rotation of the reaction ring.
  • the initial movements of the pistons away from the minimum displacement position and the final return movements of the pistons to the minimum displacement positions are more gradually accomplished than would be the case if the pistons were controlled solely by a conventional reaction ring.
  • This phenomenon results from the fact that the pivotal movement of the parallel links exerts a subtractive influence as respects the direction of movement imparted to the piston by the reaction ring assembly as the pistons leave and approach the minimum displacement positions.
  • a further object of the invention is to provide a device of the type described in which there is no tendency for the piston to cock relative to the cylinder bores.
  • Still a further object of the invention is the provision of a radial piston pump or motor wherein the connection between the pistons and the reaction ring is effected through a parallelogram linkage connector means which maintains the piston axis parallel with the cylinder axis and channels all forces exerted between piston and reaction ring in such parallel directions.
  • Still a further object of the invention is the provision of a device of the class described and including an auxil-. iary piston stabilizer which absorbs, externally of the piston and cylinder, any side thrust forces exerted against the pistons.
  • Still a further object of the invention is to provide, in a device of the class described, a piston head which employs piston rings.
  • FIG. 1 is a vertical sectional view through a radial piston pump or motor in accordance with the invention
  • FIG. 2 is a magnified section taken on the line 22 of FIG. 1;
  • FIG. 3 is a magnified vertical section through an embodiment of the invention.
  • FIG. 4 is a section taken on the line 44 of FIG. 3;
  • FIG. 5 is a magnified section taken on the line 5-5 of FIG. 3.
  • FIGS. 1 and 2 a radial piston hydraulic pump-motor which comprises the usual pintle shaft carrying a rotatable cylinder block assembly 11 in driving connection with;
  • the apparatus carries, in addition, a reaction ring chassis 13 which can, in the usual manner, be shifted from side to side relative to the pintle shaft, namely, from left to right as viewed in FIG. 1, and toward and away from the viewer in FIG. 2.
  • the reaction ring chassis position may be varied to locate the axis of the reaction ring to either side or coaxial of the axis of the pintle shaft selectively, in accordance with the desired operation of the apparatus.
  • the reaction ring chassis includes spaced support disks 14, 15, providing laterally elongated clearance spaces 16, 17, respectively, for effecting the desired eccentricity.
  • the disks 14, 15 are joined by the usual yoke or like assembly (not shown), forming a part of the mechanical linkage, to permit their simultaneous lateral movement to effect the reaction ring eccentricity referred to above.
  • the peripheries 18, 19 of the disks 14, 15 form bearing races for the support of cylindrical bearing members 20, 21, or like bearing assemblies, the opposite races for the bearings being for-med in the reaction rings 22, 23, respectively.
  • the block 11 includes a central bearing portion 24 which is rotatably mounted about the pintle shaft 10.
  • the pintle shaft incorporates high and low pressure conduits 25, 26, terminating in pressure distribution chambers 27, 28. It will be appreciated that the distribution chambers 27, 28 are outwardly open, the chambers being separated by divider lands 29, 30.
  • the cylinder block includes a multiplicity of radially directed cylindrical structures 31, seven being shown in the illustrated embodiment.
  • the cylinders 31 are provided with internal bores 32, the radial innermost ends of the bores incorporating fiuid distribution passages 33.
  • the passages are shaped in the manner shown in my US. Pat. No. 3,345,916 of Oct. 10, 1967, being axially elongated in the direction of the pintle shaft and angularly reduced in size in the areas adjacent said shaft, the passages progressively becoming wider and shorter as they merge with the cylinder bores 32.
  • the inner terminal ends of the fluid passages are sequentially connected to the radially open high and low pressure distribution chambers 27, 28 of the pintle shaft as the block rotates, the land areas 29, 30 being of a sufiicient angular extent completely to seal with a minimum of overlap each of the passages as they scan the land areas.
  • a piston assembly including a piston head portion 34 in sealing relation of the bore and a piston rod 35 extending radially outwardly from the piston head. Adjacent their outermost ends 36, the piston rods 35 are formed with a pair of bosses 37, 38, carrying cross rods 39, 40.
  • the axes of the cross rods 39, 40 are equi-distant from the radius R of the pintle shaft when the pistons are in axial alignment within the bores 32 of the cylinders.
  • the distal ends of the rods 39, 40 are provided with bearing structures, such as roller bearings 41.
  • each of the bearings 41 is afiixed to the outermost end of a connector link 42a, 42b.
  • four connector links are secured to each piston rod in view of the fact that the reaction rings proper are laterally offset from the axes of the cylinders.
  • a single pair of link arms may be used to control the action of the pistons, such an arrangement being appropriate where the reaction ring is disposed in outward surrounding relation of the pistons.
  • the links 42a, 42b will hereafter be referred to as a pair of links, the two links on the opposite side of the block 11 and connected to the opposite reaction ring 22 also comprising a pair.
  • each pair of links 42a, 42b be mounted so that the axis of the upper end of the links and the pivot axis of the lower ends of the links of each pair in all positions remain parallel to each other and thus act in the manner of a parallelogram linkage.
  • pistons with shorter heads may be effectively employed, without fear of scoring or instability.
  • the use of shorter head pistons brings secondary benefits by way of facilitating lubrication, enabling increased displacement per over-all pump diameter, enabling a larger stroke per given piston length, and permitting the use of sealing mechanisms, such as piston rings, between the piston head and the piston wall.
  • piston rod 35 is rigidly connected to a cross bar assembly 50, the cross bar or arm assembly being perpendicular to the axis of cylinder bore 32. While the cross bar and piston rod may be integrally formed, the connection is preferably effected through a threaded or otherwise secured inter-engaging 6 stud 51 on the piston, received within threaded aperture 52 on the assembly 50.
  • the cylinder members 53 of this embodiment are formed with external guide surfaces 54, 55 which parallel the cylinder axis.
  • the cross arm 50 is internally threaded, as at 56, and receives a guide cup 57, the upper end 58 of which is externally threaded and received within the portion 56.
  • the guide cup is threaded into the cross bar assembly 50, the cup including vertically directed, flattened guide surfaces 59, 60, disposed in parallel spaced relation to the surfaces 55, 54, respectively, on the cylinders.
  • Sets of needle bearings 61, 62, diagrammatically illustrated, or other suitable anti-friction guides, are interposed between the respective surfaces 55, 59 and 54, 60, to provide a low friction guiding function between the cup 57 and the cylinder 53.
  • piston head 65 Formed at the lower end of piston rod 35' is a piston head 65 which, as shown in FIG. 3, provides substantial clearances with respect to the cylinder walls.
  • the piston head is provided with a series of spaced annular grooves 66, within which are mounted piston rings 67.
  • the rings provide the requisite seals with respect to the cylinder bore 32'. It will be noted that, as in all devices incorporating piston rings, the rings 67 permit a degree of lateral movement of the pistons in the cylinders, by reason of the clearances of the rings in grooves 66. The permitted lateral movement does not interfere with the proper operation of the illustrated device, however, since the piston head is not relied on as a stabilizing element.
  • the land area 29 separating the high and low pressure areas of the pintle shaft may be provided with longitudinally directed grooves G, the depth of which need not exceed a few thousandths of an inch. These grooves function to reduce leakage across the outer surface of the lands between the lands and the rotating block, despite the existence of normal operating clearances. Without limitation, it is believed that the reduction in leakage is a result of an interruption of laminar flow across the face of the lands, the grooves tending to induce a turbulence in any such laminar movement and thereby reducing leakage losses.
  • a radial piston pump or motor comprising a pintle shaft, a cylinder block mounted on said shaft and including a plurality of radially extending cylinder members having internal cylinder bores and external guide surfaces, said guide surfaces being disposed in a plane parallel with said bores, a reaction ring assembly mounted for rotation about an axis parallel with and displaced from the axis of said pintle shaft, a piston member mounted for reciprocation in each said bore, each said member including a head portion carrying piston rings in sealing relation with said bore and a radially directed piston rod extending outwardly beyond the end of said cylinders, a cross arm assembly rigidly afiixed to the outer end of each said piston rod including a spaced pair of bearing members having their axes disposed in a common plane normal to the axis of said cylinder bore, a pair of parallel links having first end portions pivotally connected to said bearing members, the other ends of said links being pivotally connected to said reaction ring assembly whereby said References Cited UNITED STATE

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US795325*A 1969-01-30 1969-01-30 Low friction radial piston pump or motor Expired - Lifetime US3520233A (en)

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Application Number Priority Date Filing Date Title
US79532569A 1969-01-30 1969-01-30

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US795325*A Expired - Lifetime US3520233A (en) 1969-01-30 1969-01-30 Low friction radial piston pump or motor

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US (1) US3520233A (xx)
AT (1) AT295329B (xx)
BE (1) BE739727A (xx)
CH (1) CH507445A (xx)
DE (1) DE1955889A1 (xx)
FR (1) FR2029659A1 (xx)
GB (1) GB1258987A (xx)
IL (1) IL32948A (xx)
NL (1) NL6914657A (xx)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3709104A (en) * 1971-03-01 1973-01-09 Tobias J Radial piston hydraulic pump or motor with low loss reaction linkage
US4006668A (en) * 1973-10-23 1977-02-08 Sulzer Brothers Limited Hydrostatic piston machine having a cylindrical mounting pin

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2130342B (en) * 1982-10-28 1985-10-30 Edwards Ch Ltd Cistern flush valve assembly
US4433446A (en) * 1983-01-27 1984-02-28 Kohler Co. Flush valve attachment system

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB267102A (en) * 1926-03-02 1927-08-25 Arthur Hardt Improvements in or relating to rotary liquid pumps and liquid engines
US2001706A (en) * 1932-04-28 1935-05-21 Manly Corp Variable capacity pump
DE686067C (de) * 1933-09-20 1940-01-02 Gustav Schulze Fluessigkeitspumpe oder -motor eines Fluessigkeitsgetriebes
US2474536A (en) * 1945-02-17 1949-06-28 John E Lundegard Variable hydraulic pump or motor
US2510247A (en) * 1942-05-19 1950-06-06 Joseph S Parenti Apparatus for compressing fluids
US2972961A (en) * 1957-09-18 1961-02-28 Albert P Clark Hydrostatic lubricating apparatus
US3392631A (en) * 1966-08-11 1968-07-16 William E. Baker Steam engine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB267102A (en) * 1926-03-02 1927-08-25 Arthur Hardt Improvements in or relating to rotary liquid pumps and liquid engines
US2001706A (en) * 1932-04-28 1935-05-21 Manly Corp Variable capacity pump
DE686067C (de) * 1933-09-20 1940-01-02 Gustav Schulze Fluessigkeitspumpe oder -motor eines Fluessigkeitsgetriebes
US2510247A (en) * 1942-05-19 1950-06-06 Joseph S Parenti Apparatus for compressing fluids
US2474536A (en) * 1945-02-17 1949-06-28 John E Lundegard Variable hydraulic pump or motor
US2972961A (en) * 1957-09-18 1961-02-28 Albert P Clark Hydrostatic lubricating apparatus
US3392631A (en) * 1966-08-11 1968-07-16 William E. Baker Steam engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3709104A (en) * 1971-03-01 1973-01-09 Tobias J Radial piston hydraulic pump or motor with low loss reaction linkage
US4006668A (en) * 1973-10-23 1977-02-08 Sulzer Brothers Limited Hydrostatic piston machine having a cylindrical mounting pin

Also Published As

Publication number Publication date
NL6914657A (xx) 1970-08-03
AT295329B (de) 1971-12-27
IL32948A (en) 1972-09-28
FR2029659A1 (xx) 1970-10-23
BE739727A (xx) 1970-04-02
DE1955889A1 (de) 1970-08-06
CH507445A (fr) 1971-05-15
GB1258987A (xx) 1972-01-05
IL32948A0 (en) 1969-11-30

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