US3345916A - High efficiency hydraulic apparatus - Google Patents

High efficiency hydraulic apparatus Download PDF

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Publication number
US3345916A
US3345916A US508249A US50824965A US3345916A US 3345916 A US3345916 A US 3345916A US 508249 A US508249 A US 508249A US 50824965 A US50824965 A US 50824965A US 3345916 A US3345916 A US 3345916A
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US
United States
Prior art keywords
passages
bores
aperture
block
shaft
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
US508249A
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English (en)
Inventor
Tobias Jaromir
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to US508249A priority Critical patent/US3345916A/en
Priority to GB23469/66A priority patent/GB1120809A/en
Priority to SE7623/66A priority patent/SE313501B/xx
Priority to NL6608369A priority patent/NL6608369A/xx
Priority to DE19661528598 priority patent/DE1528598A1/de
Priority to NO163628A priority patent/NO125248B/no
Priority to DK420066AA priority patent/DK118168B/da
Priority to BE686040D priority patent/BE686040A/xx
Priority to CH1237466A priority patent/CH460538A/fr
Application granted granted Critical
Publication of US3345916A publication Critical patent/US3345916A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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
    • F01B1/0655—Details, component parts specially adapted for such machines 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
    • F01B1/0675—Controlling
    • F01B1/0686—Controlling by changing the effective piston stroke
    • F01B1/0689—Controlling by changing the effective piston stroke by changing the excentricity of one element relative to another element

Definitions

  • ABSTRACT OF THE DISCLOSURE A high efficiency hydraulic pump or motor of the type in which a cylinder block having radially extending cylinder bores rotates about a central pintle shaft and wherein hydraulic fluid communicates from the pintle shaft to the cylinder bores through passages extending radially inwardly from the bores to an axial aperture in the block in communication with the pintle shaft discharge, said passages being characterized by the axial dimension of such passages at their radial innermost ends being in excess of the diameter of the cylinder bores and the transverse extent of said radial innermost ends being less than the diameter of said bores, said transverse and axial dimensions, respectively, increasing and decreasing as said passages approach said cylinder bores.
  • This invention relates to a hydraulic device, and more particularly to a hydraulic pump or motor device of the radial piston type.
  • this invention relates to an ultra high efficiency radial piston hydraulic pump or mot-or.
  • this invention relates to an improved hydraulic pump or motor device of the type in which a block containing radial cylinder bores rotates about a pintle shaft having side discharge areas, the combination having improved conduits communicating between the pintle shaft and the cylinder bores, to increase the operating efiiciency of the device without any material increase in the size or weight of the pump or motor.
  • hydraulic systems are especially useful in that a single, infinitely variable hydraulic pump may, by appropriate connections, be utilized to drive one or more reversible hydraulic motors at positions remote from the pump, eachof the motors also being infinitely variable.
  • a single, infinitely variable hydraulic pump may, by appropriate connections, be utilized to drive one or more reversible hydraulic motors at positions remote from the pump, eachof the motors also being infinitely variable.
  • their use in situations where high power applications are encountered has been heretofore considered impractical.
  • a further object of the invention is to provide a novel hydraulic pump or motor of greatly improved efficiency by reason of a novel porting arrangement whereby the high losses heretofore inherent in hydraulic pumps and motors, occurring in the course of transfer of the fluid from the pintle shaft to the cylinder chamber, are obviated.
  • a further object of the invention is the provision of a hydraulic pump or motor device of the type described wherein the increase in efiiciency is achieved without significant increase in over-all size.
  • the drastic increase in efliciency obtained through the use of my device is predicated upon the provision of passages within the cylinder block connecting the cylinder bores to the pintle shaft discharge area, the passages having a cross-sectional area approximately equal to the cross-sectional area of the cylinder chambers.
  • the desired increased area passageways are provided without increasing the diameter of the block or the pintle shaft by, instead, elongating the axial dimension of the block at its junction with the pintle shaft.
  • the passages leading from the pintle shaft to the cylinder chambers are axially elongated at the junction with the pintle shaft to exceed the diameter of the cylinder chambers.
  • the transverse or lateral dimension of the passages at said junction is considerably less than the diameter of the cylinder chambers, such narrowed transverse dimension permitting the formation of a plurality of passages without any increase in the diameter of the pintle shaft discharge area or the block.
  • the axial extent of the passages progressively decreases and the transverse extent of the passages progressively increases at progressive, radially outwardly disposed portions of the passages, the radial uppermost end of the passages preferably merging smoothly into the cylinder bores.
  • the cross-sectional area at all points of the passage is approximately equal to the cross-sectional area of the cylinder chambers.
  • FIGURE 4 is a section taken on the lines 44 of FIGURE 2;
  • FIGURE 5 is a perspective view of a solid geometric figure corresponding to the outline of the passages linking the cylinder bores to the pintle shaft, better to illustrate the shape of such passages.
  • a hydraulic pump or motor assembly 10 including a fixed frame 11 carrying a fixed, generally centrally disposed pintle shaft 12 which is mounted on fixed supports (not shown) carried by the frame.
  • the frame 11 includes side wall portions 13 and 14, providing mounting means for the housing 15 of the hydraulic pump or motor.
  • the housing 15 may include laterally directed guide rods 16 and 17, integral with or separately attached to the housing.
  • the guide rod 16 is slidably disposed within an aperture 18 formed in the side wall portion 14.
  • An aperture 19 is formed within the side Wall portion 13.
  • An adjustment wheel 20 is rotatably mounted within the aperture 19, the wheel 20 including an internally threaded boss 21.
  • the guide rod 17 is externally threaded, as at 22, the boss 21 being complementally threaded over the portion 22.
  • the inner surface 25 of the housing 15 defines an annular raceway forming, in essence, one component of a roller bearing structure, an annular reaction ring 26, spaced from the surface 25 forming another component of the bearing. Between the reaction ring 26 and the annular surface 25 are disposed a plurality of cylindrical bearing members 27, which are maintained in spacedapart condition within the housing by the shallow, outwardly directed bearing sockets or recesses 28 formed in the outer surface of the reaction ring 26. Any suitable anti-friction means may be interposed between the housing and the ring where relative rotation between these parts is desired.
  • reaction ring may comprise a portion of the housing.
  • pistons carry rollers or like anti-friction devices.
  • a rotary block member 29 which is freely rotatably mounted for movement about the pintle shaft 12.
  • the block 29, which is fixed against axial movement with respect to the pintle shaft, is provided with radially directed keyway slots 30, 31, providing a driving connection with the tubular drive shaft member 32.
  • the drive shaft member which may be an output shaft in the case of a motor, or an input shaft in the case of a pump, includes a pair of axially directed teeth 33, 34, meshing respectively with the slots 30, 31, thus to. communicate rotary movement of the shaft to the block 29.
  • the block 29 incorporates the usual radially extending cylinder chambers 35. While the number of such chambers is not limited, it is common practice to provide an odd number, the illustrated embodiment incorporating nine.
  • the pintle shaft is hollowed to define axially extending input and output passageways 36, 37, respectively, the passageways terminating at their innermost ends in outwardly open discharge ports or chambers 38, 39, separated from each other by diametrically opposed lands L.
  • the block incorporates a central, axially extending bore or aperture 40 which is rotatably mounted over the pintle shaft.
  • the block 29 is axially enlarged in the area adjoining the pintle shaft, the axial dimension of said block at the shaft preferably exceeding the axial dimension of the block at a point displaced from the shaft.
  • the axially elongated nature of the block in the area adjacent the shaft is sufficient to permit the block completely to span the length of the discharge ports or chambers 38, 39, the axial extremities 41, 42 of the bore portion 40 being, of course, completed annuli and forming sealing connections with the pintle shaft 12 in the unbroken cylindrical areas to either side of the discharge ports or chambers.
  • the block 29 incorporates a series of radially extending passages linking the cylinder bores with the central bearing aperture 49 of the block, to provide a fluid path between the ports or chambers 38, 39 of the pintle shaft and the cylinder bores.
  • the passage P at said bore defines an elongated configuration in which the lengthwise dimension 50 exceeds the diameter 51 of the cylinder bores 35 by a considerable margin and the widthwise 0r transverse dimension 52 is less than the diameter 51 of the cylinder bore.
  • the total cross-sectional area of the passageway P at the bore 41) is equal or approximately equal to the cross-sectional area of a cylinder chamber 35.
  • FIGURE 5 for purposes of illustration, there is shown a solid geometric configuration which approximates the preferred shape of the passage.
  • the passages P taper angularly outwardly so as progressively to increase the transverse dimension of said passages as the passages approach the radial innermost ends of the cylinder bores 35.
  • the axial dimension of the passages P is progressively reduced as the passages approach the radial innermost ends of the cylinder bores.
  • the outermost portions of the passages are preferably circular in section and the innermost portions comprise elongated, quasi-elliptical configurations.
  • passages at the pintle-adjacent portion of the block may vary considerably, without departing from the spirit of the present invention. It is, however, an essential feature that said passages are axially elongated and transversely diminished at the pintleadjacent portion and converge axially and diverge transversely at progressive, radially disposed portions of the passages.
  • Each of the bores includes a piston member 55, the outermost ends 56 of which may be of domed or partispheroid configuration.
  • the innermost ends 57 may be flat or, for improved suction purposes, may incorporate a concavity 58.
  • the reaction ring 26 may be provided with an annular concave track 59, within which the domed portions 56 of the pistons may ride during the operation of the device.
  • the angular extent of the lands L is approximately equal to or slightly exceeds the transverse dimension 52 of the passages at the pintle-adjacent portions thereof, the lands being disposed so that preferably only one of the passages is completely isolated from communication with the chambers 38, 39 at any one time.
  • the operation of the device is in all respects conventional and need not be elaborated upon.
  • hydraulic fluid under pressure is fed to one of the passages 36 or 37, the other of said passages communicating with the reservoir.
  • the block will, in such case, be rotated and the drive shaft 32 may be connected to any device to be driven.
  • a rotary force is applied to the input shaft 32, thus to forcibly rotate the block 29, causing hydraulic fluid from a reservoir to be sucked into one of the lines 36, 37, the other said line carrying the fluid under pressure.
  • the block may comprise an integral structure containing both the passage containing components and the cylinder bores.
  • a rotary hydraulic device such as a pump or motor
  • a generally cylindrical pintle shaft having an axially elongated, recessed circumference portion defining a fluid supply area
  • a cylinder block having a central bearing aperturerotatably received on said shaft, the axial dimension of said aperture being in excess of the length of said recessed portion, said aperture being disposed in registry with said area, a plurality of radially extending cylinder bores formed in said block, and axially elongated fluid passages extending between said bores and said aperture, the axial dimension of said passages at said aperture being greater than the diameter of said bores, the transverse dimension of said passages at said boresbeing greater than the transverse dimension of said passages at said aperture.
  • a hydraulic device comprising a pintle shaft, circumferential fluid supply ports on said shaft, a cylinder block assembly having a central bearing aperture rotat ably mounted over said shaft, with said aperture overlying said supply ports, a plurality of angularly spacedapart, radially extending cylinder bores formed in said block assembly and radially extending fluid supply passages connecting said bores and said aperture, the area of any cross section through said passages taken perpendicular to the axis of said bores being substantially equal, the axial dimension of said passages at said aperture being greater than said dimension at said bore.
  • a device in accordance with claim 2 wherein said cross-sectional area of each of said passages is substantially equal to the total cross-sectional area of the piston bores fed by said passages.
  • a hydraulic device of the radial piston type which includes a pintle shaft having a circumferential discharge area
  • the improvement which comprises a cylinder block having a central bearing aperture, a plurality of angularly-spaced-apart, radially extending cylinder bores and fluid passages connecting said aperture with said bores, the axial dimension of said passages at said aperture exceeding the transverse dimension of said passages at said aperture, said transverse dimension of said passages growing progressively larger and said axial dimension of said passages growing progressively smaller as said passages approach said bores.
  • a cylinder block in accordance with claim 5 wherein the cross-sectional area of said passages, taken in a direction normal to the axis of said bores, is substantially a constant throughout the length of said passages.
  • a hydraulic device comprising a pintle shaft having laterally open fluid supply ports, a block assembly having a central bearing aperture rotatably mounted over said shaft, said aperture being of a length in excess of, and overlying, said fluid supply ports of said shaft, said block including an axially enlarged boss portion adjacent said aperture and a generally cylindrical portion outwardly of said boss portion, the axial dimension of said cylindrical portion being less than that of said boss portion, a plurality of angularly spaced-apart cylinder bores extending radially from the outer periphery of said cylindrical portion toward said shaft, and fluid supply passages in said boss portion linking said aperture and said bores, the axial dimension of said passages at said aperture being greater than the axial dimension of said cylindrical portion of said block, the transverse dimension of said pas sages at said aperture being less than the diameters of said bores, said axial dimension of said passages becoming progressively shorter and said transverse dimension of said passages becoming progressively longer as said 1,983,261 12/ 1934 Zorzi 230-177
  • a device in accordance with claim 10 wherein the 3,211,105 10/1965 Bush et all n 130 161 cross-sectional area of said passages is generally equal to FOREIGN PATENTS the cross-sectional area of said bores.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Arc Welding In General (AREA)
  • Hydraulic Motors (AREA)
US508249A 1965-11-17 1965-11-17 High efficiency hydraulic apparatus Expired - Lifetime US3345916A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US508249A US3345916A (en) 1965-11-17 1965-11-17 High efficiency hydraulic apparatus
GB23469/66A GB1120809A (en) 1965-11-17 1966-05-25 Improvements in or relating to hydraulic pumps and motors
SE7623/66A SE313501B (de) 1965-11-17 1966-06-03
NL6608369A NL6608369A (de) 1965-11-17 1966-06-16
DE19661528598 DE1528598A1 (de) 1965-11-17 1966-06-22 Hydraulische Kraft- oder Arbeits-Maschine mit rotierendem Zylinderblock
NO163628A NO125248B (de) 1965-11-17 1966-06-24
DK420066AA DK118168B (da) 1965-11-17 1966-08-16 Hydraulisk radialstempelpumpe eller -motor.
BE686040D BE686040A (de) 1965-11-17 1966-08-26
CH1237466A CH460538A (fr) 1965-11-17 1966-08-26 Dispositif hydraulique à déplacement volumétrique de fluide

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US508249A US3345916A (en) 1965-11-17 1965-11-17 High efficiency hydraulic apparatus

Publications (1)

Publication Number Publication Date
US3345916A true US3345916A (en) 1967-10-10

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ID=24021967

Family Applications (1)

Application Number Title Priority Date Filing Date
US508249A Expired - Lifetime US3345916A (en) 1965-11-17 1965-11-17 High efficiency hydraulic apparatus

Country Status (9)

Country Link
US (1) US3345916A (de)
BE (1) BE686040A (de)
CH (1) CH460538A (de)
DE (1) DE1528598A1 (de)
DK (1) DK118168B (de)
GB (1) GB1120809A (de)
NL (1) NL6608369A (de)
NO (1) NO125248B (de)
SE (1) SE313501B (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3520232A (en) * 1968-08-12 1970-07-14 Jaromir Tobias Radial piston pump and motor device
US4927338A (en) * 1987-03-02 1990-05-22 Nippondenso Co., Ltd. Radial piston pump
US5403238A (en) * 1993-08-19 1995-04-04 The Walt Disney Company Amusement park attraction
US5473990A (en) * 1993-08-19 1995-12-12 The Walt Disney Company Ride vehicle control system
US5583844A (en) * 1993-06-19 1996-12-10 The Walt Disney Company Programming device and method for controlling ride vehicles in an amusement attraction
US5623878A (en) * 1993-08-19 1997-04-29 The Walt Disney Company Dynamic ride vehicle
US5911561A (en) * 1995-01-05 1999-06-15 Linear Anstalt Radial pump with static eccentric and rotatable cylinders

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9900443D0 (en) * 1999-01-08 1999-02-24 Crittall Windows Ltd Ventilator

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1413388A (en) * 1919-08-04 1922-04-18 Sterling W Calhoun Fluid compressor
US1983261A (en) * 1931-03-07 1934-12-04 Zorxi Carlo Pump or compressor
US2205913A (en) * 1938-02-04 1940-06-25 French Oil Mill Machinery Pump
US2273468A (en) * 1939-10-20 1942-02-17 Oilgear Co Hydrodynamic machine
GB583396A (en) * 1944-09-13 1946-12-17 Thomas Desmond Hudson Andrews Improvements in or relating to air, gas or vapour compressors
US2510247A (en) * 1942-05-19 1950-06-06 Joseph S Parenti Apparatus for compressing fluids
US3034451A (en) * 1959-04-23 1962-05-15 United Aircraft Corp Pintle port construction for pumps
US3044412A (en) * 1958-05-13 1962-07-17 New York Air Brake Co High pressure hydraulic pump or motor
US3211105A (en) * 1962-01-11 1965-10-12 Stewart Warner Corp Hydraulic pump or motor

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1413388A (en) * 1919-08-04 1922-04-18 Sterling W Calhoun Fluid compressor
US1983261A (en) * 1931-03-07 1934-12-04 Zorxi Carlo Pump or compressor
US2205913A (en) * 1938-02-04 1940-06-25 French Oil Mill Machinery Pump
US2273468A (en) * 1939-10-20 1942-02-17 Oilgear Co Hydrodynamic machine
US2510247A (en) * 1942-05-19 1950-06-06 Joseph S Parenti Apparatus for compressing fluids
GB583396A (en) * 1944-09-13 1946-12-17 Thomas Desmond Hudson Andrews Improvements in or relating to air, gas or vapour compressors
US3044412A (en) * 1958-05-13 1962-07-17 New York Air Brake Co High pressure hydraulic pump or motor
US3034451A (en) * 1959-04-23 1962-05-15 United Aircraft Corp Pintle port construction for pumps
US3211105A (en) * 1962-01-11 1965-10-12 Stewart Warner Corp Hydraulic pump or motor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3520232A (en) * 1968-08-12 1970-07-14 Jaromir Tobias Radial piston pump and motor device
US4927338A (en) * 1987-03-02 1990-05-22 Nippondenso Co., Ltd. Radial piston pump
US5583844A (en) * 1993-06-19 1996-12-10 The Walt Disney Company Programming device and method for controlling ride vehicles in an amusement attraction
US5403238A (en) * 1993-08-19 1995-04-04 The Walt Disney Company Amusement park attraction
US5473990A (en) * 1993-08-19 1995-12-12 The Walt Disney Company Ride vehicle control system
US5623878A (en) * 1993-08-19 1997-04-29 The Walt Disney Company Dynamic ride vehicle
US5911561A (en) * 1995-01-05 1999-06-15 Linear Anstalt Radial pump with static eccentric and rotatable cylinders

Also Published As

Publication number Publication date
DE1528598A1 (de) 1970-07-09
GB1120809A (en) 1968-07-24
DK118168B (da) 1970-07-13
BE686040A (de) 1967-02-27
NL6608369A (de) 1967-05-18
NO125248B (de) 1972-08-07
SE313501B (de) 1969-08-11
CH460538A (fr) 1968-07-31

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