US3373696A - Fluid transmission devices - Google Patents

Fluid transmission devices Download PDF

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Publication number
US3373696A
US3373696A US455246A US45524665A US3373696A US 3373696 A US3373696 A US 3373696A US 455246 A US455246 A US 455246A US 45524665 A US45524665 A US 45524665A US 3373696 A US3373696 A US 3373696A
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US
United States
Prior art keywords
plate
caps
pistons
chambers
relative
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
US455246A
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English (en)
Inventor
Geyer Howard Marion
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.)
General Electric Co
Original Assignee
General Electric Co
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 General Electric Co filed Critical General Electric Co
Priority to US455246A priority Critical patent/US3373696A/en
Priority to GB20587/66A priority patent/GB1106486A/en
Priority to BE680842D priority patent/BE680842A/xx
Priority to DE19661653438 priority patent/DE1653438A1/de
Application granted granted Critical
Publication of US3373696A publication Critical patent/US3373696A/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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0064—Machine housing
    • F01B3/0067—Machine housing cylinder barrel bearing means
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/007—Swash plate
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0085—Pistons
    • F01B3/0088—Piston shoe retaining means
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/106—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by changing the inclination of the swash plate

Definitions

  • the present invention relates to improvements in uid transmission devices of the type which may be employed as either a pump or a motor.
  • the environment of the invention is found in such a device which comprises a pump body and a plurality of pistons reciprocable in chambers formed therein.
  • the ends of the pistons are so connected to a member which nutates or is otherwise moved relative to the piston body so that the pistons reciprocate within the pump body.
  • the pistons may be reciprocated to pressurize fluid when the device is used as a pump or pressurized iluid may be employed to reciprocate the pistons when the device is used as a motor. In either event fluid inlet and outlet passageways are brought into communication successively with the reciprocating pistons.
  • a pump environment but it is to be understood that at least the broader aspects of the invention will be equally applicable to a motor, as will be apparent to those skilled in the art.
  • the objects of the present invention are to provide a simple and economically manufactured device of the type referred to and in so doing to minimize, if not eliminate, the stress concentrations discussed above and further to actually minimize thrust forces which further contribute to excessive wear conditions.
  • a pump or the like comprising a pump body having a plurality of chambers formed therein generally parallel to each other and circularly arranged. Pistons are respectively reciprocable in these chambers and project outwardly therefrom. Inlet and outlet passageways respectively communicate with opposite ends of these chambers successively as the pistons rotate. Caps are socketed to receive ball ends formed on the outer ends of the pistons.
  • the caps have iianges disposed in a common plane coincident with the center about which the ball end is generated. A plate is relieved to receive the outer ends of the caps encompassing the ball ends being the flanges so that the anges may engage a bearing surface on the plate also lying on this common plane.
  • Means are provided for nutating the plate relative to the pump body to control and impart reciprocation to the pistons.
  • cam plate having a bearing surface opposed to the pistons projecting from the pump body.
  • the cam plate and pump body are relatively rotatable and the piston chambers are disposed generally parallel to and concentric of the axis of relative rotation.
  • the bearing surface on the cam plate is disposed at an angle to a plane normal to the axis of relative rotation.
  • the nutating plate has opposed surfaces which are preferably parallel. One of these opposed surfaces bears against the angled surface of the cam plate and the other bears against the flanges of the caps.
  • the nutating plate is preferably provided with through holes to receive the outer ends of the caps, which holes are sealed at one end by the cam plate and at the opposite end by the cap flanges to form chambers in the nutating plate.
  • Passageway means are provided from the piston chambers to these plate chambers so that pressurized fluid, usually a lubricating liquid, may also pressurize the chambers in the plate to provide a counterbalancing force to the thrust force which is transmitted from the pistons to the cam plate as the device is in operation.
  • FIG. 1 is a sectional elevation of a pump embodying the present invention.
  • FIG. 2 is a section taken on line II-II in FIG. l;
  • FIG. 3 is a section taken on line III-III in FIG. l.
  • FIG. 4 is a perspective view of a modified embodiment of the invention.
  • the pump seen in FIGS. 1-3 comprises a housing 10 secured to a base piate 12 by screws 14.
  • the base plate 12 has inlet and discharge ports numbered 16 and 18 respectively which in turn are connected to conduits (not shown) for conducting fluids, usually liquids, to and from the pump.
  • the base of a pump body 20 sealingly engages the upper surface of the plate 12 and overlies the ports 16 and 18.
  • a plurality of cylindrical chambers 22 formed inthe pump body 20 are successively registerable with the ports 16 and 18.
  • a piston 24 is slidably received in each of the chambers 22.
  • Each of the pistons 24 is formed with a ball end 26 which is received by a socket in a cap 28. These sockets are swaged to retain the ball ends 26 therein.
  • the caps 28 bear against the undersurface of a plate 30 which wobbles or nutates relative to the pump body 20.
  • the pump body 20 is rotated relative to a xed cam plate 32 to obtain the wobble action referred to.
  • the pump body 20 is joined to the lower end of a shaft 34 by a straight spline connection at 36.
  • the plate 30 rotates at the same rate as the pump body about the axis of shaft 34 as provided for by the spherical spline connection indicated at 38.
  • the upper end of the shaft 34 is appropriately journaled in the housing 10 and projects therethrough for connection to a rotary power source to be driven in the direction indicated by the arrow.
  • the plate 3@ nutates about a horizontal axis y.
  • the spherical spline connection 38 accommodates this nutating action while maintaining a drive connection between the shaft 34 and the plate 3i) so that relative angular movement, about axis x, between plate 30 and pump body 20 is prevented.
  • the upper surface of the plate 30 is socketed at 39 to receive the lower portion of the plate 32 to thus laterally position the plate 30 as it nutates.
  • the nutating or wobble movement of the plate 3i) causes the pistons 30 to reciprocate in the chambers 22 so that as they move upwardly, liquid is drawn from the inlet port 16 and discharged under positive pressure through the discharge port 18.
  • the right hand piston 24 (FIG. 1) will next move downward and exert a bearing load on plates 30, 32 as it discharges liquid from its chamber 22.
  • the left hand piston 24 will move upwardly to draw liquid into its chamber 22.
  • a plurality of clips 41 may be secured to the plate 30 by screws 43. These clips form slots 45 which capture the lower portions of the caps to retain them against the plate during a suction stroke.
  • the tilt plate 32 While the tilt plate 32 is stationary in normal operation, it is also adjustable about an axis normal to and intersecting the axes x and y in order to control lthe volume and capacity of a given pump.
  • the cam plate 32 is mounted on trunnions 49 (indicated in FIG. 1) which are appropriately journaled. Means ⁇ (not shown) are then provided to tilt the plate 32 on the trunnions 4t) to and lock it at a desired angle.
  • the upper surface of the plate 32 is cylindrically formed and engages rolls 42 to provide a thrust support for the plate 32 in any position to which it is to be adjusted. ⁇
  • the spherical ball ends 26 are each generated about respective centers which lie in a common plane z.
  • the sockets in the caps 28 are correspondingly formed to receive the ball ends 26 with a close t permitting esse-ntially free swivelling movement.
  • the upper ends of the caps 28 are received by clearance holes 44 in the plate 30.
  • the actual surface on each cap which transmits a thrust load to the plate 30 is an annular flange surface 46 which lies in the plane z, as does the lower bearing surface of the plate 30 which surface is preferably parallel to its opposed upper surface that engages the angled bearing surface of the cam plate 32.
  • the forces acting on the caps 28 are relatively complex and involve not only a vertical thrust load but also a horizontal component of this thrust load. Further as the plate 36 nutates, there is relative radial movement (referenced to axis x) between it and the caps 23 as will be evident from FIG. 3. This causes nutation of the caps 28 on the ball ends 26. The coincidence of the centers for the ball ends 26 on plane z is effective in preventing any forces, incident to this compound movement which might cause the caps 28 to tilt relative to the plate 30 and cause a stress concentration. There may be rotation of the caps 28 relative to the ball ends 26 or plate 30, but this tendency is also minimized by the coincident relationship referred to and by the fact that there is no direct contact between the caps 28 and the fixed angle plate 32. The upper surface of the plate 30 transmits the thrust load to the stationary plate 32 and because of its large surface contact therewith there is little or no tendency for relative tipping therebetween.
  • the described arrangement provide for the transmission of thrust forces from the rotating and reciprocating pistons 24 to the stationary angle plate 32 in a manner which minimizes stress concentrations and gives optimum wear under a wide range of operating conditions, it enables the provision of countcrbalancing lubrication forces which further minimize wear and the power requirements for operation of the pump.
  • the flange surfaces 46 sealingly engage the undersurface of the nutating plate 30 and the upper surface of the latter sealingly engages the xed angle plate 32.
  • the ends of the holes 44 are thus sealed to form closed chambers.
  • a bleed hole 4S is formed in the upper end of each piston 24 and opens into a countersink S0 in the upper surface of each ball end 26.
  • a hole 52 in each of the caps 28 is thus able to maintain the chambers in plate 3i) in communication with the piston chambers 22 at all times.
  • the chambers in platepsi) are thus at essentially the same pressure as the piston chambers 22 at all times.
  • the diameter of the holes 44 is preferably somewhat less than that of the chambers 22 so that the effective forces on the caps 28 and plate 32 minimize the thrust forces on the nutating plate 3i) without causing actual separation or excessive leakage therebetween.
  • FIG. 4 illustrates another embodiment of the invention in which an alternate means is employed to rotate a nutating plate 30 simultaneously with the pump body 2t).
  • the shaft 34 and plate 30 have been modified to eliminate the spherical spline connection therebetween as described in the previous embodiment.
  • Further pintles 54 project from opposite sides of the plate 30 and carry journal blocks 56 thereon. These journal blocks are guidingly received in slots 58 formed in a shroud l60, secured to the pump body 20 for rotation therewith.
  • the remaining components of the pump may be as before and those seen in FIG. 4 are identified by like reference characters.
  • the described pump may also be used as a motor by the appropriate introduction of pressurized uid into the piston chambers.
  • the cam plate 32 may be rotated relative to the pump body 2i) to obtain the desired nutating action.
  • a pump or the like comprising,
  • said pump body having a plurality of circularly arranged chambers generally parallel to the axis of relative rotation
  • cam plate having a bearing surface facing said pump body and angled from a plane normal to the axis of relative rotation
  • pistons respectively reciprocable in said chambers and projecting from one end thereof towards said cam plate
  • said caps further having flanges disposed in a common plane, which plane is coincident with the centers about which the ball ends are generated,
  • a pump or the Ilike comprising,
  • said pump body having a plurality of circularly arranged cylindrical -chambers concentric of and generally parallel to the axis of relative rotation
  • cam plate having a bearing surface facing said pump body and angled from a plane normal to the axis of relative rotation
  • pistons respectively reciprocable in said chambers and projecting from one end thereof toward said cam plate
  • said caps further having anges disposed in a common plane, which plane is coincident with the centers about which the ball ends are generated,
  • said wobble plate having clearance holes therethrough receiving the portions of said caps outwardly of said common plane
  • a pump or the like comprising,
  • said pump body having a plurality of circularly arranged cylindrical chambers concentric of and generally parallel to the axis of relative rotation
  • cam plate having a bearing surface facing said pump body and angled from a plane normal to the axis of relative rotation
  • pistons respectively reciprocable in said chambers and projecting from one end thereof toward said cam plate
  • said caps further having uninterrupted anges disposed in a common plane which plane is coincident with the centers about which the ball ends are generated,
  • said wobble plate having clearance holes therethrough receiving the portions of said caps outwardly of said common plane
  • a pump or the like comprising,
  • said pump body having a plurality of circularly arranged cylindrical chambers concentric of and general'ly parallel to the axis of relative rotation
  • cam plate having a bearing surface facing said pump body and angled from a plane normal to the axis of relative rotation
  • pistons respectively reciprocable in said chambers and projecting from one end thereof toward said cam plate
  • said caps further having uninterrupted flanges disposed in a common plane which plane is coincident with the centers about which the ball ends are generated,
  • said wobble plate having clearance holes therethrough receiving the portions of said caps outwardly of said common plane
  • a pump or the like comprising,
  • pistons respectively reciprocable in said chambers, projecting from one end thereof and having spherical ball ends,
  • said caps further having uninterrupted ange portions disposed in a common plane which plane is coincident with the centers about which the ball ends are generated,
  • a pump or the like comprising a pump body having generally parallel chambers therein,
  • each of said pistons having a cap spherically mounted on the outer end thereof, each of said caps having ,a ange lying in a plane coincident with the center of the spherical mount therefor,
  • said plate being relieved to receive the portions of said caps outwardly of said flanges, with said flanges engaging the rst bearing .surface of said plate for the transmission of thrust forces thereto,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US455246A 1965-05-12 1965-05-12 Fluid transmission devices Expired - Lifetime US3373696A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US455246A US3373696A (en) 1965-05-12 1965-05-12 Fluid transmission devices
GB20587/66A GB1106486A (en) 1965-05-12 1966-05-10 Improvements in axial piston pumps or motors
BE680842D BE680842A (cs) 1965-05-12 1966-05-11
DE19661653438 DE1653438A1 (de) 1965-05-12 1966-05-11 Stroemungsmittelgetriebe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US455246A US3373696A (en) 1965-05-12 1965-05-12 Fluid transmission devices

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US3373696A true US3373696A (en) 1968-03-19

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US455246A Expired - Lifetime US3373696A (en) 1965-05-12 1965-05-12 Fluid transmission devices

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BE (1) BE680842A (cs)
DE (1) DE1653438A1 (cs)
GB (1) GB1106486A (cs)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3589244A (en) * 1969-01-29 1971-06-29 Renault Barrel-type hydraulic motors and pumps
US3739692A (en) * 1968-09-06 1973-06-19 Reyrolle Hydraulics Ltd Swashplate and like hydraulic machines
US3828654A (en) * 1972-08-03 1974-08-13 Fmc Corp Piston for torque transmitting apparatus of the swash plate type
US4478134A (en) * 1980-10-31 1984-10-23 Honda Giken Kogyo Kabushiki Kaisha Swash plate type hydraulic device
US5167181A (en) * 1991-12-04 1992-12-01 Ken Lee W Fluid transfer devices
US20100300281A1 (en) * 2007-05-14 2010-12-02 Robert Bosch Gmbh Retaining segment
US20100307330A1 (en) * 2007-05-14 2010-12-09 Robert Bosch Gmbh Axial piston machine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT408898B (de) * 1998-04-27 2002-03-25 Joerg Thurner Axialkolbenverstellmaschine

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2168658A (en) * 1936-12-24 1939-08-08 Waterbury Tool Co Power transmission pump or motor
US2555479A (en) * 1947-07-11 1951-06-05 Nathan Mfg Co Variable discharge pump and control therefor
US2776629A (en) * 1952-07-10 1957-01-08 Vickers Inc Power transmission
US2864456A (en) * 1955-08-02 1958-12-16 Research Corp Automatic control for electrical precipitators
US2880042A (en) * 1957-06-20 1959-03-31 New York Air Brake Co Piston
FR1269286A (fr) * 1960-06-30 1961-08-11 Pompe et moteur à débit variable
US3006284A (en) * 1961-10-31 Swash-plate pump
US3050014A (en) * 1959-06-18 1962-08-21 United Aircraft Corp Pump timing device
US3073254A (en) * 1959-12-24 1963-01-15 United Aircraft Corp Pressure balanced pump
US3143858A (en) * 1963-02-19 1964-08-11 Borg Warner Hydrostatic transmission
US3198130A (en) * 1962-04-06 1965-08-03 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3240159A (en) * 1962-07-20 1966-03-15 Dowty Hydraulic Units Ltd Hydraulic apparatus

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3006284A (en) * 1961-10-31 Swash-plate pump
US2168658A (en) * 1936-12-24 1939-08-08 Waterbury Tool Co Power transmission pump or motor
US2555479A (en) * 1947-07-11 1951-06-05 Nathan Mfg Co Variable discharge pump and control therefor
US2776629A (en) * 1952-07-10 1957-01-08 Vickers Inc Power transmission
US2864456A (en) * 1955-08-02 1958-12-16 Research Corp Automatic control for electrical precipitators
US2880042A (en) * 1957-06-20 1959-03-31 New York Air Brake Co Piston
US3050014A (en) * 1959-06-18 1962-08-21 United Aircraft Corp Pump timing device
US3073254A (en) * 1959-12-24 1963-01-15 United Aircraft Corp Pressure balanced pump
FR1269286A (fr) * 1960-06-30 1961-08-11 Pompe et moteur à débit variable
US3198130A (en) * 1962-04-06 1965-08-03 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3240159A (en) * 1962-07-20 1966-03-15 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3143858A (en) * 1963-02-19 1964-08-11 Borg Warner Hydrostatic transmission

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3739692A (en) * 1968-09-06 1973-06-19 Reyrolle Hydraulics Ltd Swashplate and like hydraulic machines
US3589244A (en) * 1969-01-29 1971-06-29 Renault Barrel-type hydraulic motors and pumps
US3828654A (en) * 1972-08-03 1974-08-13 Fmc Corp Piston for torque transmitting apparatus of the swash plate type
US4478134A (en) * 1980-10-31 1984-10-23 Honda Giken Kogyo Kabushiki Kaisha Swash plate type hydraulic device
US5167181A (en) * 1991-12-04 1992-12-01 Ken Lee W Fluid transfer devices
US20100300281A1 (en) * 2007-05-14 2010-12-02 Robert Bosch Gmbh Retaining segment
US20100307330A1 (en) * 2007-05-14 2010-12-09 Robert Bosch Gmbh Axial piston machine
US8261654B2 (en) * 2007-05-14 2012-09-11 Robert Bosch Gmbh Axial piston machine having swivel cradle actuating pistons and displacement limiting devices
US8555773B2 (en) * 2007-05-14 2013-10-15 Robert Bosch Gmbh Retaining segment

Also Published As

Publication number Publication date
BE680842A (cs) 1966-10-17
GB1106486A (en) 1968-03-20
DE1653438A1 (de) 1971-04-08

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