US3304885A - Piston pump lubrication structure - Google Patents

Piston pump lubrication structure Download PDF

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Publication number
US3304885A
US3304885A US452090A US45209065A US3304885A US 3304885 A US3304885 A US 3304885A US 452090 A US452090 A US 452090A US 45209065 A US45209065 A US 45209065A US 3304885 A US3304885 A US 3304885A
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Prior art keywords
shaft
passageways
pump
extending
fluid
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US452090A
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Harold R Orth
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Navistar Inc
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International Harverster Corp
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Priority to US452090A priority Critical patent/US3304885A/en
Priority to GB6335/66A priority patent/GB1141705A/en
Priority to DE19661653477 priority patent/DE1653477A1/de
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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
    • 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
    • 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
    • F01B3/0047—Particularities in the contacting area between cylinder barrel and valve 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
    • F01B3/0032—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
    • F01B3/0073—Swash plate swash plate bearing means or driving or driven axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type
    • F16H39/08—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders
    • F16H39/10—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders with cylinders arranged around, and parallel or approximately parallel to the main axis of the gearing

Definitions

  • an axial piston pump when driven mechanically, it functions as a pump to pump a working fluid from a low pressure source into a high pressure outlet line; and when it is supplied with a relatively high pressure flow of fluid, the pump functions as a motor to supply a mechanical output of power. Consequently, while for purposes of simplification the invention will be referred to as a pump in the description and claims which follows, it should be clear that the invention may be employed with equal advantages when the invention is functioning as a motor.
  • an object of the invention is to provide an improved axial piston pump.
  • Another object of the invention is to provide an axial piston pump having an improved lubrication structure to permit operation at higher speeds.
  • Still another object of the invention is to provide a simple relatively foolproof axial piston pump arrangement to achieve forced lubrication and cooling of the pump components.
  • Still another object of the invention is to provide an improved axial piston pump lubricating system to achieve selective lubrication of internally disposed pump compo nents such as pump shaft bearings, valve plates, and shaft splines as well as relatively inaccessible internal surfaces of pump slippers, slipper retaining guides and thrust plate.
  • internally disposed pump compo nents such as pump shaft bearings, valve plates, and shaft splines as well as relatively inaccessible internal surfaces of pump slippers, slipper retaining guides and thrust plate.
  • Yet another object of the invention is to provide an improved axial piston pump structure to achieve internal lubrication of the pump components to permit safe operation of the pump at relatively high operating speeds of over about 3000 r.p.m.
  • a further object of the invention is to provide a lubricating system for an axial piston pump operating in a dry sump where pump components are not picking up lubricating fluid by rotation within a fluid, and to achieve lubrication of the pump without churning power losses associated with submerged pump operation.
  • Sill another object of the invention is to provide a forced lubricating system for a hydrostatic transmission incorporating an axial piston pump and an axial piston motor coaxially arranged and cooperating fo operation at high speeds of over about 3000 r.p.m., the lubricating system directing a central flow of lubricating and cooling fluid to internal components of the pump and motor.
  • FIG. 1 is,a somewhat schematic, simplified sectional view of an embodiment of an axial piston pump constructed in accordance with the present invention
  • FIG. 2 is a somewhat schematic, sectional view of a hydrostatic transmission including an axial piston pump and an axial piston motor both constructed in accordance with the teachings of the present invention
  • FIG. 3 is a somewhat schematic simplified sectional view similar to FIG. 1 of another embodiment of an axial piston pump constructed in accordance with the invention
  • FIG. 4 is a schematic representation of a flow diagram of an axial piston pump as illustrated in FIGS. 1' and 3;
  • FIG. 5 is a schematic representation of a flow diagram of a hydrostatic transmission as illustrated in FIG. 2;
  • FIGS. 6 and 7 are end sectional views taken along the lines 66 and 7-7 respectively of FIG. 1;
  • FIG. 8 is an enlarged sectional view taken along the 0 line 88 of FIG. 6 showing a valve plate portion of the axial piston pump of FIG. 1;
  • FIGS. 9 and 10 are end sectional views taken along the lines 99 and 10-10 respectively of FIG. 3;
  • FIG. 11 is an enlarged sectional view taken along the line 11-11 of FIG. 9;
  • FIG. 12 is an enlarged somewhat schematic sectional view of another embodiment of an axial piston pump similar to the showings of FIGS. 8 and 11 but constructed without valve plates;
  • FIGS. 13 and 14 are end sectional views taken along the lines 1313 and 14-14 respectively of FIG. 12.
  • FIG. 1 shows an axial piston pump 10 including a rotatable cylinder block 12 having a plurality of axially extending splines, the block being splined on a rotatable drive shaft 14 driven by an associated source of power such as a vehicle engine 15, FIG. 4, the shaft 14 having a plurality of axially extending splines 16 complementary to the cylinder block splines for rotation of the cylinder block with the drive shaft 14;
  • the cylinder block 12 has a plurality of axial cylinder bores 18 therein, each housing one of a plurality of reciprocable pistons 20, each of the pistons 20 having a ball or outer end 22 force fitted within individual sockets 23 provided for this purpose in a pump sockcted bearing surface or slipper 24.
  • First and second valve plates 32, 28 respectively are provided for receipt or exhaust of a fluid from the cylinder bores 18.
  • the cylinder block 12 is biased by .a cylinder block spring 26 against the second or right valve plate 28 pinned to or integral with the cylinder block 12 for rotation therewith.
  • the valve plate 28 comprises a bearing plate which may be but is not necessarily integral with the block 12 having a flat valving surface 30.
  • the first Valve plate or port plate 32 having a flat complementary valving surface 34 which bears or slides against the fiat face 38 of the right valve plate 28.
  • the first valve plate 32 is pinned to a housing 36, although it may be integral with the housing 36, a portion of which is shown in the drawing, and is thus maintained stationary.
  • the first and second valve plates 32, 28 are formed with complementary arcuate shaped ports 40, 38 for successive fluid communication with ports 42 in the cylinder bores 18 as the cylinder block 12 rotates to admit and exhaust a working fluid, not shown, to and from the cylinder bores 18, as is well known in the art.
  • the ball ends 22 of the pistons 28 cooperate with a swash plate assembly includin a swash plate 44 pivotable about the drive shaft 14 by means of a pair of trunnions 46, 48 having a plurality of trunnion bearings 50 comprising tapered roller bearings supporting the swash plate 44.
  • the swash plate 44 is pivoted between a minimum displacement neutral position approximateiy as shown in FIG. 1 to maximum displacement positions, as shown generally in FIG. 2, at opposite sides of the center position in order to vary the fluid displacement of the pump.
  • the pump drive shaft 14 is connected for rotation with an input shaft, not shown, to rotate the drive shaft.
  • the swash plate 44 has a generally cylindrical inner portion 54 with an annular thrust plate 56 therein providing a flat bearing surface 57 for the slipper 24 which slides thereon.
  • a slipper retainer 58 and slipper retainer guide 60 are provided to maintain the slipper in bearing position against the thrust plate 56, the slipper retainer guide 60 being biased to the right, as viewed in the figure, by a slipper retainer spring 62.
  • the slipper retainer guide 60 is splined to the shaft 14 for rotation therewith and has a generally spherical outer surface 64 on which a complementally spherically shaped inner surface 66 of the slipper retainer 58 slides.
  • First and second main shaft bearings 68, 70 are positioned at the left and right ends of the main shaft to support the shaft 14 for rotation within the pump housing 36.
  • the rotatable main shaft 14 is provided with an axially extending central passageway 74 in communication with a plurality of first, second and third radial passageways or openings 76, 78, 80 in communication therewith for receipt of a lubricating fluid.
  • the first radial passageways 76 are comm-unicatively connected to the first main shaft bearing 68 which is in communication with a plurality of radially extending passageways 84, 82 provided respectively in the first and second valve plates 32, 28 to carry a lubricating fluid radially about the valve plates to dissipate the heat generated by the intermediate rubbing surfaces 34, 30 of the valve plates.
  • the splined area of the pump shaft 14, extending axially from an intermediate portion 86 of the shaft toward the right end of the shaft adjacent the pump slippers 24, is subject to considerable wear and fretting due to rotational deflection.
  • the splines 16 of the shaft and the splines, not shown, of the cylinder block 12 are slightly undercut to provide undercut spline passageways designated by the numeral 85 for the flow of lubricating fluid.
  • the second or intermediate radial passageways 78 are positioned immediately adjacent the spline-d area at the left or valve plate end of the splines 16 and are in communication with the undercut passageways 85 provided in the splined area.
  • the right hand end of the cylinder block is notched at points indicated by the numeral 86 and a plurality of radial openings 87 in line therewith are provided in the slipper retainer guide 60, the openings 87 being in communication with the intermediate radial passageways 78 by means of the undercut spline passageways 85 for receipt of lubricating fluid therefrom.
  • the third radial passageways 86 are positioned at the right end of the axially extending central passageway 74 at the right hand end of the pump shaft 14 leading to and being in communication with the right shaft bearing 70 to direct a flow of lubricating fluid through the hearing.
  • the annular thrust plate 56 has an inner edge 90 adjacent the slipper retainer guide 60 which edge 98 is chamfered so as to encourage the flow of lubricating fluid flowing radially outwardly from the openings 85, 87 to flow over surface 57 rather than through opening 89.
  • Conventional means 180, FIG. 4 are provided to direct a flow of lubricating fluid under pressure from a reservoir 182 to the pump 10 at the left end of the axially extending central assageway 74 in the pump shaft 14, with arrows indicating the direction of flow. Fluid enters the pump at the valve plate area and travels axially to the right through the passageway 74 entering the first, second and third radial passageways 76, 78 and 80. Lubricating fluid first enters radial passageway 76 flowing through and lubricating the main shaft bearings 68 and then flowing radially outwardly through the valve plate passageways 82, 84 to cool the valve plates, the fluid then being directed by conventional means, not shown, to a fluid reservoir 182, FIG. 4.
  • the lubricating fluid from the intermediate radial passageways 78 then sprays centrifugally outwardly from the slipper retainer guide openings 87 to lubricate and cool the surfaces of the slipper retainer guide 60, slipper 24 and slipper retainer 58; and the fluid continues in a spray radially outwardly through openings, not shown, provided in the swash plate 44 to lubricate the trunnion bearings 50, as indicated by the arrows, before returning to the fluid reservoir 182, FIG. 4.
  • the third radial passageway 80 in fluid communication with the right shaft bearings 70 permits flow of lubricating fluid from axial passageway 74 through the right shaft bearings 70 with means, not shown, provided in the pump housing for return of the lubricating fluid to the fluid reservoir 182, FIG. 4.
  • first and second valve plates 32, 28 are constructed may best be seen by reference to FIGS. 6 to 8 shown in conjunction with an axial piston pump similar to that illustrated in FIG. 1 but utilizing conventional straight roller bearings 68b instead of the tapered roller bearings 68 utilized in the embodiment of FIG. 1.
  • the second valve plate 28, FIG. 7, has
  • arcuate shaped ports 38 forming no part of the present invention, and has'an inner annular ring 198 and an outer annular ring 200 straddling the ports 38, the rings 198, 200 being connected communicatively by radial passageways 82 with inner and outer radial passageways 202, 204 respectively, passageways 202 communicatively connecting the inner ring 198 to the area about the first main shaft bearing 68 and passageways 204 carrying lubricating fluid radially outwardly from the outer ring 200 to the peripheral edge of the valve plate 28 and thence to the reservoir.
  • the first valve plate 32 constructed in a similar manner to valve plate 28, has an inner ring or annular fluid channel 190 and an outer ring or annular fluid channel 192 straddling ports 40 and being communicatively connected by radially extending passageways 84, with inner radial passageways 194 provided to connect the inner ring 190 communicatively with fluid from the fluid area about the first main shaft bearing, with outer radial passageways 196 provided to connect communicatively the outer ring 192 to the peripheral edges of the first valve plate 32 and thence to reservoir.
  • FIG. 3 and FIGS. 9-11 Another embodiment of the invention is illustrated in FIG. 3 and FIGS. 9-11 wherein like parts are designated by like numerals with the addition of the sufiix a for identification.
  • FIG. 3 is a conventional axial piston pump similar to the axial piston pump of FIG. 1 and designated generally by the numeral 10a, an additional description of such similar conventional features will not be given. Rather, those features, wherein the pump of FIG. 3 differs from the pump of FIG. 1 and which features embody the concepts of the present invention, will be described.
  • the axial piston pump 10 includes a housing 36a having a passageway 190 which is in fluid communication with a source 180a of lubricating fluid under pressure.
  • An antifriction bearing 68a supporting one end of pump shaft 14a is in communication with radial fluid passageways 212, 84a provided in valve plates 28a and 32a; and the bearing 68a is also in fluid communication with a fluid chamber 192 provided about spring 26a.
  • the chamher 192 is in fluid communication with undercut splined passageways 85a provided about the splined area 16 of the shaft by means of a passageway 194 in the housing about shaft 14.
  • cylinder block 12a is notched at points indicated by the numeral 86a and a plurality of radial openings 87a in line therewith are provided in the slipper retainer guide 60a, the openings 87a being in communication with the undercut splined passageways 85a for receipt of lubricating fluid therefrom.
  • Annular thrust plate 56a has an inner edge 90a adjacent the slipper retainer guide 60a which edge 90a is chamfered so as to direct the flow of lubricating fluid radially outwardly from opening 86a, 87a in the slipper retainer guide 60a to flow over surface 57a of thrust plate 56a rather than through opening 89a, the openings 87a being in communication with the undercut splined passageways for receipt of lubricating fluid.
  • Conventional means 180a are provided to direct the flow of lubricating fluid under pressure from a source 182a of lubricating fluid to the axial piston pump 10a,
  • lubricating fluid moving through opening 190 at the left end of housing 36a with arrows indicating the direction of flow. Fluid then enters the anti-friction bearings 68:: where a portion of the flow moves radially outwardly through the valve plate passageways 82a, 84a to cool the valve plates, the fluid then being directed by conventional means, not shown, to the fluid reservoir.
  • the lubricating fluid then sprays centrifugally outwardly from the slipper retainer guide openings 87a to lubricate and cool the surfaces of the slipper retainer guide 60a, slipper 24a and slipper retainer 58a; and the fluid continues to spray radially outwardly through openings, not shown, in the swash plate 44a, to lubricate trunnion bearings 50a, the fluid then being directed by conventional means, not shown, to the fluid reservoir.
  • FIGS. 9-11 A first valve plate or port plate 32a is illustrated in FIG. 9 pinned to the housing 36a, the plate being similar in construction to valve plate 32, FIG. 6, including inner and outer rings 190a, 192a, inner and outer radial passageways 194a, 196a and intermediate radially extending passageways 84a communicatively connecting the inner and outer rings 190a, 192a.
  • fluid is directed radially outwardly from about the first main bearing 68a to radial passageways 194a, inner ring 190a radially extending passageways 84a and 212, FIG. 10, to the outer ring 192a and via outer radial passageways 196a to the reservoir.
  • the cylinder barrel 12a is provided with a valving surface 205 which is complementary to the flat valve face of valve plate 320.
  • Cylinder barrel 12a has complementary inner and outer rings 206, 208 and arcuate ports 38a similar to the ports of the second valve those utilized in FIGS. 9-11 with the addition of the suffix c for identification.
  • the axial piston pump designated generally by the numeral 100, with only a portion of the pump being illustrated, includes a cylinder block 12c and a housing or end cap 360, FIG. 13.
  • End cap 360 has arcuate shaped ports 40c therein and has a valving surface, designated generally by the'numeral 214 which is complementary to a flat valving surface 216 of the cylinder barrel 12c.
  • the cylinder barrel 120 is provided with arcuate ports 38c, inner and outer rings 206e, 208a, inner radial passageways 210e, radially extending passageways 212e, and outer radial passageways 217 communicatively connecting the inner ring 206c to the outer ring 2080 and thence to the outer periphery of the cylinder barrel and to a reservoir, not shown.
  • a hydrostatic transmission designated generally by the numeral 92 having an axial piston pump 96 and an axial piston motor 98 coaxially arranged with a transmission housing, not shown, with a common central stationary section 100 ing pump and motor valve plates 109, 111 pinned to opposite sides thereof, the central section'100 being stationarily mounted within the transmission housing.
  • the respective pump and motor cylinder blocks 101, 103 of the pump and motor 96, 98 are biased by springs, not
  • the pump and motor second valve plates 102, 104 and central sechav-' motor cylintion 100 with its first valve plates 109, 111 are formed with complementary cooperating arcuate shaped inlet and outlet ports indicated respectively by the numerals 106, 108 in the pump and motor second valve plates 102, 104 and by the numerals 110, 113, 115 in the center section 100 and pump and motor first valve plates 109, 111 respectively for successive communication with ports 112, 114 in cylinders 116, 118 of the pump and motor cylinder blocks 101, 103.
  • Outer ball ends 120, 121 of pistons 122, 123 in the pump and motor respectively cooperate with swash plate assemblies 124, 126 similar to the assembly illustrated in FIG. 1 and including pump and motor swash plates 128, 130, pump and motor thrust plates 132, 134, pump and motor slippers 136, 138, pump and motor slipper retainers 140, 142 and pump and motor slipper retainer guides 144, 146.
  • Ball ends of the pump and motor pistons 122, 123 cooperate with the swash plates 128, 130 which are pivotable in opposite directions from a minimum displacement neutral center position such as illustrated in FIG. 1 to a maximum displacement position with the swash plate 128, 130 generally as illustrated in FIG. 2 in order to vary the displacement of the pump, as is well understood in the art.
  • a pump drive shaft 140 is connected for rotation with an input shaft, not shown, adapted to be driven by a prime mover such as an internal combustion engine 41, FIG. 5, conventionally associated with tractors and the like.
  • the motor 98 is identical in construction to the pump 96 but may be somewhat larger than the pump 96 as indicated generally in FIG. 5, with the motors cylinder block 103 .splined on an output shaft 142 for rotation therewith.
  • the arcuate ports 108 and 115 of the motor valve plates 104 and 111 cooperate with ports 110 of the center section 100 and the valve plate ports 113 and 106 of the pump valve plates 102 and 109 so that the pump and motor are connected in a closed, closely cou pled hydraulic circuit.
  • Ball ends 121 of the motor pistons cooperate with the motor swash plate assembly 126 which is variable between a minimum allowable displacement position as illustrated in FIG. 1 and a maximum displacement position as illustrated in FIG. 2.
  • the motor shaft 142 is connected to an output shaft, not shown, adapted to be connected to the propelling wheels of an associated vehicle such as a tractor.
  • the swash plate assemblies 124, 126 are controlled by means, not shown, such as by hydraulically actuatable piston assemblies, as is well known in the art.
  • the pump and motor shafts 140, 142 are each provided with a central axially extending lubricant passageway 144, 146 respectively with first, second and third radially extending pump passageways 148, 150, 152 in communication with axial pump passageway 144 and corresponding to first, second and third radial passageways 76, 78, 80 as illustrated in FIG. 1.
  • First, second and third radially extending motor passageways 154, 156, 158 in communication with the axially extending center motor passageway 146 are also provided. Additional passageways for flow of lubricating fluid are provided in the pump 96 and motor 98 similar to those provided in the pump, FIG.
  • pump and motor splines 160, 162 which are slightly undercut providing undercut spline passageways in communication with the second or intermediate radial passageways 150, 156 and leading communicatively to cylinder block notches, not shown, and slipper retainer guide openings 164, 166 providing lubrication respectively for the pump and motor thrust plates, slippers, slipper retainers, and slipper retainer guides.
  • the pump and motor radial passageways 148, 150, 152 and 154, 156, 158 provide lubrication for pump and motor main shaft bearings 168, 170 and other bearings, not shown, supporting the shaft for rotation and further provide coolant for the pump and motor second valve plates 102 and 104, first valve plates 109 and 111 and 3 center section by means of radially extending tanking grooves or passageways provided in the valve plates, being in communication with shaft bearings 168, 170.
  • Conventional means 184, FIG. 5, provide a flow of lubricating fluid under pressure to the axial shaft passageways 144, 146 as by a radial opening 172 in the center section 100 in communication with the pump and motor axial passageways 144, 146 thus providing a central common fiow of lubricant and ensuring selective forced lubrication and cooling of the various wearing surfaces of the pump and motor to permit safe and efficient operation of the hydrostatic transmission at high speeds of over about 3000 to 4000 r.p.m.
  • an axial piston pump including a housing, a rotatable drive shaft extending through said housing, said shaft having first and second ends, first and second antifriction bearings supporting said shaft at its first and second ends respectively for rotation within said housing, said shaft having an outer area having a plurality of splines extending axially from a first point at an intermediate location on said shaft and extending to a second point adjacent the second end of said shaft, a cylinder block having first and second spaced ends and a plurality of axially extending splines being complementally positioned to the splines on said shaft for rotation therewith, said cylinder block having a plurality of axial cylinder bores, a plurality of pistons, each of said bores housing one of said pistons for reciprocation therein, said pistons each having a ball portion at one end thereof, said ball portions extending outwardly from said cylinder bores toward the second end of said shaft and being fitted within socketed bearing surfaces, a swash plate assembly being positioned about the shaft at least
  • An axial piston pump to be operated at high speeds in a dry sump, comprising a housing; a rotating drive shaft extending through said housing, said shaft having first and second ends; first and second anti-friction bearings mounted in said housing supporting said shaft at its first and second ends respectively for rotation within said housing, said shaft having an outer area having a plurality of axially extending splines extending from a first point intermediate said first and second ends of said shaft and extending to a second point adjacent said second end of said shaft; a cylinder block splined to said shaft for rotation therewith having first and second spaced ends and a plurality of axially extending splines complemental in shape to said shaft splines and positioned for engagement with said shaft splines, said cylinder block having a plurality of axial cylinder bores; a plurality of reciprocable pistons housed individually within said bores, said pistons each having a ball portion at one end thereof extending outwardly from said cylinder bores toward a plane perpendic
  • said pump housing and said cylinder block respectively having first and second annular valve plates positioned about said shaft between said housing and said first end of said cylinder block adjacent said first anti-friction bearings, said first and second valve plates each having complemental relatively rotating bearing surfaces, said valve plates each having a plurality of axially extending cooperating pump ports therein for fluid communication with complementary ports provided in said cylinder block bores, means providing said valve plates with a plurality of radially extending fluid passagewaysin communication with said first anti-friction bearings;
  • lubricating fluid under pressure is directed a rotatable drive shaft extending through said housing, a lubricant reservoir, first and second anti-friction bearings supporting said shaft at its first and second ends respectively for rotation within said housing,
  • said shaft having a splined outer area having a plurality of axially extending splines extending from an intermediate location on said shaft toward a point adajcent the second end of said shaft,
  • a cylinder block being positioned about said shaft, said blockhaving a plurality of axially extending splines
  • said piston pump including a swash complementally positioned to the splines on said shaft for rotation of said cylinder block with said shaft, plurality of reciprocable pistons positioned within said axial cylinder bores for reciprocation therein, said pistons each having a ball portion at one end, said pistons being positioned with said ball end extending outwardly from said cylinder bores toward the second end of said shaft,
  • swash plate pivotable about the right end of said shaft, a Y plurality of trunnion bearings mounted within said housing and supporting said swash plate for pivotal movement about said shaft, said swash plate having a generally cylindrical opening facing said pistons, thrust plate being generally annular in shape and being positioned within said cylindrical opening in said swash plate, said thrust plate having a generally flat, surface facing said pistons, Y slipper positioned arcuately about said shaftan having a first and second end, said first end having means providing socket openings therein, said second end comprising a generally flat surface being generally complemental to the flat surface of said thrust plate and being adapted for sliding movement on said thrust plate, said ball ends of said pistons being fitted within said sockets of said slipper,
  • slipper retainer guide positioned about a portion of the second end of said cylinder block, said slipper retainer guide being splined to said shaft for rotation therewith,
  • first and second valve plates being positioned at the first end of said cylinder block between said housing and said cylinder block, said first valve plate comprising a stationary housing plate, said second valve plate being a cylinder block plate for rotation therewith, said valve plates having intermediate abutting relatively rotating flat face portions, said valve plates being positioned adjacent said first anti-friction bear ings and being in fluid communication therewith, the improvement comprising:
  • each of said valve plates with a plurality of radially extending passageways adjacent said face portions communicatively connecting said first anti-friction bearings and said fluid reservoir,
  • said lubricant also flowing through said second radially extending shaft passageways to flow into said splined passageways, through said openings provided in said slipper retainer guide about said slipper and said thrust plate and radially outwardly to lubricate said trunnion bearings and returning to said reservoir.
  • a hydraulic transmission including an axial piston pump, an axial piston motor, conduit means communicatively connecting said pump and said motor, said pump and motor respectively having a rotating pump and motor shaft, said shafts each havingan outer area having a plurality of axially extending splines thereon, pump and motor cylinder block being splined respectively to said pump and motor shaft splines for rotation of said cylinder blocks with said respective rotating shafts, inner pump and motor anti-friction bearings supporting inner ends respectively of said pump shaft and said motor shaft adjacent said conduit means, a pump and a motor swash plate assembly axially spaced from said conduit means, outer pump and motor anti-friction bearings supporting outer ends respectively of said pump shaft and said motor shaft, the improvement comprising:
  • pump and motor means each providing first, second and third radial passageways connected communicatively to said pump and motor axially extending passageways, said pump and motor each having valve plates having radially extending passageways connected communicatively with said inner pump and motor anti-friction bearings, said first radially extending pump and motor passageways being in communication with said pump and motor inner anti-friction bearings;
  • said second radially extending pump and motor passageways being positioned respectively at intermediate portions of said pump and motor shafts and leading communicatively from said axial pump and motor passageways to said splined areas of said shaft at a position immediately adjacent the valve plate end of said splined area, means providing splined fluid passageways extending axially through said pump and motor splined areas and connected communicatively respectively to said pump and motor swash plate assemblies; said third pump and motor radially extending passageways leading respectively communicatively from said axially extending pump and motor passageways to said pump and motor outer antifriction bearings whereby lubricating fluid under pressure is directed in predetermined proportions to said pump and motor bearings, splined areas of said pump and motor shafts, pump and motor valve plates, and pump and motor swash plate assemblies.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Fluid Gearings (AREA)
US452090A 1965-04-30 1965-04-30 Piston pump lubrication structure Expired - Lifetime US3304885A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US452090A US3304885A (en) 1965-04-30 1965-04-30 Piston pump lubrication structure
GB6335/66A GB1141705A (en) 1965-04-30 1966-02-14 Hydraulic axial piston pump, motor or transmission lubrication structure
DE19661653477 DE1653477A1 (de) 1965-04-30 1966-04-29 Schmiersystem fuer als Pumpe oder Motor wirkende Axialkolbenmaschine

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US452090A US3304885A (en) 1965-04-30 1965-04-30 Piston pump lubrication structure

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GB (1) GB1141705A (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3382814A (en) * 1966-05-23 1968-05-14 Sundstrand Corp Piston holddown means
US3399628A (en) * 1966-05-17 1968-09-03 Sundstrand Corp Piston return mechanism
US3433173A (en) * 1967-02-08 1969-03-18 Bennes Marrel Hydraulic pumps and motors having axial pistons and inclined swashplates
US3687012A (en) * 1970-11-02 1972-08-29 Applied Power Ind Inc Hydraulic motor
DE2350038A1 (de) * 1972-11-02 1974-05-16 Deere & Co Hydrostatischer zusatzantrieb fuer kraftfahrzeuge, insbesondere ackerschlepper
US3893375A (en) * 1973-02-07 1975-07-08 Caterpillar Tractor Co Axial piston hydraulic device with forced lubrication means
US4090430A (en) * 1974-10-09 1978-05-23 The Japan Steel Works Swash plate type compressor
FR2470265A1 (fr) * 1979-11-21 1981-05-29 Ifield Eng Pty Perfectionnements aux faces a lumieres de distribution dans les pompes et moteurs hydrauliques
US4352637A (en) * 1980-06-04 1982-10-05 General Signal Corporation Jet cooling pump
US4505187A (en) * 1982-01-13 1985-03-19 Fiat Auto S.P.A. Reciprocating piston engine with swash plate mechanism
US4637293A (en) * 1984-11-14 1987-01-20 Honda Giken Kogyo Kabushiki Kaisha Slant plate type hydraulic device
WO1994005924A1 (en) * 1992-08-27 1994-03-17 Gleasman Vernon E Swash plate type hydraulic machine
WO1994016219A1 (en) * 1993-01-18 1994-07-21 Danfoss A/S Hydraulic axial piston machine
US20150068395A1 (en) * 2013-09-09 2015-03-12 Kanzaki Kokyukoki Mfg. Co., Ltd. Axial piston device
CN104806738A (zh) * 2014-01-28 2015-07-29 株式会社神崎高级工机制作所 润滑油供给构造
US20160348674A1 (en) * 2013-12-17 2016-12-01 Poclain Hydraulics Industrie Hydraulic system with a drain housing
CN109162916A (zh) * 2018-10-17 2019-01-08 江苏汇智高端工程机械创新中心有限公司 轴向柱塞泵/马达

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5547229B2 (de) * 1972-03-29 1980-11-28
JPS5840664B2 (ja) * 1980-04-28 1983-09-07 アイシン精機株式会社 アキシヤルピストン型流体ポンプ・モ−タ−

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Publication number Priority date Publication date Assignee Title
US1308844A (en) * 1919-07-08 And william e
US2858771A (en) * 1955-10-27 1958-11-04 Richard T Cornelius Cooling system for hydraulic pumps
US2972962A (en) * 1956-07-16 1961-02-28 Oilgear Co Hydraulic thrust bearing
US3120816A (en) * 1959-04-16 1964-02-11 Council Scient Ind Res Hydraulic pumps and motors
US3124079A (en) * 1964-03-10 Jxanjacquxs j joyer

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1308844A (en) * 1919-07-08 And william e
US3124079A (en) * 1964-03-10 Jxanjacquxs j joyer
US2858771A (en) * 1955-10-27 1958-11-04 Richard T Cornelius Cooling system for hydraulic pumps
US2972962A (en) * 1956-07-16 1961-02-28 Oilgear Co Hydraulic thrust bearing
US3120816A (en) * 1959-04-16 1964-02-11 Council Scient Ind Res Hydraulic pumps and motors

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3399628A (en) * 1966-05-17 1968-09-03 Sundstrand Corp Piston return mechanism
US3382814A (en) * 1966-05-23 1968-05-14 Sundstrand Corp Piston holddown means
US3433173A (en) * 1967-02-08 1969-03-18 Bennes Marrel Hydraulic pumps and motors having axial pistons and inclined swashplates
US3687012A (en) * 1970-11-02 1972-08-29 Applied Power Ind Inc Hydraulic motor
DE2350038A1 (de) * 1972-11-02 1974-05-16 Deere & Co Hydrostatischer zusatzantrieb fuer kraftfahrzeuge, insbesondere ackerschlepper
FR2205862A5 (de) * 1972-11-02 1974-05-31 Deere & Co
US3823650A (en) * 1972-11-02 1974-07-16 Deere & Co Destroking of hydrostatic drive motors
US3893375A (en) * 1973-02-07 1975-07-08 Caterpillar Tractor Co Axial piston hydraulic device with forced lubrication means
US4090430A (en) * 1974-10-09 1978-05-23 The Japan Steel Works Swash plate type compressor
FR2470265A1 (fr) * 1979-11-21 1981-05-29 Ifield Eng Pty Perfectionnements aux faces a lumieres de distribution dans les pompes et moteurs hydrauliques
US4352637A (en) * 1980-06-04 1982-10-05 General Signal Corporation Jet cooling pump
US4505187A (en) * 1982-01-13 1985-03-19 Fiat Auto S.P.A. Reciprocating piston engine with swash plate mechanism
US4637293A (en) * 1984-11-14 1987-01-20 Honda Giken Kogyo Kabushiki Kaisha Slant plate type hydraulic device
WO1994005924A1 (en) * 1992-08-27 1994-03-17 Gleasman Vernon E Swash plate type hydraulic machine
US5440878A (en) * 1992-08-27 1995-08-15 Vernon E. Gleasman Variable hydraulic machine
WO1994016219A1 (en) * 1993-01-18 1994-07-21 Danfoss A/S Hydraulic axial piston machine
US20150068395A1 (en) * 2013-09-09 2015-03-12 Kanzaki Kokyukoki Mfg. Co., Ltd. Axial piston device
CN104421414A (zh) * 2013-09-09 2015-03-18 株式会社神崎高级工机制作所 轴向活塞装置
US9822876B2 (en) * 2013-09-09 2017-11-21 Kanzaki Kokyukoki Mfg. Co., Ltd. Axial piston device
CN104421414B (zh) * 2013-09-09 2018-03-13 株式会社神崎高级工机制作所 轴向活塞装置
US20160348674A1 (en) * 2013-12-17 2016-12-01 Poclain Hydraulics Industrie Hydraulic system with a drain housing
CN104806738A (zh) * 2014-01-28 2015-07-29 株式会社神崎高级工机制作所 润滑油供给构造
US20150211396A1 (en) * 2014-01-28 2015-07-30 Kanzaki Kokyukoki Mfg. Co., Ltd. Lubricating oil supply structure
JP2015140694A (ja) * 2014-01-28 2015-08-03 株式会社 神崎高級工機製作所 潤滑油供給構造
CN109162916A (zh) * 2018-10-17 2019-01-08 江苏汇智高端工程机械创新中心有限公司 轴向柱塞泵/马达

Also Published As

Publication number Publication date
GB1141705A (en) 1969-01-29
DE1653477A1 (de) 1971-07-22

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