EP0266744A2 - Pumpe mit Ringventilelement - Google Patents

Pumpe mit Ringventilelement Download PDF

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Publication number
EP0266744A2
EP0266744A2 EP87116170A EP87116170A EP0266744A2 EP 0266744 A2 EP0266744 A2 EP 0266744A2 EP 87116170 A EP87116170 A EP 87116170A EP 87116170 A EP87116170 A EP 87116170A EP 0266744 A2 EP0266744 A2 EP 0266744A2
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European Patent Office
Prior art keywords
port
valve
cylinder
seat surface
ports
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EP87116170A
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English (en)
French (fr)
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EP0266744A3 (de
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Joseph S. Cardillo
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves

Definitions

  • the present invention is in the field of hydraulic pumps, and relates particularly to the type of hydraulic pump having a rotating cylinder block and wherein inlet and output porting is accomplished by cooperation between cylinder porting in the rotating cylinder block with fixed porting in the housing, this type of hydraulic pump finding particular utility for fuel injection systems.
  • most hydraulic pumps are of the rotating cylinder block type.
  • means in the body of the pump such as a swash plate is engageable with the pistons which orbit with the rotating cylinder block for moving the pistons in regular succession through positive pressure or compression strokes and negative pressure or suction strokes, with the pistons in one 180° sector of the body moving in positive pressure or compression strokes and the pistons in the other 180° sector of the body moving in negative pressure or suction strokes.
  • a swash plate is engageable with the pistons which orbit with the rotating cylinder block for moving the pistons in regular succession through positive pressure or compression strokes and negative pressure or suction strokes, with the pistons in one 180° sector of the body moving in positive pressure or compression strokes and the pistons in the other 180° sector of the body moving in negative pressure or suction strokes.
  • kidney port-type valve system two large arcuate, kidney-shaped ports are stationary in the pump body, carried in an end housing of the pump body.
  • One of the large kidney ports covers one 180° sector for intake, and the other covers the other 180° sector for discharge.
  • These large stationary kidney ports are separated by lands at their ends, so that they are actually each somewhat less than 180° in extent.
  • An annular array of small, regularly spaced cylinder kidney ports is located in a flat annular cylinder port face on the rotating cylinder block, each communicating with a respective pump cylinder.
  • the rotating cylinder port axis and the axis of the large stationary kidney ports are coaxial, and the small cylinder ports commutate abruptly from positive pressure to negative pressure at one land, and from negative pressure to positive pressure at the other land.
  • the state-of-the-art kidney port-type valve employed in rotating cylinder block hydraulic pumps has a number of serious problems which are inherent in the geometry, and particularly in the coaxial alignment of the rotating cylinder ports and the large stationary kidney ports.
  • One such inherent problem is that the large stationary kidney ports and rotating cylinder ports are required to have a relatively large radial spacing from the axis of rotation relative to the specified flow volume and pressure of the pump, which causes an undesirably high scrubbing velocity of the rotating cylinder block port face against the opposed stationary kidney port face, resulting in an undesirably large amount of wear.
  • kidney port-type valving Another inherent problem with the kidney port-type valving is that the long stationary kidney-shaped slots with their abrupt ends and the short intermediate lands make flat lapping of the opposed porting surfaces a problem in production, tending to result in an inaccurate face-to-face seal between the valving surfaces.
  • the relatively large porting radius contributes to this difficulty of flat lapping in production.
  • the positive and negative pumping functions of the rotating cylinder block pump, where the pistons are swash plate actuated, are essentially sine functions, with zero pumping at the lands, and with full positive or pressure pumping proximate the center of one of the large stationary kidney ports and full negative or suction pumping proximate the center of the other large stationary kidney port.
  • the abrupt exposure of essentially zero pressure cylinder ports to full high pressure output and full negative pressure input of the pump inherently introduces undesirable pressure irregularities or "hydraulic ripple" into both the output and the input, and input irregularities will be reflected as further irregularities in the output.
  • Another object of the invention is to provide a valve port system for a rotating cylinder block-type hydraulic pump which embodies a novel ring-shaped valve seat surface which is eccentrically located relative to the axis of rotation of the rotating cylinder block.
  • Another object of the invention is to provide a novel eccentric ring valve configuration for the rotary cylinder block-type hydraulic pump which has an uninterrupted symmetrical geometry which lends itself particularly well to flat lapping in production for provision of an efficient face-to-face seal of the valve port surfaces.
  • a further object of the invention is to provide a ring valve porting system of the character described for a rotating cylinder-type hydraulic pump wherein the rotating cylinder port surface and cylinder ports have narrow, acute angles of attack and departure relative to the novel eccentric ring valve element of the invention, minimizing wear during operation and avoiding any tendency for grooving and consequent leakage, and causing a continuous self-cleaning action and micro-surface lapping during operation.
  • a still further object of the invention is to provide a novel eccentric ring valve porting system for rotary cylinder block-type hydraulic pumps wherein the geometry of the arcuate ring seat output and inlet porting edges and rotating annular cluster of cylinder ports enables the ring seat and cylinder port valving surfaces to be much smaller in area than the valving surfaces of a conventional kidney port-type valve system for a comparable pumping flow volume and pressure, such smaller area not only minimizing leakage because of the much smaller valving surface perimeter, but also enabling more accurate mating flatness of the valving surfaces to be manufactured and maintained.
  • Yet a further object of the invention is to provide an eccentric ring valve porting system for rotary cylinder block-type hydraulic pumps wherein the valving surface accuracy and relatively small dimension for the hydraulic fluid flow volume and pressure enable hydraulic fluid leakage from between the mating valving surfaces to be so greatly minimized that pump output pressure builds up rapidly at very low pump speeds, which is a critical advantage where the valving system of the invention is employed in fuel injector pumps which are engine driven, and where engine starting is totally dependent upon pump pressure build-up at low engine speeds.
  • a still further object of the invention is to provide a novel eccentric ring valve porting system for rotary cylinder block hydraulic pumps in which the rotating cylinder port openings and closings at the arcuate ring valve seat output and inlet stationary port edges are gradual and not abrupt as in the kidney port-type valve conventionally employed in such hydraulic pumps, and wherein the valve porting characteristics generally follow the pumping characteristics, whereby output pressure irregularities or hydraulic ripple are minimized.
  • the pistons and cylinders orbit through a first 180° sector of the body of the pump in which the pistons move in compression or output strokes and a second 180° sector of the body in which the pistons move in suction or input strokes.
  • the cylinder block is provided with a cylinder port face which is generally radially orientated relative to the axis of rotation of the cylinder block, with a circular array of regularly spaced cylinder ports opening at the cylinder port face, each of which ports is in communication with a respective one of the cylinders.
  • a generally ring-shaped valve element has an annular ring seat surface which is in face-to-face engagement with the cylinder port face, with the axis of the ring seat surface eccentrically offset relative to the axis of the ring seat surface eccentrically offset relative to the axis of rotation of the cylinder block and cylinder ports.
  • This eccentric offset of the ring seat axis is preferably toward the compression or output 180° sector of the body or the pump, causing the compression or output cylinders to be exposed inside the inner edge of the ring seat surface for positive pressure output porting of the pumped hydraulic fluid, and the suction or input cylinders to be exposed outside the outer edge of the ring seat surface for negative pressure or suction input porting of the fluid from a hydraulic fluid source.
  • Output fluid pressure is applied to the ring valve element to hold the ring valve seat surface down against the cylinder port face so as to more than counterbalance the lift-off force of hydraulic fluid which works into the interface between the cylinder port face and the valve seat surface, and start-up spring biasing is also applied to the ring valve element for biasing the porting surfaces together until the output fluid pressure builds up accomplish this function.
  • the ring valve pump of the present invention is generally designated 10 and is encased in a generally cylindrical body 12 having ends 14 and 16.
  • the body 12 consists of a cylindrical case 18, a valve end housing 20 secured to one end of case 18, and a shaft end housing 22 secured to the other end of case 18.
  • Valve end housing 20 contains the ring valve element of the invention which cooperates eccentrically with annularly arrayed cylinder porting of the pump to define the inlet and output flow paths of the invention.
  • Shaft end housing 22 on the other hand, has the pump shaft coaxially supported therein with the driven end of the pump shaft projecting outwardly therethrough.
  • Valve end housing 20 is attached to one end of cylindrical case 18 by means of an annular series of regularly spaced bolts 24, being positively located relative to case 18 by an annular series of regularly spaced locating pins 26.
  • An annular gasket 28 seals the interface between valve end housing 20 and cylindrical case 18.
  • fluid inlet passage 30 extends through valve end housing 20 parallel to but considerably radially offset from the center axis 32 of pump 10, opening out at the valve end 14 of body 12 for connection to and communication with a fluid source of supply.
  • Output passage 34 also extends partly through valve end housing 20, opening out at the valve end 14 of body 12 for connection to and communication with apparatus receiving the pressurized liquid from ring valve pump 10, such as diesel or gasoline fuel injector apparatus.
  • output passage 34 is aligned with the eccentric axis 36 of the ring valve element of the invention.
  • the eccentric axis 36 is parallel to the center axis 32 of pump 10, but is radially offset from center axis 32 an eccentric amount designated "e" in Figures 2, 4 and 6 which enables the novel inlet and output porting of the invention to be accomplished between the stationary ring valve element and the rotating cylinder block porting as described in detail hereinafter.
  • Shaft end housing 22 has an axial passage 37 through which the outer, driven end portion of pump shaft 38 extends.
  • Shaft end housing 22 is connected to cylindrical case 18 by means of a series of regularly spaced bolts 40, being positively located relative to case 18 by a series of regularly spaced locating pins 42.
  • the interface between case 18 and shaft end housing 22 is sealed by a gasket 44.
  • a generally annular cylinder block 46 is mounted on the inner end portion of pump shaft 38, being provided with a central bore 48 which receives the inner end portion of shaft 38.
  • Cylinder block 46 is secured to shaft 38 by means of a coaxial screw 50 which has its head recessed relative to a flat annular port face 52 on cylinder block 46.
  • An O-ring seal 54 between the inner end of shaft 38 and cylinder block 48 provides a fluid-­tight seal therebetween.
  • Shaft 38 is a drive shaft for rotating the cylinder block 46, and is accordingly keyed to cylinder block 46 by means of elongated key 56 which is engaged in registering slots in shaft 38 and cylinder block 46.
  • the port end portion of cylinder block 46 is journalled in a needle bearing assembly 58 located partly within case 18 and partly within the periphery of valve end housing 20.
  • Needle bearing assembly 58 has an inner bearing race 60 secured to cylinder block 46.
  • Rotational support for shaft 38 and cylinder block 46 is completed by means of a ball bearing assembly 62 mounted within shaft end housing 22.
  • a pair of shaft seals 64 of the lip seal type is mounted in shaft end housing passage 37, and the space between seals 64 is vented to the outside of pump body 12 by a passage 65 to prevent pressure buildup between the seals.
  • Cylinder bores 66 and sleeves 68 are parallel to and equally radially spaced from the center axis 32 of pump 10. In the embodiment of the invention illustrated in the drawings, there are seven of the cylinder bores 66 and sleeves 68. Cylinder sleeves 68 have reduced outer portions which extend out of cylinder bores 66 toward the shaft end 16 of body 12, these reduced outer portions 70 extending through complementary passages in a retainer plate 72 which is secured to the shaft end surface of cylinder block 46 by means of a series of regularly spaced screws 74, so as to retain cylinder sleeves 68 in cylinder block 46.
  • Cylinder head flow passages 78 incline axially and radially inwardly from head ends 76 of the cylinders to cylinder head ports 80 to achieve the very small radial distance of cylinder head ports 80 from the center axis 32 which is an important aspect of the invention, while nevertheless enabling the cylinders to be relatively widely radially spaced outwardly from the center axis 32 to provide the required amount of space for the cylinders, pistons, and piston actuating mechanism to be described in detail below.
  • Cylinder head ports 80 are round counterbores at the port ends of inclined flow passages 78.
  • a piston 82 is slideably mounted in each of the cylinder sleeves 68, pistons 82 being reciprocally driven as cam followers as they orbit about the center axis 32 during rotation of cylinder block 46.
  • Pistons 82 have inner fluid actuating ends 83 and outer cam follower ends 84.
  • Outer cam follower piston ends 84 may be of generally spherical configuration as shown, or alternatively, may be of a modified cone configuration with the general cone angle approximating the cam angle of inclination relative to axis 32 of pump 10.
  • Each of the pistons 82 is biased outwardly relative to its cylinder sleeve 68 by a helical piston spring 86 engaged over the reduced outer portion 70 of the respective cylinder sleeve 68.
  • each spring 86 is applied by each spring 86 to a respective spring guide 88 and thence through a respective guide retaining ring 90 to the respective piston 82 near its outer end 84.
  • the inner end of each piston spring 86 bears against a respective spacer washer 92 which in turn bears against the retainer plate 72.
  • Cam swash plate 94 is in the form of a ring which is freely rotatably backed against a ring-shaped roller bearing assembly 98 which in turn bears against a thrust washer 100, both bearing assembly 98 and thrust washer 100 being located on cam plate structure 96.
  • An annular bushing 102 concentrically locates swash plate 94 around its axis of rotation, which is designated 103 in Figure 3.
  • cam plate structure 96 is held in its geometrically fixed location within pump body 12 by the annular end portion 104 of cam plate structure 96 bearing against and overlapping the outer race of ball bearing assembly 62 and by being pinned against rotational movement by pins 105 in shaft end housing 22.
  • the axis 103 of cam swash plate 94 has a fixed angle of inclination 106 relative to center axis 32 of pump 10 in the plane of the Figure 3 section, and this is 90° from the plane of the Figure 4 section or from the direction of the ring valve element eccentricity "e” illustrated in Figures 2, 4 and 6.
  • the angle of inclination 106 of swash plate axis 103 provides a second eccentricity in the ring valve pump 10 of the invention, which cooperates with the porting eccentricity "e” in a new way described in detail below.
  • a fluid access port 107 is provided through the wall of case 18 enabling the interior of pump body 12 to be filled with the liquid being pumped, or emptied if desired, and access port 107 will be plugged during operation of ring valve pump 10.
  • the end portion of shaft 38 which projects outwardly from end housing 22 is provided with a drive key slot 108.
  • the ring valve element of the invention is generally designated 110, and it is mounted within valve end housing 20 so as to butt face-to-face against the flat annular port face 52 of cylinder block 46.
  • Ring valve element 110 has a cylindrical body 112 which fits within a generally complementary but somewhat longer cylindrical recess 114 in valve end housing 20.
  • An O-ring seal 116 and slipper ring 118 are seated within an annular groove in cylindrical body 112 to provide a generally fluid-tight seal between body 112 of valve element 110 and the cylindrical surface of recess 14 in end housing 20.
  • the valving surface of ring valve element 110 is flat annular ring seat surface 120 which bears flush against cylinder block port face 52 and is defined between inner and outer cylindrical surfaces of valve element body 112.
  • the inner edge 122 of ring seat surface 120 defines the fixed or nonrotating output port of the valve, and this in turn communicates through an output conduit 124 extending axially through valve element 110 to the cylindrical recess 114 and thence to output passage 34 of the ring valve pump 10.
  • Annular outer periphery 126 of ring seat surface 120 defines the fixed or nonrotating inlet port of the valve.
  • the inner end of valve end housing 20 is annularly recessed to provide valve inlet chamber 128 which surrounds the inner, porting end of ring valve element 110.
  • An annular locating flange 130 projects peripherally from ring valve element 110 within inlet chamber 128, and an annular series of regularly spaced locating pins 132 keys locating flange 130, and hence valve element 110, against rotation relative to valve end housing 20.
  • Pins 132 are fixed to valve end housing 20, but have an axially sliding fit in complimentary holes in valve element locating flange 130 to permit axial adjustment of valve element 110 to an optimal seated position against cylinder block port face 52.
  • An annular series of helical springs 134 is mounted in respective regularly spaced recesses 136 in valve end housing 20, springs 134 bearing against flange 130 on valve element 110 so as to bias the valve element ring seat surface 120 generally flush against cylinder block port face 52.
  • Springs 134 are only required for start-up biasing to hold the porting surfaces 120 and 52 together until substantial fluid output pressures has been developed by the pump, after which fluid output pressure itself provides the desired biasing force as described in detail below.
  • Inlet chamber 128 is isolated from cylinder block needle bearing assembly 58 by means of an O-ring seal 138 mounted in an annular retainer 140 which is biased against needle bearing race 60 by means of a wave or marcel spring 142.
  • eccentricities there are two separate eccentricities embodied in the present invention which are cooperatively arranged so as to substantially completely avoid irregularity or "ripple" in the pressurized output flow from the ring valve and rotary cylinder block combination of the present invention.
  • One of these eccentricities is the angular axial offset 106 of the swash plate axis 103 relative to the center axis 32 of pump 10.
  • the other eccentricity is the eccentricity "e” of the ring valve element axis 36 relative to the center or primary axis 32 of the pump, which is the axis about which pump cylinder block 46 and cylinder valve ports 80 rotate.
  • These two axes of eccentricity are cooperatively related in a wholely new way in the present invention to substantially completely avoid flow irregularities or hydraulic ripple in the output of ring valve pump 10.
  • the eccentric angle of inclination 106 of axis 103 of swash plate 94 produces the pumping action of pistons 82 in response to rotation of cylinder block 46 and consequent orbiting of the cylinders 66 and piston 82.
  • cylinder block 46 With the direction of offset of eccentricity "e" of ring valve element eccentric axis 36 relative to center axis 32, and the direction of inclination 106 of cam swash plate axis 103 relative to center axis 32, cylinder block 46 will rotate clockwise as illustrated in Figures 5 and 6, and the upper cylinder as viewed in each of Figures 3 and 4 will be moving upwardly out of the sheet, while the lower cylinder in each of Figures 3 4 and will be moving downwardly into the sheet. This direction of rotation is illustrated by phantom arrows in Figure 6.
  • piston 82b Conversely, during this first 180° of rotation from the position illustrated in Figure 3, piston 82b will be shifted in a compression stroke from approximately its fully extended position as illustrated in Figure 3 to a fully recessed position corresponding approximately to the position of piston 82a in Figure 3. Then, during the next 180° of rotation of cylinder block 46, piston 82a will move back forwardly in a compression stroke to its fully recessed position as shown in Figure 3, while piston 82b will move back rearwardly in a suction stroke to its fully extended position as illustrated in Figure 3.
  • cylinder block 46 has a 90° rotational lead relative to where it is in Figure 3, so the pistons 82c and 82d seen in Figure 4 are close to the middle of their axial travels, and hence close to having their highest movement speeds.
  • the upper piston 82c in Figure 4 is close to the middle of its suction stroke, while the lower piston 82d in Figure 4 is close to the middle of its compression stroke.
  • the body 12 of pump 10 may be considered as having two 180° sectors through which the cylinders 66, pistons 82, and cylinder ports 80 orbit, a 180° compression sector which is the sector of body 12 shown in Figure 3 and the lower half of body 12 as viewed in Figure 4, and a 180° suction sector which is the sector body 12 out of the page in Figure 3 and the upper half of body 12 as viewed in Figure 4.
  • the axially oriented compression and suction strokes of pistons 82 follow a sinusoidal path around the general cylinder of orbiting of the pistons around axis 32, piston movement slowing down to essentially zero proximate the fully recessed and fully extended positions of the pistons where the apices of the sine curve are traced; and having their most rapid axial movement proximate the midpoints of their strokes corresponding to the steepest slope of the sine curve representing their movements.
  • the novel eccentric ring valve porting of the invention produces valve port inlet and output apertures which vary in cross-­sectional dimension surprisingly closely with the sine curve movement pattern of the pistons 82 in synchronism with the piston movements to substantially completely eliminate flow irregularities or hydraulic ripple, as described in detail below.
  • swash plate bearing assembly 98 results in a minimal amount of friction between the freely rotating swash plate and the piston cam follower ends 84, with the spherical or modified conical configuration of the ends 84.
  • the swash plate surface engages piston heads 84 in an orbiting engagement path, called a smear path, on the swash plate surface, and although pistons 82 are free to rotate in their respective cylinders, they only slightly oscillate or nutate in the cylinder bores.
  • Figure 6 illustrates how cylinder ports 80, which communicate with respective cylinders 66 through respective cylinder headflow passages 78, are commutated relative to the eccentric ring seat surface 120, and hence relative to inner output port periphery 122 and outer inlet port periphery 126 of ring seat surface 120.
  • cylinder port 80a which communicates through flow passage 78a to the cylinder containing piston 82a, is at its location of greatest closure and is about to become uncovered at its outer edge radially outwardly of the outer periphery or inlet port 126 of ring seat surface 120 so as to be exposed to inlet chamber 128.
  • cylinder port 80b which communicates through passage 78b to the cylinder containing piston 82b, has already become partly uncovered inwardly of the inner periphery or output port 122 of ring seat surface 120 so as to communicate without conduit 124.
  • Cylinder port 80c which is the next port ahead of 80b, and communicates with the respective cylinder through flow passage 78c, is exposed almost to its fullest extent inwardly of ring output portion 122.
  • the next cylinder port 80e which is ahead of port 80c but behind port 80a, has moved well past its location of greatest opening inside ring output port 122, and is now moving toward its closed position.
  • port 80f is approximately one-half opened outwardly of outer periphery 126 of seat 120 for communication with inlet chamber 128, and is moving toward its fully opened position.
  • Cylinder port 80d has moved slightly past its most fully opened position outside of outer periphery 126 of ring seat 120, and is still close to its fully opened position for communication with inlet chamber 128.
  • Cylinder port 80g has moved well past its fully opened position and is now moving toward its closed position inside of outer periphery 126 of ring seat 120.
  • ring seat surface 120 of ring valve element 110 performs the identification of cylinder ports 80 during commutation of cylinder ports 80 caused by rotation of cylinder block 46, the inner periphery 122 of ring seat 120 identifying the cylinder ports 80 for communication to output conduit 124 when their respective pistons are in compression mode, and the outer periphery 126 of ring seat surface 120 identifying the cylinder ports 80 whose pistons are in suction mode for communication with inlet chamber 128.
  • Inner and outer phantom circles 144 and 146 have been drawn about center axis 32 in Figure 6 to indicate the respective inner and outer edges of cylinder ports 80.
  • Inner circle 144 indicates the directions of movement of the inner edges and inner portions of ports 80 as they approach the inner edge 122 of ring seat 120 during opening and closing of their output phase of movement, and also during the main portion of the output phase.
  • the upper edges of ports 80 move into their open positions at an acute angle relative to inner seat edge 122, and then only the upper peripheral edge portions of ports 80 are first opened at such acute angle.
  • ports 80 close against the upper part of inner seat edge 122, they also move at an acute angle relative to edge 122, and only small lower peripheral edge portions of ports 80 are being closed off.
  • most of the lengths of the left-­hand sides of inner circle 144 and inner seat edge 122 are generally parallel to each other in an offset tangential relationship, so that during that portion of the output phase of the valve porting in which large areas of cylinder ports 80 are exposed inside of ring seat edge 122, the opening and closing changes in the exposure of ports 180 within inner seat edge 122 are relatively slowly accomplished.
  • the cylinder ports are uncovered and covered rapidly at full circumferential speed of the cylinder block, rapidly fully opening into the large stationary kidney ports, remaining fully opened through the entire extent of the sweep in communication with the large kidney ports, and then rapidly closing when reaching the ends of the large kidney ports.
  • Such sudden porting and consequent sudden exposure of the high pressure, high volume output to low pressure, low volume pump port flow leads to substantial irregularity or hydraulic ripple in the output.
  • the ring valve of the present invention has several characteristics which cooperate in a synergistic way to provide a much tighter porting surface seal both initially in the manufactured product and over a long working life of the valve, as compared to the conventional kidney valve.
  • annular ring seat surface 120 and annular cluster of cylinder port holes 80 lends itself particularly well to flat lapping in production, for provision of an optimum face-to-face seal.
  • Another such characteristic is that the symmetrical geometry and narrow angles of attack and departure of cylinder port face 52 and cylinder ports 80 relative to the inner and outer edges 122 and 126, respectively, of ring seat surface 120 cause a self-cleaning action and a continuous micro-­surface lapping which maintains an accurate flatness of the mating surfaces as the valve wears over a long operational life. With this action, there is no tendency whatsoever for grooving to occur, and the original tight, generally leak-proof seal is maintained over the long operational life.
  • the geometry of the eccentric ring seat surface 120 and annular cluster of cylinder ports 80 enables the valving surfaces to be much smaller in area, with a consequently much smaller periphery, than the conventional kidney valve.
  • This smaller size enables more accurate flatness to be manufactured and maintained in the mating porting surfaces.
  • the more accurate flatness enables the mating valve surfaces to be closer together in their surface-to-surface direction, or in the direction normal to the surfaces, minimizing the escape path in this normal or axial direction of the valve, while the reduced perimeter enabled by the smaller valving surfaces reduces the fluid escape path in the direction parallel to the flat surfaces, or in the general radial direction of the valve.
  • the smaller radius of the portion of the rotating cylinder port face 52 which engages ring seat surface 120 results in reduced scrubbing velocity, which is proportional to radius, and therefore reduced wear.
  • the velocity of the portion of cylinder block port face 52 which faces against ring seat surface 120 is actually very low in absolute terms.
  • the seal ring seat surface outer diameter was approximately one inch, with an eccentricity of approximately 3/16 inch. This results in the diameter of cylinder block port face 52 which sweeps against ring seat surface 120 being approximately 11/8 inch which, multiplied by pi (3.14) gives an outer periphery of the sweeping surface of approximately 4.32 inch.
  • the outer peripheral speed of the sweeping surface is approximately 14.4 feet per second, with an average speed of port face surface 52 which sweeps ring seat surface 120 that is considerably less than 14.4 feet per second.
  • ring valve pump 10 of the invention results from the very low leakage achieved with the ring valve porting of the present invention. This is the ability of ring valve pump 10 of the invention to build up to full operating output pressure at very low rpm. This is very important where the pump is engine-driven, which is preferably at crankshaft speed, but may be at camshaft speed, or may be at any other desired speed through a belt, gear or shaft drive. Where ring valve pump 10 is employed to pump pressurized fuel to fuel injectors, it is absolutely essential that the pump 10 be capable of providing substantially full pressure at engine starting speeds, which are very low.
  • Sealing of the present ring valve porting is so volumetrically very tight that full pressure has been achieved with prototypes of the present ring valve pump at engine speeds under 70 rpm, as compared to in excess of 300 rpm normally required with conventional rotating cylinder block fuel injector pumps which have kidney valve porting. This is a better than four-to-one start-up advantage for the present invention, which indicates a new order of magnitude of port sealing advantage for the present invention.
  • Ring valve element 10 and the portion of cylinder block port face 52 exposed to inlet chamber 128 are immersed in the fluid being pumped. Additionally, a thin film of the fluid, only a few molecules in thickness, continuously works its way in between the opposed porting faces, ring seat surface 120 and that portion of cylinder port face 52 which registers with ring seat surface 120 during rotation of the cylinder block. This thin film of fluid between the porting faces serves to lubricate the faces against wear. This thin film is actually pumped into the interface between the porting surfaces by the high fluid pressure within output port 122 of ring valve element 110 and in those cylinder ports 80 receiving pressurized fluid from their respective cylinders, these being cylinder ports 80b, 80c and 80e in Figure 6.
  • This pressurized fluid in the interface gradually works its way out from between the porting surfaces, but at such a slow rate as to not represent any material amount of fluid leakage.
  • This pressurized fluid in the porting surface interface produces a lift-off force which tends to lift ring seat surface 120 axially off of cylinder port face 52.
  • the lift-off pressure pattern is approximately shown by phantom line 148 in Figure 6A, extending radially outwardly from ring valve output port 122, and curving even further radially outwardly about the pressurized cylinder ports 80.
  • the total lift-off force on ring valve element 110 is determined by area increments times the pressure at the increments integrated over the entire area defined within the lift-off pressure pattern 148.
  • the lift-off pressure pattern 148 will continuously vary as the pressurized cylinder ports 80 rotate, and the extent of the lift-off force will slightly vary with such variations in the lift-off pattern 148.
  • This lift-off force at its worst condition is more than counterbalanced by a hold-down force of output fluid pressure in cylindrical recess 114 of end housing 120 against ring valve element 110.
  • This hold-down force is determined by the output fluid pressure times the cross-sectional area of valve element cylindrical body 112 from an inner radius defined by output port 122 and an outer radius defined by the outer periphery of O-ring seal 116.
  • phantom line 148 in Figure 6A generally defines the lift-off pressure and force pattern, it is to be understood that the pressure and force per incremental area are at a maximum proximate output port 122 and the pressurized cylinder ports 80, and diminish radially outwardly therefrom generally to the pattern line 148. Nevertheless, it is to be understood that the entire interface between ring seat surface 120 and the registering portion of cylinder port face 52 is lubricated by a thin film of the fluid being pumped.
  • valve element 110 The fluid pressure hold-down force on valve element 110 is made sufficient around the entire annular extent of ring valve element 110 to provide firm seating of ring seat surface 120 against cylinder port face 52, despite the irregularities of the lift-off pressure pattern 148 about the ring seat center which is the eccentric center 36. Although this may cause somewhat more force to be applied between the valving surfaces on one side of ring seat 120 than the other, this has not been found to provide any appreciably greater wear on the side having the greater force application, particularly in view of the lubricating film between the valving surfaces, and with the very low wiping speed of one surface against the other.
  • the pressure of slipper ring 118 around O-ring seal 116 provides ring valve element 110 with full freedom of axial movement for microadjustment of ring seat surface 120 against cylinder block port face 52 for assurance of an optimum seal between these porting faces.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP87116170A 1986-11-04 1987-11-03 Pumpe mit Ringventilelement Withdrawn EP0266744A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US92666486A 1986-11-04 1986-11-04
US926664 1986-11-04

Publications (2)

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EP0266744A2 true EP0266744A2 (de) 1988-05-11
EP0266744A3 EP0266744A3 (de) 1990-01-17

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EP87116170A Withdrawn EP0266744A3 (de) 1986-11-04 1987-11-03 Pumpe mit Ringventilelement

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EP (1) EP0266744A3 (de)
JP (1) JPS63219883A (de)
CN (1) CN1012273B (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4536356B2 (ja) * 2003-11-05 2010-09-01 マロール株式会社 手動油圧ポンプ装置
JP4335938B2 (ja) * 2007-10-26 2009-09-30 三菱電機株式会社 燃料供給装置
JP4692560B2 (ja) * 2008-03-07 2011-06-01 株式会社デンソー 圧縮機
US9140244B2 (en) * 2011-08-31 2015-09-22 Caterpillar Inc. Piston pump with cam actuated valves
CN103922707B (zh) * 2014-03-17 2015-07-01 淄博畅安陶瓷科技有限公司 偏心陶瓷环及其制备方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE968539C (de) * 1955-09-04 1958-02-27 Gusswerk Paul Saalmann & Sohn Axialkolbenpumpe oder -motor
AT242517B (de) * 1962-09-19 1965-09-27 Mannesmann Meer Ag Flüssigkeitspumpe oder -motor
AT312424B (de) * 1970-10-22 1973-12-27 Eickmann Karl Axialkolbenmaschine
DE3025593A1 (de) * 1980-07-05 1982-02-11 Breinlich, Richard, Dr., 7120 Bietigheim-Bissingen Axialkolbenaggregat
DE3112930A1 (de) * 1981-03-31 1982-10-07 Joseph Vögele AG, 6800 Mannheim Axialkolbenpumpe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE968539C (de) * 1955-09-04 1958-02-27 Gusswerk Paul Saalmann & Sohn Axialkolbenpumpe oder -motor
AT242517B (de) * 1962-09-19 1965-09-27 Mannesmann Meer Ag Flüssigkeitspumpe oder -motor
AT312424B (de) * 1970-10-22 1973-12-27 Eickmann Karl Axialkolbenmaschine
DE3025593A1 (de) * 1980-07-05 1982-02-11 Breinlich, Richard, Dr., 7120 Bietigheim-Bissingen Axialkolbenaggregat
DE3112930A1 (de) * 1981-03-31 1982-10-07 Joseph Vögele AG, 6800 Mannheim Axialkolbenpumpe

Also Published As

Publication number Publication date
EP0266744A3 (de) 1990-01-17
CN1012273B (zh) 1991-04-03
CN87101496A (zh) 1988-05-18
JPS63219883A (ja) 1988-09-13

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