US3785758A - Vane pump with ramp on minor diameter - Google Patents

Vane pump with ramp on minor diameter Download PDF

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Publication number
US3785758A
US3785758A US00246774A US3785758DA US3785758A US 3785758 A US3785758 A US 3785758A US 00246774 A US00246774 A US 00246774A US 3785758D A US3785758D A US 3785758DA US 3785758 A US3785758 A US 3785758A
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United States
Prior art keywords
vane
ramp
cam surface
vanes
lip
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Expired - Lifetime
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US00246774A
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English (en)
Inventor
J Wilcox
C Adams
J Swain
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Hagglunds Denison Corp
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Abex Corp
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Assigned to HAGGLUNDS DENISON CORPORATION reassignment HAGGLUNDS DENISON CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: ABEX CORPORATION
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid

Definitions

  • ABSTRACT A hydraulic pump of the vane type wherein the cam surface of the stator is formed with a ramp on the minor diameter portion traversed by the vanes as they move from the pressure zone to the suction zone.
  • vanes of the two lip type When vanes of the two lip type are used, an in-ramp is especially desirable for pumps wherein the vane are spring operated, while an out-ramp is especially desirable for pumps wherein the vanes are operated by hydraulic actuators.
  • the provision of such ramps has been found to improve radial balance of the rotor, vane tip sealing, and to reduce pressure ripple, as well as wear.
  • This invention relates to improvements in hydraulic pumps of the type having rotor and stator members, one of which mounts vanes that engage a cam surface carried by the other member. More particularly, the invention is directed to improvements in the shape or contour of the cam surface in a pump having vanes of either the single or twolip type.
  • the vanes are mounted by the rotor for inward and outward movement in vane slots relative to the axis of rotor rotation.
  • the tips of the vanes slide over or .track on the cam surface of the stator that encircles the rotor.
  • the cam surface is contoured so that the spacing between it and the rotor periphery. varies around the rotor.
  • This so-called pumping space bounded by the rotor surface and the cam surface, is generally regarded as comprising four zones: the pressure zone, the suction zone, a transfer zone (which lies between the suction zone and the pressure zone in the direction of rotation), and a sealing zone (which lies between the pressure zone and the suction zone in the direction of rotation).
  • the variations in cam surfacerotor spacing in these zones causes vane movement and consequent changes in the volume of the intervane spaces or transfer pockets between each pair of vanes.
  • the pump operates by receiving fluid through the suction port into each pocket as it traverses the suction zone, transferring the fluid in the pocket by moving it from the suction zone across a transfer zone to the pressure zone,-and expelling the fluid from the pocket to a pressure port opening tothe pressure zone by reducing the pockets volume.
  • the pocket increases in volume as it traverses the suction zone, and decreases in volume in the pressure zone.
  • the volume decrease at the pressure zone occurs because the cam surface approaches the rotor surface more closely there. The cam surface pushes the vanes back into their rotor slots, and the projection of the vanes from the rotor is thereby diminished.
  • the corresponding reduction of pocket volume results in the positive displacement of the fluid therein to the outlet port.
  • the approach of the cam surface toward the rotor surface across the pressure zone is'called the pressure ramp, the term ramp being used to designate an inclined surface or approach, as opposed to an arc of fixed or constant diameter about the rotor axis.
  • suction ramp This outward cam surface inclination across the suction zone is referred to as the suction ramp; it is an outward ramp, as opposed to the pressure ramp which is an inward ramp-
  • suction and pressure ramps are present in virtually all vane pumps and they are essential to establish the pumping action.
  • This invention is predicated on the discovery that it is advantageous to provide a ramp, of certain small angulation, on the minor diameter of the cam surface.
  • a ramp provides the grestest advantages in a certain sub-class of vane pumps, viz., those which have vanesof the two-lip type, but it is also useful with vanes of the single lip type.
  • Vanes of the two-lip type are known per se, and are shown for example in the above mentioned Adams et al patent. Such vanes are characterized by two circumferentially spaced cam surface engaging edges or lips, between their front and back faces. These lips comprise a leading lip and a trailing lip, and they are separated by a groove between them. The groove providesfluid communication and pressure balance between the top and bottom of the vane. Both lips of the vane are intended to engage the cam surface where the surface is We have found, however, that that is not the most dc sirable configuration. It is probably impossible, or at least very impractical in the commercial production of pumps, to produce a cam ring having a sealing zone surface that is truly concentric with the center of rotor rotation. ln fact, if viewed under great enlargement, a
  • cam surface can be considered as comprising a wavy line, or as having tiny deviations from the theoretical true radius shape. Even a surface that approximates a precision constant diameter will seldom, if ever, by perfectly concentric with the shaft centerline in the final pump assembly. This is because all individual parts require dimensional tolerance for manufacturing, as well as tolerances for concentricity of various diameters on circular components. This can allow looseness or shifting of the cam relative to the housing and shaft. Even though the unassembled cam ring may have a minor cam surface closely concentric with the outside diameter, after it has been assembled into the pump the outside diameter is unlikely to be perfectly concentric with the center of rotation of the shaft and rotor, due to the manufacturing tolerances described.
  • the minor cam surfaces may be eccentric with the center of rotation in a somewhat random mount and direction from pump to pump.
  • This eccentricity may introduce the need for a vane, if it is to track the cam, to move into or out of a vane slot as the vane traverses a minor sea] surface, or even require the vane to undergo both directions of movement in sequence on the same sweep across this seal surface.
  • This same eccentricity in the installed'cam may require that a vane directly opposite the first vane move out as the first vane moves into the slot, or in, as the first vane moves out. This produces a somewhat random and unpredictable need for slight vane stroking or radial movement during the vane sweep across the minor seal, with no assurance that vanes 180 apart are undergoing the same direction or magnitude of stroking.
  • the cam will have one shape or contour as manufactured, but will distort slightly into a different shape when in a pump that is running under pressure.
  • the magnitude of the distortion increases with higher pressure.
  • This distortion is made worse by the fact that some of the inter nal cam surfaces are under the influence of outlet pressure, with other surfaces exposed to the lower inlet pressure, with some surface areas cycling between inlet and outlet pressures as vanes reach and leave the ports. This results in a cyclic distortion of the cam relative to the manufactured shape.
  • the side load will reverse directions. This will establish a substantial but fluctuating radial load on the rotor shaft.
  • the load in this case, will be the product of the pressure difference in the two slots times the cross-sectional area of a vane.
  • the radial force on the rotor can be as much as three-fourths of a ton, and may be applied and released many times a second. The sudden application and release of a force of this magnitude is believed to set up pump vibration, noise, shaft deflection, and to increase wear, and may break the seal between the vane and cam, producing erratic cross-port leakage with associated problems.
  • vane actuating means Two general types of vane actuating means are well known in the art: springs and hydraulic actuators (for example, pistons).
  • springs and hydraulic actuators for example, pistons
  • One or more springs can be mounted in the rotor beneath each vane to bias it toward the cam surface.
  • a piston can be mounted in the rotor beneath the vane and operated by pressure fluid from the pressure zone to apply a pressure dependant force to hold the vane against the 5 cam surface.
  • each piston-type hydraulic actuator urges the respective vane outwardly.
  • the top and bottom of the vane are connected by the vane groove described above, and when the leading lip of the vane is contacting the cam surface across the sealing zone, most of the cop of the vane is exposed to pressure. This pressure is applied to,
  • the amount of the ramp should not be substantially more than that angulation which is needed just to insure that the same lip of the vane will remain in contact with the cam surface across the sealing zone, considering the unavoidable irregularities in the inclination of the ramp.
  • This angulation may be essentially constant along the length of the sealing zone, and generally will be in the range of about W to 1% or 2, for either an in-ramp or an out-ramp. Ramps less than would not be sufficient'to overcome the problems of eccentric assemblies and distortion of the cam from pressure that could cause lip switch; on the other. hand, ramp angulations greater than about 2 tend to cause trapped volume changes which are relatively so great as to result in excessive pressure increase in the sealing zone from fluid compression, or in cavitation, during the moment when two vanes are sealing on the minor diameter, between ports.
  • FIG. 1 is an end plan view of the rotor and stator assembly of a balanced reversible pump with piston operated twolip vanes, in accordance with a preferred embodiment of the invention
  • FIG. 2 is an end plan view of the stator of FIG. I, superimposed on a polar graph, and shows in exaggerated form the several operating segments of the cam surface which constitute the minor and major diameters and the pressure and suction ramps;
  • FIG. 3 is an enlarged fragmentary view of a piston opeated vane in contact with an out-ramp on the cam surface in the sealing section of the pump, the ramp inclination being greatly exaggerated;
  • FIG. 4 is a view similar to FIG. 3, but shows the altered pressure relationsthat would exist if the vane rode on an in-ramp instead of an out-ramp in the sealing section;
  • Hg. 5 is a view similar to FIG. 4 but shows a spring operated vane in contact with an in-ramp on the cam surface in the sealing zone, the ramp inclination again being greatly exaggerated;
  • FIG. 6 is a graph which shows the radial width of the pumping zone, i.e., the vane displacement, as a function of angular position on a cam surface with an outramp on the minor diameter;
  • FIG. 7 is a graph similar to FIG. 6, but shows the radial displacement of the vane as a function of position along the cam surface for a pump having an inward ramp on the minor diameter, also in accordance with the invention. 7
  • a pump rotor is designated at l in the drawings.
  • the rotor is driven by a shaft 2, and mounts a plurality of vanes, each designated at 3, that reside in individual vane slots 4 in the rotor.
  • the vanes are of the two-lip type, and at their outer edges engage a cam surface 5 which is presented on a cam ring or stator 6.
  • Stator 6 and rotor l comprise an operating assembly in a pump body, not shown.
  • cam surface 5 is contoured so that pairs of diametrically opposite low presusre, inlet or suction zones at 10, transfer zones at ll, high pressure outlet or exhaust zones at 12, and sealing zones at 13,, are defined in the pumping space 14 between the cam surface 5 and the rotor l, as designated inFIG. 1.
  • cam surface 5 is formed in part from a pair of opposed arcs which extend across the transfer zones 11. While these arcs 15 are frequently called the major diameter part of the cam surface (see FIG. 2), they may have a slight ramp or inward lead in the direction of rotation. (In the drawings the direction of rotor rotation is shown as being counterclockwise).
  • a second pair of arcs 16 of shorter radius than the major diameter arcs 15 extend across the respective sealing zones 13 and define what is called the minor diameter portion of the cam surface.
  • the pairs of arcs l5 and 16 are interconnected by suction ramps I8 and pressure ramps 19, which extend across and bound the suction zone [0 and pressure zone 12.
  • suction ramps I8 and pressure ramps 19 which extend across and bound the suction zone [0 and pressure zone 12.
  • each pocket rceives fluid at the suction ports 20, which open to the respective suction zones 10, and delivers it to the pressure ports 22 which communicate with the respective pressure zones 12.
  • the so-called minor diameter part 16 of the cam surface instead of being a true arm or constant radius about the rotor center 17, has a slight ramp or lead.
  • the distance from the center 17 of rotor rotation to cam surface 5 progressively changes along this minor diameter arc.
  • the extent of this ramp is greatly exaggerated in the drawings, the ramp being much less than appears.
  • the ramp shown in FIGS. 1 and 2 on the sealing zone or minor diameter part of the cam ring is an out-ramp.
  • the ramp By reference to the concentric circles shown in FIG. 2, it will be seen that, with reference to the assumed counterclockwise direction of rotor rotation, the ramp progressively recedes from the center 17.
  • FIGS. 1 and 3 One form of such hydraulic pressure operated means is shown in FIGS. 1 and 3.
  • One or more pistons, each designated at 27, are supported for radial sliding movement in bores in rotor I. These bores extend inwardly toward the center of the rotor from the inner ends 26 of the vane slots. At the inner ends the piston bores are all connected by a circumferential channel in the rotor around shaft 2. This channel, not shown in the drawings, is supplied with pressure fluid from the pressure zone of the pump in a manner known per se, as for example shown in U.S. Pat. Nos. 2,832,293 and 3,223,044. The inner end of each piston is exposed to high pressure, but the outer end of the piston and the bottom of the vane in the slot end 26 are exposed to the pressure that prevails in slot 26 which varies as the rotor rotates.
  • FIG. 3 shows, at a greatly exaggerated angle, the contact between a hydraulic piston operated vane 3a and the minor diameter'part 16 of the cam surface in the sealing zone.
  • the front lip of this vane 3a is designated at 29, and the trailing or rear lip is designated at 30. Since the minor diameter l6 has an out-ramp, the trailing vane lip 30 is in contact with the ramp, and front lip 29 is spaced slightly below the cam surface.
  • the trailing face or surface 31 of the vane is exposed to pressure P from the pressure zone (see FIG. 1).
  • leading face or surface 32 of vane 3a is exposed to suction designated by the letter S, since that face of the vane is in communication with the suction zone 10.
  • the suction zone pressure acts on leading lip 29 of vane 3a and in the groove 33 that is between the two lips of the vane.
  • Groove 33 applies the (low) suction zone pressure to the bottom surface 34 of vane 3a in the bottom 26 of the rotor slot.
  • a low pressure acts over the entire inner end 34 of the 'vane, and across most-but not all-of the top of the vane.
  • Both the leading lip and the trailing lip of the vane have a slight round, as designated at 3%. These rounds are formed on the lips adjacent the front and rear faces 29 and 30 of the vanes. It will be noted that there is a small area designated at 36, behind (i.e., to the right in FIG. 3) of theline of contact 37 of the vane trailing lip 30 with the minor diameter 16. The tip area 36 sees or is exposed to the pressure P from the pressure zone. Apart from this small area on the top of the vane-perhaps 2 percent of the total area of the top the vane-the top and bottom of the vane are at essentially the same low pressure, and hence are pressure balanced, so that there is no net pressure force on them. The force applied to the hydraulic piston pin 27 is effectiye to urge the vane outwardly.
  • FIG. 6 of the drawings is a graph which illustrates or develops the radial distance between the cam surface and the rotor surface 23, as a function of angular po-' sition around the cam, starting (arbitrarily) from the beginning of the suction ramp.
  • the graph includes. slightly more than 180 of cam surface length, and for theb alanced cam ring'siiawmrwm be understood that the entire cam surface will include two full cycles, only one of which is shown.
  • the suction ramp 18 (designated in FIG. 6 as the portion 40 of the curve) progressively recedes from the periphery 23 of the rotor 1 across each suction zone 10, so that the volume be in the approximate range of W to 2. This is about the minimum amount necessary to insure that lip switching will not occur.
  • the ramp should be an in-ramp. This is illustrated in FIGS. 5 and 7.
  • a spring actuated vane is shown in contact with an in-ramped minor diameter 16 of the cam ring.
  • the vane is urged outwardly by one or more springs designated at 48 which at its end is received in sockets in the rotor and vane.
  • the leading lip 49 of the vane is in contact withthe ramp on minor diameter 16, and the trailing lip 50 is spaced from the cam surface.
  • the vane groove 51 communicates the pressure P behind the vane to the bottom 52 of the vane.
  • ramp angulation is designated at 44, and preferably is about /2", but as previously stated can advantageously surface, whereas if an out-ramp were used, the force of the spring might or might not be sufficient to accelerate the vane, as well as overcome the substantial vane to slot friction, sufficiently to maintain tracking.
  • FIG. 7 A development of the cam surface shape for a spring operated vane is shown inFIG. 7.
  • the minor diameter leads inwardly in the direction of rotation, rather than outwardly.
  • the angulation of the inward ramp 55 can be constant, and in the range of 3 4 to about 2. In a typical pump, this may amount to about 0.010 inches of inward vane travel in 1.25 inches of cam surface length.
  • vanes mounted in vane slots in one memberfor engaging a cam surface presented by the and the suction zone, said vanes being provided with means for biasing them towards the cam surface
  • a ramp on said cam surface extending substantially across said sealing zone, said ramp being an outramp and having an angulation of about 5 1 2 and allowing the vanes to move only radially outward relative to the center of rotation of the rotor, as said vanes traverse said sealing zone in sealing engagement with said ca m surface.
  • vanes are of the two-lip type.
  • vanes are of the two-lip type and are urged toward the cam surface by hydraulic pressure operated means acting thereon.
  • vanes are of the single lip type.
  • vanes are of the two-lip type and the ramp angulation is substantially the minimum angulation which maintains contact of the cam surface with the same lip of the vane as it traverses said sealing zone.
  • said ramp being at substantially the minimum angulation necessary to insure that a selected lip of each vane will continuously contact the cam surface across the said minor diameter portion.
  • a method of preventing lip switching as a two-lip vane moves across the minor diameter portion of the cam surface of a vane pump comprising,
  • a vane pump having vanes of the two-lip type and wherein the tops and bottoms of the respective vanes are hydraulically interconnected and the lips of the vanes engage a cam surface having a minor diameter surface portion, the improvement comprising,
  • said ramp being at an angulation and direction such as to maintain a first lip only of each said vane continuously in contact with said minor diameter portion while the respective vane is traversing it, the second lip of the said vane being spaced from the cam surface, the source of pressure exposed to the vane top and vane bottom thereby being unchanging as the vane traverses the minor diameter portion.
  • vanes In a vane type hydraulic pump having rotor and stator members and vanes mounted in vane slots in one member for engaging a cam surface presented by the other member, a pressure zone and a suction zone in the pumping space between the one member and said cam surface, a transfer zone and a sealing zone in said pumping space alternately between the pressure zone and the suction zone, said vanes being provided with means for biasing them towards the cam surface,
  • vanes being of the two-lip type
  • a ramp on said cam surface extending substantially across said sealing zone, said ramp having an anguynpf abqu -Z" Q1h EQQi$1YEUEEFEYEFE9 said sealing zone in sealing engagement with said cam surface, they move radially in a single direction thereon relative to the center of rotation of the rotor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US00246774A 1972-04-24 1972-04-24 Vane pump with ramp on minor diameter Expired - Lifetime US3785758A (en)

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US24677472A 1972-04-24 1972-04-24

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US (1) US3785758A (enrdf_load_stackoverflow)
JP (1) JPS5319121B2 (enrdf_load_stackoverflow)
CA (1) CA984671A (enrdf_load_stackoverflow)
DE (1) DE2313480C2 (enrdf_load_stackoverflow)
FR (1) FR2182446A5 (enrdf_load_stackoverflow)
GB (1) GB1424553A (enrdf_load_stackoverflow)
IT (1) IT977342B (enrdf_load_stackoverflow)

Cited By (13)

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Publication number Priority date Publication date Assignee Title
US4080124A (en) * 1974-11-04 1978-03-21 Trw Inc. Optimum porting configuration for a slipper seal pump
DE2912254A1 (de) * 1979-03-28 1980-11-06 Mainz Gmbh Feinmech Werke Rotationskolbenmaschine
US4284392A (en) * 1977-01-03 1981-08-18 Lear Siegler, Inc. Roller pump with radial members
US4486160A (en) * 1981-07-18 1984-12-04 Dowty Hydraulic Units Limited Pumps and motors
US4738603A (en) * 1983-03-08 1988-04-19 Kabushiki Kaisha Toyota Chuo Kenkyusho Hydraulic vane pump
DE3800324A1 (de) * 1987-01-09 1988-07-21 Diesel Kiki Co Fluegelzellenverdichter
US6086348A (en) * 1996-07-29 2000-07-11 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US6227832B1 (en) * 1997-08-28 2001-05-08 Michael Rechberger Rotating piston machine
CN101365880B (zh) * 2005-09-13 2011-01-19 亚历山大·阿纳托利耶维奇·施加诺夫 产生工作流体无湍流流动的方法及实施该方法的设备
CZ303465B6 (cs) * 2011-08-15 2012-09-26 Plíva@Roman Hydraulický lamelový prevodník s lamelami ve statoru
CN103912486A (zh) * 2013-01-09 2014-07-09 广西玉柴机器股份有限公司 叶片式输油泵
US20150027686A1 (en) * 2012-03-02 2015-01-29 Petrochina Company Limited Crude Oil Lifting System and Method Utilizing Vane Pump for Conveying Fluid
CN112648181A (zh) * 2020-12-04 2021-04-13 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵

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JPS6020593B2 (ja) * 1974-08-09 1985-05-22 テイ−、ア−ル、ダブリユ−、インコーポレーテツド 膨脹室型ポンプ
GB8417146D0 (en) * 1984-07-05 1984-08-08 Hobourn Eaton Ltd Roller-and vane-type pumps
JPS61124615A (ja) * 1984-11-17 1986-06-12 株式会社アデランス かつらベ−ス及びその製造方法
JPS62215003A (ja) * 1986-03-12 1987-09-21 株式会社　東京義髪整形 かつら
DE9102526U1 (de) * 1991-03-02 1992-04-02 Bergmann GmbH & Co KG, 7958 Laupheim Montur für den künstlichen Haarersatz
DE102010046591B4 (de) 2010-09-25 2015-03-12 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Flügelzellenpumpe

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US3481276A (en) * 1967-11-27 1969-12-02 Abex Corp Vane tracking in hydraulic pumps
US3711227A (en) * 1969-12-22 1973-01-16 A Schmitz Vane-type fluid pump
US3627456A (en) * 1970-03-25 1971-12-14 Diversified Prod Vanes for fluid power converter
US3652189A (en) * 1970-10-29 1972-03-28 Sperry Rand Corp Power transmission

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4080124A (en) * 1974-11-04 1978-03-21 Trw Inc. Optimum porting configuration for a slipper seal pump
US4284392A (en) * 1977-01-03 1981-08-18 Lear Siegler, Inc. Roller pump with radial members
DE2912254A1 (de) * 1979-03-28 1980-11-06 Mainz Gmbh Feinmech Werke Rotationskolbenmaschine
US4486160A (en) * 1981-07-18 1984-12-04 Dowty Hydraulic Units Limited Pumps and motors
US4738603A (en) * 1983-03-08 1988-04-19 Kabushiki Kaisha Toyota Chuo Kenkyusho Hydraulic vane pump
DE3800324A1 (de) * 1987-01-09 1988-07-21 Diesel Kiki Co Fluegelzellenverdichter
US6086348A (en) * 1996-07-29 2000-07-11 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US6227832B1 (en) * 1997-08-28 2001-05-08 Michael Rechberger Rotating piston machine
CN101365880B (zh) * 2005-09-13 2011-01-19 亚历山大·阿纳托利耶维奇·施加诺夫 产生工作流体无湍流流动的方法及实施该方法的设备
CZ303465B6 (cs) * 2011-08-15 2012-09-26 Plíva@Roman Hydraulický lamelový prevodník s lamelami ve statoru
US20150027686A1 (en) * 2012-03-02 2015-01-29 Petrochina Company Limited Crude Oil Lifting System and Method Utilizing Vane Pump for Conveying Fluid
CN103912486A (zh) * 2013-01-09 2014-07-09 广西玉柴机器股份有限公司 叶片式输油泵
CN112648181A (zh) * 2020-12-04 2021-04-13 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵
CN112648181B (zh) * 2020-12-04 2022-04-01 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵

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Publication number Publication date
FR2182446A5 (enrdf_load_stackoverflow) 1973-12-07
JPS5319121B2 (enrdf_load_stackoverflow) 1978-06-19
IT977342B (it) 1974-09-10
DE2313480C2 (de) 1983-08-18
DE2313480A1 (de) 1973-11-15
CA984671A (en) 1976-03-02
JPS4917506A (enrdf_load_stackoverflow) 1974-02-16
GB1424553A (en) 1976-02-11

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