US3818803A - Pumps - Google Patents

Pumps Download PDF

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Publication number
US3818803A
US3818803A US00307942A US30794272A US3818803A US 3818803 A US3818803 A US 3818803A US 00307942 A US00307942 A US 00307942A US 30794272 A US30794272 A US 30794272A US 3818803 A US3818803 A US 3818803A
Authority
US
United States
Prior art keywords
pump
cylinders
cylinder block
face
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00307942A
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English (en)
Inventor
G Scott
K Lloyd
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SEV PUMPS Ltd
SEVERN PUMPS Ltd GB
Original Assignee
SEV PUMPS Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SEV PUMPS Ltd filed Critical SEV PUMPS Ltd
Application granted granted Critical
Publication of US3818803A publication Critical patent/US3818803A/en
Priority to US05/699,688 priority Critical patent/USRE29519E/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • 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
    • 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
    • F04B1/2078—Swash plates
    • 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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/90—Slurry pumps, e.g. concrete

Definitions

  • a wedge device On the suction side a wedge device is arranged to direct the concrete into or away from the cylinders according to whether the solid lumps are correctly placed for easy entry into the cylinders or likely to cause an obstruction at the downstream end of the suction side.
  • a water barrier separates the concrete space from the oil filled drive mechanism and there is water lubrication of the working face of the cylinder block.
  • the suction space with which, the axial cylinders are in direct communication' is equipped with guide means for solids in suspension, the arrangement being such that over a first, exposed part of the suction space all liquids and solids have free access to the cylinders and over a second partof the suction space, circumferentially downstream of the first path, said guide means is operative selectively to urge the media carried towards it into the cylinders bya wedging action, and to reject and return to the first part solids that are not correctly sized and/or positioned for entry into the cylinders 'in the second P
  • the pump will be arranged so that there is gravity feed to the suction space. It will there-. fore be convenient hereafter to refer to the pump in that attitude with
  • the guide means preferably takes the form of a wedge member curving around the axis of the pump from a point substantially at the centre of the suction to a valve blade which divides the suction from the discharge side of the pump.
  • This valve blade may extend 2 diametrically across the pump and be-offset by a small angle circumferentially downstream from the, plane through the upper and lower dead centre positions of thepistons.
  • Slurry being gravity fed to the suction side either enters the cylinders directly during the first half of the pistons suction stroke or is carried on the upper end face of the cylinder block towards the wedge member.
  • the slurry that enters the mouth of the V or U-shaped tunnel is guided towards the centre of the cylinder path, where the land area between adjacent cylinders is a minimum, and is both drawn into the cylinders by the suction effect and pushed thereinto by the wedging effect of the tunnel roof.
  • Any solids in the slurry that cannot readily enter the tunnel (for example those near the edges of the cylinder path) are carried up onto the curved ramp and return eventually by gravity and suction into the first suction part, where they have another chance of entering a cylinder.
  • the cylinder bores will be of considerably greater diameter than the maximum size of solids to be handled by the pump.
  • the outlet side of the pump is, of more conventional form.
  • a connector is provided which has a kidney shaped mouth for co-operating-with a kidney shaped port over the outlet side and a circular outlet for fitting directly to the discharge pipeline.
  • a water barrier between the working face of the pistons and the piston rods and their drive mechanism This may be achieved by making each piston double headed with a space between the heads. These spaces are filled by water which has access through ports in the side of the cylinder bore to a cavity of the cylinder block. A continuous circulation of water is maintained to lubricate the cylinders, both by the axial motion of the pistons and by the rotational motion of the cylinder block.
  • an annular water channel or groove, eccentric with respect to the pump axis is provided in part of the pump housing that cooperates with the periphery of the working end face.
  • the pump housing may conveniently have trunnions or other means for pivoting it for ready access.
  • its axis will be vertical and it will generally be mounted beneath a hopper for liquid concrete.
  • FIG. 1 is a diagrammatic plan view of an axial piston pump showing the suction and discharge sides
  • FIG. 2 is a perspective view of guide means for the suction side of the pump, and a cross-section thereof,
  • FIG. 3 is a diagrammatic plan view of an outlet connector for the pump
  • FIG. 4 is an axial section of the pump of FIG. 1, and
  • FIG. 5 is a detail of FIG. 4.
  • the axial piston pump has a cylinder block 1 with seven cylinders 2.
  • the block 1 rotates in a clockwise direction as viewed in FIG. 1 and the suction side is on the left and the outlet side on the right of a valve plate or blade 3 which extends diametrically across the end face of the cylinder block at a small angle, 12 for example, to the line 4 between the upper and lower dead centre positions of the pistons 5.
  • This retardation of the valve blade 3 is to avoid concrete mix being forced up under the blade, and possibly causing distortion and leakage, at the final stages of a delivery stroke when a piston is in the 5 to 6 oclock region.
  • the blade 3 may be fixed or be adjustable within limits.
  • the upper surface of the member 6 is a ramp 612 that extends upwardly from B towards C and which may also be canted inwardly towards the axis of the ramp.
  • Material that does not immediately enter the cylinders in the AB quadrant is carried on the end face of the cylinder block 1 towards the mouth of the tunnel of the member 6. Any large solids that hit the mouth of the tunnel are either directed up the ramp and return eventually by gravity and suction to join the other material being fed to the AB quadrant, or else are drawn into the tunnel where they are directed towards the centre of the path of the piston and cylinders.
  • the pistons 5 are receding and the block 1 is rotating and therefore although a solid might not immediately be sucked into a cylinder it can be drawn along the tunnel and urged downwardly and towards the centre of the tunnel by the roof of the latter and by the suction effect of the pistons. It will then be drawn into a succeeding cylinder.
  • each cylinder mouth may be cut away as indicated at 7 on one of the cylinders in FIG. 1.
  • the outlet side of the pump has a funnel-like member 8 (FIG. 3) fitted thereto, the mough adjacent the pump being kidney-shaped for fitting a correspondingly shaped outlet port and the outlet being circular for fitting directly to a pipe line, without a reducer transition section.
  • the rotary drive is applied to the cylinder block 1 by means of a shaft 9 fixed thereto or integral therewith and extending co-axially out from the base of a housing 10.
  • a swash plate 11, of a fixed angle in this example rotates on a ramp 12 through hydrostatic pads 13, being driven from the shaft 9 via bevel gears 14 and 15, the gear 15 being sleeved on the shaft and fixed against rotation with respect thereto by a pin 16 which extends radially from the shaft through an axial slot 17 in a sleeve portion of the gear 15.
  • the latter is urged into engagement with the gear 14 fast with the swash plate 11 by means of a spring 18 reacting against the base of the cylinder block 1.
  • the spring bias is provided primarily for the pump priming stage, when the swash plate might otherwise tend to lift off the ramp.
  • Piston rods 19 having spherical ends are captive to the swash plate 11 by means of v readily replaceable socket and plate assemblies 20 and to the ends of the pistons 5 by means of plates 21. These ends are hydrostatically padded, the rods 19 being co-axially bored for the passage of oil and the swash plate, ramp and housing having oil ducting as shown in FIG. 4.
  • Each piston comprises a main core 22 having an enlarged nonworking end 23 with which the associated piston rod co-operates.
  • a flattenable, but normally dished spring washer 27 acts between a shoulder abovethe enlarged head end of the core 22 and the lower piston head 25 and cushions and limits downward movement of the piston heads and sleeve with respect to the core. This facility for limited axial movement is provided to reduce shock loading in the event of any small particles in the pumped material not allowing the normal full stroke of the piston.
  • the piston head 24 has a cap 28 the interior of which is normally axially spaced from the head of a bolt 29 which is secured at the end of the core 22. This bolt 29 provides an axial stop against the piston head 24 escaping the core 22.
  • a triangular section sealing ring 30 of rubber or other resilient material At the perimeter of the working side of the piston head 24 there is bonded a triangular section sealing ring 30 of rubber or other resilient material, the rim of the cap 28 being cut away to accommodate this, and there is a similar ring 30 on the same side of the other piston head 25.
  • the cylinder block 1 is a hollow casting or of fabricated form and the walls of each cylinder have ports 31 which place the space between the piston heads 24 and 25 in communication with a central space 32 to which a continuous supply of water is maintained. These ports 31 may be continuously open whatever the piston position or at least are never exposed above the piston head 24 or below the piston head 25.
  • the water supply to the space 32 is via a connection 33 central of the valve blade 3, a water seal 34 at the end of the shaft 9 where it is carried by a bearing 35 within the valve blade, a coaxial drilling 36 through the shaft 9 to a point within the block 1 and radial ports 37.
  • the water eventually es- '5' capes through angled ports 38, one of which is shown in FIG. 5.
  • Each cylinder is lined with hard chromed liners 51 pressed or bonded in and retained by the replaceable wear plate 40.
  • the perimeters of this wear plate and the end plate 39 project radially of the cylinder block and are axially confined between hydrostatic bearings 45 and the flange 42 of the housing 10.
  • This seal comprises an annular groove 46 in the underside of the flange 42 and having two sealing rings 47 and 48 against the radially inner and outer walls respectively, to leave a passage for water.
  • Water supplied to this passage via an inlet 49 is maintained at a pressure greater than that of the normal outlet pressure of the pump so that there tends to be seepage of water radially inwards, thereby lubricating the face of the wear plate.
  • This annular groove is not concentric with the axis of the pump but is slightly eccentric thereto so as to obtain a better spread of lubricating water, to reduce the heat generation and to assist heat dissipation.
  • v The exterior of the housing 10 is provided with trunnions 50 to enable the whole pump to be pivoted easily away from its working position, for example to-be washed out after use.
  • the gears 14 and 15 cannot transmit sufficient torque.
  • the perimeters of the underside of the cylinder block 1 and of the upper face of the swash plate 11 are provided with large diameter bevel gears that mesh below the top dead centre piston position. These will surround the piston rods 19 as opposed to being within the cage formed by those rods. These will still be spring loading of the swash plate through one or more springs acting between the block 1 and the base of shallow conical thrust member resembling the gear 15 but without teeth, the conical face bearing on the swash plate.
  • axial piston pumps giving continuous flow are possible and the number of pistons may differ from seven.
  • a tilting cylinder-block pump of the Thoma type may be used instead of aswash plate pump.
  • variable displacement versions of these pumps may be employed. All these pumps will work satisfactorily on liquids without solids in suspension. They are readily mounted on mobile trailers or directly on mixer trucks. and can be driven by a power take-off or an auxiliary prime mover. There is no requirement for any external valve mechanism hydraulically or otherwise operated.
  • the tunnel of the wedge member 6 can be of inverted U or other cross-sectional form.
  • a re-mixer at the hopper delivery end orwithin a funnel that may form the inlet to the pump.
  • This is a rotating blade or blades whose drive is conveniently taken from the pump prime mover.
  • the re-mixer drive shaft may be geared to or be chain driven from the shaft 9.
  • the pump has been described for convenience with its axis vertical, it can operate equally well in different attitudes provided gravity feed to the suction side can be established.
  • its axis may be horizontal with the suction side uppermost.
  • a hopper or funnel adapted to channel concrete mix downwards and inwards towards the pump.
  • An axial piston pump adapted for pumping concrete or other abrasive media and slurries, including a cylinder block with an annular array of axially parallel cylinders, each with a reciprocable piston therein and a working end face to which the cylinders open; bearing means for locating said block in an axially fixed position; means co-operating with said face to divide it into an inlet and a delivery side; means for reciprocating the pistons to give them suction strokes on the inlet side and pressure strokes on the delivery side, the strokes commencing at an upstream end and finishing at a downstream end of the respective side to draw and discharge media progressively into and from the cylinders; guide means disposed in the circumferentially downstream portion of the inlet side, leaving the upstream portion of the inlet side free and the full diametral extent of said cylinders exposed in that upstream portion, said guide means having a first surface facing said cylinder block and forming a convergent tunnel therewith, open at the upstream end and narrowing in
  • valve blade is offset a small angle circumferentially downstream from the plane through the upper and lower dead centre positions of the pistons.
  • a pump as claimed in claim 1 wherein a fluid barrier is continuously provided between the working faces of the pistons and said reciprocating means, the pistons being double headed with a space between the heads which is filled by fluid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US00307942A 1971-11-24 1972-11-20 Pumps Expired - Lifetime US3818803A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US05/699,688 USRE29519E (en) 1971-11-24 1976-06-25 Pumps

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB5430371A GB1411084A (en) 1971-11-24 1971-11-24 Pumps

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/699,688 Reissue USRE29519E (en) 1971-11-24 1976-06-25 Pumps

Publications (1)

Publication Number Publication Date
US3818803A true US3818803A (en) 1974-06-25

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ID=10470576

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Application Number Title Priority Date Filing Date
US00307942A Expired - Lifetime US3818803A (en) 1971-11-24 1972-11-20 Pumps

Country Status (6)

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US (1) US3818803A (it)
AU (1) AU470329B2 (it)
DE (1) DE2257455A1 (it)
ES (1) ES408911A1 (it)
GB (1) GB1411084A (it)
IT (1) IT974845B (it)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999895A (en) * 1971-11-29 1976-12-28 Bede Alfred Boyle Rotating barrel pump
US4044654A (en) * 1974-03-27 1977-08-30 D. B. A. Hydraulic engine
US4131395A (en) * 1976-09-29 1978-12-26 Gusmer Corporation Feeder for apparatus for ejecting a mixture of a plurality of liquids
US4516475A (en) * 1977-07-02 1985-05-14 Robert Bosch Gmbh Hydrostatic piston machine
US4872394A (en) * 1984-02-29 1989-10-10 Shimadzu Corporation Bent axis type axial piston pump or motor
US5000667A (en) * 1988-06-07 1991-03-19 Matsushita Electric Industrial Co., Ltd. Movable slanting plate type compressor
US5013219A (en) * 1989-02-09 1991-05-07 The University Of Delaware Positive displacement piston pump
WO2004035228A3 (en) * 2002-10-15 2004-07-15 Matsushita Electric Industrial Co Ltd Paste ejection apparatus
US20050147507A1 (en) * 2002-02-13 2005-07-07 Hiroyuki Makino Expander
CN100359162C (zh) * 2002-10-15 2008-01-02 松下电器产业株式会社 挤胶设备
CN103352822A (zh) * 2013-06-20 2013-10-16 山东科技大学 柱塞斜盘式泥浆泵
CN104847619A (zh) * 2015-01-29 2015-08-19 北汽福田汽车股份有限公司 混凝土泵送机构及包括其的混凝土输送设备
US10995745B1 (en) * 2020-01-15 2021-05-04 Texas Institute Of Science, Inc. Submersible pump assembly and method for use of same
US20210190066A1 (en) * 2019-12-19 2021-06-24 Danfoss A/S Valve plate assembly
AU2020424507B2 (en) * 2020-01-23 2022-09-08 Hess Corporation Submersible pump assembly and method for use of same

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE449391B (sv) * 1982-04-07 1987-04-27 Asea Atom Ab Kolvpumpanordning for pumpning av en blandning av grovkornigt material och vetska
CA2154875A1 (en) * 1993-02-02 1994-08-18 Karl Schlecht Process for conveying thick matter containing preshredded scrap metal or similar solids

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US985835A (en) * 1908-12-28 1911-03-07 Universal Speed Control Company Variable-fluid gear.
US1483199A (en) * 1920-12-16 1924-02-12 William H Keller Inc Rotary piston drill
US2633104A (en) * 1949-07-15 1953-03-31 Borg Warner Motor port construction
GB895070A (en) * 1959-11-04 1962-04-26 Otto Max Kastner Improvements in or relating to piston pumps
US3270686A (en) * 1964-02-13 1966-09-06 Daytona Thompson Corp Pump and releasable housing therefor
DE1926278A1 (de) * 1969-05-22 1970-11-26 Boyer Jean Jacques Einrichtung fuer hydraulische Trommelpumpen zum Schutz der Gleitflaechen bei Nulleistung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US985835A (en) * 1908-12-28 1911-03-07 Universal Speed Control Company Variable-fluid gear.
US1483199A (en) * 1920-12-16 1924-02-12 William H Keller Inc Rotary piston drill
US2633104A (en) * 1949-07-15 1953-03-31 Borg Warner Motor port construction
GB895070A (en) * 1959-11-04 1962-04-26 Otto Max Kastner Improvements in or relating to piston pumps
US3270686A (en) * 1964-02-13 1966-09-06 Daytona Thompson Corp Pump and releasable housing therefor
DE1926278A1 (de) * 1969-05-22 1970-11-26 Boyer Jean Jacques Einrichtung fuer hydraulische Trommelpumpen zum Schutz der Gleitflaechen bei Nulleistung

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999895A (en) * 1971-11-29 1976-12-28 Bede Alfred Boyle Rotating barrel pump
US4044654A (en) * 1974-03-27 1977-08-30 D. B. A. Hydraulic engine
US4131395A (en) * 1976-09-29 1978-12-26 Gusmer Corporation Feeder for apparatus for ejecting a mixture of a plurality of liquids
US4516475A (en) * 1977-07-02 1985-05-14 Robert Bosch Gmbh Hydrostatic piston machine
US4872394A (en) * 1984-02-29 1989-10-10 Shimadzu Corporation Bent axis type axial piston pump or motor
US5000667A (en) * 1988-06-07 1991-03-19 Matsushita Electric Industrial Co., Ltd. Movable slanting plate type compressor
US5013219A (en) * 1989-02-09 1991-05-07 The University Of Delaware Positive displacement piston pump
US20050147507A1 (en) * 2002-02-13 2005-07-07 Hiroyuki Makino Expander
WO2004035228A3 (en) * 2002-10-15 2004-07-15 Matsushita Electric Industrial Co Ltd Paste ejection apparatus
CN100359162C (zh) * 2002-10-15 2008-01-02 松下电器产业株式会社 挤胶设备
CN103352822A (zh) * 2013-06-20 2013-10-16 山东科技大学 柱塞斜盘式泥浆泵
CN104847619A (zh) * 2015-01-29 2015-08-19 北汽福田汽车股份有限公司 混凝土泵送机构及包括其的混凝土输送设备
CN104847619B (zh) * 2015-01-29 2018-02-23 北汽福田汽车股份有限公司 混凝土泵送机构及包括其的混凝土输送设备
US20210190066A1 (en) * 2019-12-19 2021-06-24 Danfoss A/S Valve plate assembly
US11555488B2 (en) * 2019-12-19 2023-01-17 Danfoss A/S Valve plate assembly
US10995745B1 (en) * 2020-01-15 2021-05-04 Texas Institute Of Science, Inc. Submersible pump assembly and method for use of same
AU2020424507B2 (en) * 2020-01-23 2022-09-08 Hess Corporation Submersible pump assembly and method for use of same

Also Published As

Publication number Publication date
AU470329B2 (en) 1976-03-11
IT974845B (it) 1974-07-10
DE2257455A1 (de) 1973-05-30
ES408911A1 (es) 1975-10-16
AU4920772A (en) 1974-06-06
GB1411084A (en) 1975-10-22

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