US3339830A - Vacuum operated pump - Google Patents

Vacuum operated pump Download PDF

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Publication number
US3339830A
US3339830A US584398A US58439866A US3339830A US 3339830 A US3339830 A US 3339830A US 584398 A US584398 A US 584398A US 58439866 A US58439866 A US 58439866A US 3339830 A US3339830 A US 3339830A
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United States
Prior art keywords
piston
pressure
diaphragm
rod
cylinder
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Expired - Lifetime
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US584398A
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English (en)
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George C Graham
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Individual
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Individual
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Priority to US584398A priority Critical patent/US3339830A/en
Priority to ES344367A priority patent/ES344367A1/es
Priority to DE19671653468 priority patent/DE1653468A1/de
Priority to FR1553754D priority patent/FR1553754A/fr
Priority to GB40243/67A priority patent/GB1192467A/en
Application granted granted Critical
Publication of US3339830A publication Critical patent/US3339830A/en
Anticipated expiration legal-status Critical
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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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/008—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being a fluid transmission link
    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/1207—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air using a source of partial vacuum or sub-atmospheric pressure

Definitions

  • This invention relates to a novel vacuum operated pump or compressor for use in connection with motor vehicle and stationary engines or other vacuum sources for establishing and maintaining fluid pressure in systems such as shock absorbers, tire inflating devices, or other systems requiring compressed air and other fluids under pressure.
  • the pump or compressor herein is designed for low cost manufacture, low friction operation, and minimum wear with little, if any, lubrication being required after original assembly of the device while, at the same time, efiicient functioning of the operating parts is ensured.
  • a salient feature of the invention is the provision of a piston in the subject pump which is mounted without close tolerances within its pumping cylinder while other piston assembly components and mountings have ample clearances to permit free movement thereof without reducing the pumping or compression efficiency of the device.
  • Another important feature of the invention is the isolation of the pumping cylinder from the vacuum chamber of the device whereby high pumping efliciency is realized and a lesser quantity of negative air pressure is required to operate the device as compared with previous conventional apparatus.
  • the vacuum or'negative air pressure power unit always has the same maximum thrust which is not appreciably decreased, if at all, by increased size of the compression piston and its cylinder. Accordingly, the same vacuum or negative air pressure unit can serve as a source of power for a wide range of pressure pistons and cylinders of different sizes for air compression units with only minor changes being required in substituting the pressure piston and cylinder components thereof.
  • the reciprocating pump assembly comprises a flexible diaphragm to the opposite sides of which two separate pistons are mounted, it is difiicult to obtain precision alignment of a common axis between said pistons, while at the same time the flexibility of the diaphragm introduces the possibilities of deviation of reciprocating movement of the piston assembly from a true rectilinear axis.
  • the achievement of a desirable straight line axis for the two piston rods and of the diaphragm assembly in a true rectilinear axis would ordinarily involve high cost precision manufacturing and assembly techniques which 3,339,830 Patented Sept. 5, 1967 are prohibitive for general purpose low cost vaccum pumps.
  • the structure 'of the present invention provides a pivoting axis for the piston-diaphragm assembly in the region of the partition between the vacuum chamber and the pressure cylinder where a ring seal and retainer ring are located so that deviations of movement from a true axis are compensated for even though the component parts are made according to low or moderate cost normal manufacturing tolerances. Therefore, even though each of the component parts of the piston-diaphr-agm assembly do not move in a constant straight line axis, the partition seal and the pressure piston rod seal will nevertheless effectively maintain the integrity of their scaling functions.
  • piston-diaphragm apparatus may be assembled out of true axial alignment because of normal manufacturing tolerances and notwithstanding the existence of a pivoting axis for said piston-diaphragm assembly, nevertheless effective seals are maintained during reciprocating action by the pressure piston and the piston rod seal.
  • FIGURE 1A is a vertical central section of the pump of the present invention showing the movable pumping elements located at the end of the pressure stroke;
  • FIGURE 1B is comparable to 1A showing a vertical central section of the pump showing the pumping elements located at the end of the suction stroke.
  • each figure of the drawing each show one-half of the complete device as a semi-circular section, wherein like numbers refer to some of the same parts although they are shown in different operational locations. Except for the control valve mechanisms, each part of the device may be assumed to be substantially circular in crosssection. Some parts of the drawing are shown in elevation and other parts are indicated diagrammatically.
  • the body of the device comprises a pair of bell sections 11 and 12, each having annular mating flanges 13 and 14, respectively, which are secured together by means of a plurality of spaced apart bolts 16.
  • Clamped fast between flanges 13 and 14 is the peripheral edge portion of a flexible diaphragm 17 which is movable within space enclosed by bell sections 11 and 12 and which divides and separates said space into two chambers 18 and 19 which vary inversely in volume according as said diaphragm moves in one direction or the other.
  • dome 22 Formed integrally with the end wall 21 of bell section 11 is a dome 22 of circular cross-section enclosed by an integrally formed end wall 23. Dome 22 surrounds a dummy piston chamber 24.
  • Bell section 12 has an end wall or partition 26 having a central axial aperture 27 through which a piston rod 28 moves reciprocably, there being a slight clearance between said rod and said aperture.
  • Movable reciprocably within piston chamber 24 is a dummy piston rod 29, the inner end of said rod being threadably secured to the inner reduced end portion of piston rod 28.
  • Mounted on opposite sides of the central portion of diaphragm 17 are circular clamp plates 31 and 32, said clamp plates being urged toward each other by virtue of opposing shoulders 33 and 34 of rods 28 and 29, respectively, bearing upon said plates when said rods are threadably secured together, a central portion of rod 28 extending through axially aligned central apertures in said clamp plates and said diaphragm.
  • a dummy piston head 36 Integrally formed or otherwise mounted at the outer end of rod 29 is a dummy piston head 36 which has a pair of spaced apart annular flanges 37 and 38 whose peripheries are spaced apart from and move with clearance relative to the interior surface of dummy cylinder 24.
  • annular recess 39 Formed between flanges 37 and 38 of dummy piston head 36 is an annular recess 39 which optionally accommodates a lubricated or unlubricated felt or plastic cut ring 41 which ensures that flanges 37 and 38 do not cause serious scoring between the metal parts.
  • ring 41 may be loose enough to permit air to bypass said ring when piston head 36 moves reciprocably within said cylinder.
  • dummy piston head 36 may have a longitudinal aperture 42, off-center axially, that serves as an air vent or hole in order to ensure free flow of air when a thicker ring 41 is used or provided.
  • a circular outwardly extending collar 43 that is located coaxially relative to aperture 27 in said end wall, and has a somewhat greater diameter than said aperture.
  • a circular adapter ring 44 Threadably connected to the outer end of collar 43 is a circular adapter ring 44 having an integrally formed, outwardly extending, L-shaped annular flange 46.
  • a circular porous filter ring 47 Secured between end wall 26 of bell section 12 and flange 46 is a circular porous filter ring 47 made of helically wound cellulose ribbons or suitable material.
  • the pumping or compression component of the device comprises a circular compression cylinder 51, the inner end of which fits at least partially into a mating circular recess 52 formed within the confines of flange 46 of ring 44.
  • a circular compression cylinder 51 Intermediate the ends of compression cylinder 51 and formed integrally on the surface thereof is an outwardly extending annular flange 53, a lateral surface of which mates with an opposing lateral surface of flange 46 and is secured thereto by a plurality of spaced apart bolts 54 circularly arrayed in said flanges.
  • the outer end of cylinder 51 terminates in an integrally for-med end wall 56 to enclose a pumping or compression chamber 57.
  • valve housing 61 Located centrally in end wall 56 is an outlet port 58 which communicates with valve chamber 59 within valve housing 61 formed integrally with an extending outwardly from said end wall.
  • a check valve 62 Positioned within valve chamber 59 is a check valve 62 that is urged against valve seat 63 by one end of a valve spring 64, the other end of which bears against a plug 66 threadably inserted into the end of valve housing 61.
  • Plug 66 is threadably tightened by means of a nut 67 integrally formed with said plug, the latter having an integrally formed, outwardly extending connection tube 68.
  • Plug 66, nut 67 and tube 68 have a common central aperture 69.
  • Connection tube 68 may be provided with sawtooth ridges for accommodating flexible connecting tubing or the like.
  • Piston 71 Threadably or otherwise mounted on the outer end of piston rod 28 is a piston 71 of enlarged diameter whose periphery is somewhat spaced apart from the interior wall of cylinder 51.
  • Piston 71 has an annular recess 72 bounded by spaced apart flanges 73 and 74, said recess loosely accommodating an elastic, flexible O-ring 76.
  • O-ring 7-6 is urged outwardly and against flange 73 to act as an air-tight seal between piston 71 and the interior wall of cylinder 51 whereby pressure is produced within said cylinder to cause fluid or air to move through port 58 and to urge check valve 62 away from valve seat 63 against the action of spring 64, whereby compressed air passes outwardly through pipe 68.
  • O-ring 76 is urged against flange 74 whereby air bypasses said O- ring through recess 72 and through one or more spaced apart apertures 77 in flange 74 as well as between periphery of piston 71 and interior wall of cylinder 51.
  • Equalizing atmospheric air is provided for cylinder 51 by means of one or a plurality of spaced apart apertures 78 arrayed in a circle in adapter ring 44, said atmospheric air reaching said apertures by passing through porous filter ring 47.
  • end wall 26 has an annular coaxially aligned recess of somewhat enlarged diameter formed by the juncture between an annular sloping wall 81 and an annular perpendicular wall 82. Nested in said recess is a somewhat loosely fitting resilient O-ring 83 which is retained therein by means of a washer 84 made of a suitable low friction plastic material such as Delrin, nylon, Teflon, or of a material which is substantially self-lubricating or compatible relative to piston rod 28.
  • a washer 84 made of a suitable low friction plastic material such as Delrin, nylon, Teflon, or of a material which is substantially self-lubricating or compatible relative to piston rod 28.
  • washer 84 may be made of a suitable material which, when initially lubricated at the time of assembly of the apparatus, requires no lubrication thereafter. Washer 84 is retained against an annular shoulder 85 in the interior of collar 43 by means of a spider ring 86 frictionally engaging an annular longitudinal wall 87 in the interior of said collar.
  • the inside diameter of washer 84 is slightly larger than the outside diameter of piston rod 28.
  • the latter may be provided with one or a plurality of spaced apart apertures 87 arrayed circularly in said washer.
  • the material of washer 84 is selected to have the characteristics of low friction relative to the material of piston rod 28 in order to prevent any scoring or damage of said rod.
  • the relative diameters of aperture 27 and rod 28 are selected whereby a loose bearing fit exists between those two elements.
  • pressure cylinder 51 and adapter ring 47 may be threadably removed from collar 43 and replaced by a cylinder-adapter assembly of a different size, while piston 71 may also be removed from piston rod 28 and replaced by a piston that cooperates dimensionally with the substituted cylinder.
  • Boss 92 encloses a control valve chamber 93 which has a pair of spaced apart ports 94 and 95 which communicate by respective pipe lines 96 and 97, with ports 98 and 99 in respective bell sections 11 and 12.
  • Pipe lines 96 and 97 are illustrated diagrammatically. Ports 98 and 99 each communicate with respective chambers 18 and 19 on opposite sides of diaphragm 17.
  • valve 102 mounted pivotally on shaft 101 in valve chamber 93 is an oscillating valve 102 which has an arcuate slot 103 on one flat side which is positionable in either of two locations whereby port 104 communicating with pipe 91 is operatively connected alternatively with either port 94 or port 95.
  • valve 102 When valve 102 is in the position shown in solid lines in FIGURE 1A establishing communication between ports 94 and 104, negative air pressure induced by way of pipe 91 through port 104 is transmitted by slot 103 to port 94 whereby negative pressure is induced in chamber 18.
  • slot 103 establishes communication between ports 104 and 95 whereby negative pressure is induced in chamber 19.
  • valve 102 is spaced apart from either one of ports 94 or 95,the latter communicates with atmospheric air whereby such air can enter into one of the corresponding chambers 18 and 19 when the other is subjected to negative pressure.
  • valve and porting mechanisms and functions are well known in the art which accounts for their being represented diagrammatically herein.
  • valve 102 Connected to valve 102 is a rocker control lever 106' which is movable equi-angularly with said valve.
  • Lever 106 extends movably through a suitable isolation barrier 107, illustrated diagrammatically, Which separates valve chamber 93 from the interior of cylinder 22 and chamber 18 where negative pressure is intermittently induced.
  • isolation barrier 107 illustrated diagrammatically, Which separates valve chamber 93 from the interior of cylinder 22 and chamber 18 where negative pressure is intermittently induced.
  • the structural and functional means for setting up such an isolation barrier are well known in the art.
  • rocker control level 106 extends into the space substantially at the juncture between cylinder 22 and bell section 21.
  • rocker control lever 106 Upon the upward movement of piston rod 29 and of dummy piston 36, the head of rocker control lever 106 is engaged by the upper surface of an outwardly extending boss 108 formed on piston rod 29 causing said rocker control lever to move pivotally into a position as shown in dotted outline in FIGURE 1A whereby communication is established between ports 95 and 104.
  • control valve 102 is in either of the two alternate positions shown in FIGURE 1A, negative pressure is established alternately in chamber 18 and 19 on opposite sides of diaphragm 17 whereby said diaphragm is caused to move reciprocably within the space formed between bell sections 11 and 12, thereby causing piston rod 28 and piston 71 to move reciprocably within thechamber of pumping or compressing cylinder 51.
  • work piston 71 is moved reciprocably by the action of diaphragm 17 moving alternately within the space defined by bell sections 11 and 12 by means of alternately induced negative pressures in chambers 18 and 19.
  • negative pressure is induced in chamber 18, for example, as when control valve 102 is in the solid line position as shown in FIGURE 1A, chamber 19 is opened to atmospheric pressure since port 95 communicates" with atmospheric pressure in valve chamber 93 by means'well known in the art.
  • control valve 102 is in a position where it provides communication between port 104 and ,port 95, negative pressure is induced in chamber 19 to cause the diaphragm to move downwardly to produce the pressure stroke of piston 71.
  • port 94 is open to atmospheric pres: sure which, in turn, provides atmospheric pressure for chamber 18.
  • O-ring seal acts as a one-way, one-purpose seal. Whatever frictional engagement there may be between O-ring 83 and the surface of piston rod 28 tending initially to move in the same direction, it is immediately superseded by the far superior influence of the negative pressure in chamber 19 to produce the necessary scaling function in the opposite direction.
  • Washer 84 acts as a retainer for O-rin'g 83 in its recess while also serving as a loose bearing for piston rod 28.
  • a pump having a reciprocating assembly as shown and described herein would normally have four potential spaced apart points or areas of contact between moving and stationary parts. They comprise the dummy piston 36 relative to cylinder 22, the area where diaphragm 17 is secured by clamp plates 31 and 32, the seal provided by O-ring 83, and the O-ring 76 providing the pressure seal for work piston 71.
  • the present invention permits the use of wide manufacturing tolerances in respect of dummy piston 36, work piston 71, the clamping means for diaphragm 17, and the O-ring seal for work piston 71, thereby realizing low manufacturing costs.
  • dummy piston 36 does not perform any fluid pumping action, nevertheless it does operate in conjunction with cylinder 22 as a dashpot to prevent excessive speed of travel on the upward or retraction stroke of work piston 71.
  • the number or the diameter size of air vents 42 in the dummy piston 36 may be determined by the dash-pot effect that is necessary or desired in conjunction with the other operating parts of the pump.
  • the device of the present invention produces pressures of from about 150% to 25 respectively, greater than those units where the vacuum chamber is not isolated from the pressure chamber.
  • the quantity of negative air pressure as represented by cubic inches of space on the work side of diaphragm 17 in chamber 19 where the power producing action takes place is between about 68% to 25% less in the apparatus of the present invention than in other devices where there is no isolation between the vacuum chamber and the work piston chamber.
  • the present invention requires a considerably lesser quantity of vacuum or negative air pressure that is to be drawn from the internal combustion engine which is the source of the negative air pressure.
  • vacuum chamber 19 is greatly reduced in volume whereby the negative pressure induced therein is more effectively operative upon diaphragm 17.
  • a pump comprising a housing, a flexible diaphragm mounted in said housing and dividing the interior of the latter into first and second vacuum chambers, means for subjecting said first and second vacuum chambers alternately to negative pressure and atmospheric pressure for moving said diaphragm reciprocably within said housing, a pressure cylinder on said housing, a partition between said pressure cylinder and said first vacuum chamber, a piston rod connected to one side of said diaphragm, an aperture in said partition through which said rod moves reciprocably, a portion of said rod extending into said pressure cylinder, a piston mounted on said rod and movable reciprocably within said pressure cylinder, and oneway sealing means mounted between said rod and said partition effectively isolating said first vacuum chamber from said pressure cylinder during the time when said first vacuum chamber is under negative pressure to cause said diaphragm to perform the pressure stroke for said rod and said piston, said one-way sealing means being exposed to and being activated by atmospheric pressure to produce its sealing function.
  • a pump comprising a housing, a flexible diaphragm mounted in said housing and dividing the interior of the latter into first and second vacuum chambers, said diaphragm being movable reciprocably within said housing, a pressure cylinder on said housing, a partition between said pressure cylinder and said first vacuum chamber, a piston rod connected to one side of said diaphragm and movable therewith, an aperture in said partition through which said piston rod moves reciprocably, a portion of said piston rod extending into said pressure cylinder, a piston on said piston rod movable reciprocably within said pressure cylinder, and a one-way first seal between said piston rod and said partition, a second seal between said piston and the interior wall of said pressure cylinder, the axis of said piston rod being yieldably pivotable in the region of said first seal to accommodate the deviation of reciprocating movement of the piston rod-diaphragm assembly from a true axis, said second seal maintaining the seal between said piston and interior wall of said pressure cylinder despite such deviation during the pressure stroke of said piston,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Atmospheric Sciences (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US584398A 1966-10-05 1966-10-05 Vacuum operated pump Expired - Lifetime US3339830A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US584398A US3339830A (en) 1966-10-05 1966-10-05 Vacuum operated pump
ES344367A ES344367A1 (es) 1966-10-05 1967-08-23 Una bomba de funcionamiento por vacio para establecer y mantener una presion de fluido en vehiculos de motor.
DE19671653468 DE1653468A1 (de) 1966-10-05 1967-08-31 Durch Unterdruck angetriebene Pumpe
FR1553754D FR1553754A (de) 1966-10-05 1967-09-01
GB40243/67A GB1192467A (en) 1966-10-05 1967-09-04 Vacuum Operated Reciprocating Pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US584398A US3339830A (en) 1966-10-05 1966-10-05 Vacuum operated pump

Publications (1)

Publication Number Publication Date
US3339830A true US3339830A (en) 1967-09-05

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Application Number Title Priority Date Filing Date
US584398A Expired - Lifetime US3339830A (en) 1966-10-05 1966-10-05 Vacuum operated pump

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US (1) US3339830A (de)
DE (1) DE1653468A1 (de)
ES (1) ES344367A1 (de)
FR (1) FR1553754A (de)
GB (1) GB1192467A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3465735A (en) * 1968-01-08 1969-09-09 F & E Mfg Co Air flow control system for internal combustion engine
US3544239A (en) * 1968-11-25 1970-12-01 George C Graham Vacuum operated compound double-acting piston pump or compressor
US3632233A (en) * 1970-07-09 1972-01-04 George C Graham Fluid pump apparatus and system
EP0107342A2 (de) * 1982-09-29 1984-05-02 General Motors Corporation Pumpeinrichtung
US4459088A (en) * 1982-09-29 1984-07-10 General Motors Corporation Exhaust driven vacuum pump assembly
US4502847A (en) * 1982-09-29 1985-03-05 General Motors Corporation Exhaust gas operated vacuum pump assembly
US4502848A (en) * 1982-09-29 1985-03-05 General Motors Corporation Exhaust gas operated vacuum pump assembly

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5314272A (en) * 1976-07-27 1978-02-08 Nissan Motor Co Ltd Oil pressure generator for vehicles
FR3035527B1 (fr) 2015-04-27 2018-09-21 Commissariat A L'energie Atomique Et Aux Energies Alternatives Vitrage multiple tactile

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1956612A (en) * 1932-03-30 1934-05-01 & D Expl Du Generateur A Pisto Fuel injection pump for internal combustion engines
US2629328A (en) * 1947-09-26 1953-02-24 Floyd R Ladd Pump
US3253775A (en) * 1963-11-29 1966-05-31 Gen Motors Corp Fluid supply system

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1956612A (en) * 1932-03-30 1934-05-01 & D Expl Du Generateur A Pisto Fuel injection pump for internal combustion engines
US2629328A (en) * 1947-09-26 1953-02-24 Floyd R Ladd Pump
US3253775A (en) * 1963-11-29 1966-05-31 Gen Motors Corp Fluid supply system

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3465735A (en) * 1968-01-08 1969-09-09 F & E Mfg Co Air flow control system for internal combustion engine
US3544239A (en) * 1968-11-25 1970-12-01 George C Graham Vacuum operated compound double-acting piston pump or compressor
US3632233A (en) * 1970-07-09 1972-01-04 George C Graham Fluid pump apparatus and system
EP0107342A2 (de) * 1982-09-29 1984-05-02 General Motors Corporation Pumpeinrichtung
US4459088A (en) * 1982-09-29 1984-07-10 General Motors Corporation Exhaust driven vacuum pump assembly
US4502847A (en) * 1982-09-29 1985-03-05 General Motors Corporation Exhaust gas operated vacuum pump assembly
US4502848A (en) * 1982-09-29 1985-03-05 General Motors Corporation Exhaust gas operated vacuum pump assembly
EP0107342A3 (de) * 1982-09-29 1986-02-26 General Motors Corporation Pumpeinrichtung

Also Published As

Publication number Publication date
FR1553754A (de) 1969-01-17
GB1192467A (en) 1970-05-20
ES344367A1 (es) 1968-12-01
DE1653468A1 (de) 1970-07-09

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