US3829256A - Displacement machine - Google Patents

Displacement machine Download PDF

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Publication number
US3829256A
US3829256A US00312479A US31247972A US3829256A US 3829256 A US3829256 A US 3829256A US 00312479 A US00312479 A US 00312479A US 31247972 A US31247972 A US 31247972A US 3829256 A US3829256 A US 3829256A
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Prior art keywords
displacement
chamber
vanes
sections
vane
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US00312479A
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English (en)
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H Guttinger
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Aginfor AG
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Aginfor AG
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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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/04—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal-axis type

Definitions

  • a displacement device is arranged to carry out a revolving movement and has a respective substantially cylindrical sectorshaped vane located in each of the chamber sections of the displacement chamber.
  • Each of the vanes has longitudinal edges and curved surfaces, each of said vanes, independently of its momentary position and during the course of the revolving movement, contacting by means of said longitudinal edges the planar closure surfaces and at least with one of its curved surfaces the associated cylindrical jacket sector of the associated chamber section along a contact line.
  • the present invention relates to a new and improved construction of displacement machine embodying a displacement compartment or chamber subdivided into at least two series connected consecutively arranged chamber sections, each of which is bounded by a respective outer and inner cylindrical jacket sector as well as by two planar or flat closure surfaces.
  • the displacement machine further comprises substantially cylindrical sector-shaped vanes of a displacement device designed for carrying out a rotatory movement and which vanes are arranged in the chamber sections of the displacement compartment, and further wherein, each of the vanes, independently of its momentary position during the course of the rotatory movement, contacts by means of its longitudinal edges the planar closure surfaces and with at least one of its'curved or domed surfaces the confronting cylindrical jacket section of the associated chamber section along a contact jacket line.
  • Machines withrotatory or circulating displacement devices have, according to a newly employed nomenclature or designation in the art, also been referred to as circular piston machines to express the fact that the displacement device (piston) carries out a rotatory or circulatory movement, that is to say, a movement wherein each point of the displacement device describes a complete circle, and all circles have the same diameter.
  • the rotational piston machines in which the displacement device (or piston) carries out at least a rotational movement which can be superimposed upon a circulatory movement, so that there is produced a type of rolling-off movement of the displacement device in the displacement chamber or compartment.
  • the displacement device In the event that the displacement device is mechanically driven then such type machine functions as a pump; on the other hand if the displacement device is driven by a fluid medium which flows through the machine then, in the broadest sense, it operates as a motor, wherein under this expression there is also tobe understood a throughflow measuring device.
  • Displacement machines similar to the previously mentioned type are known to the art in a number of different constructional variations.
  • so-called spiral pumps and motors
  • the displacement device possesses the form of a spiral with at least one convolution
  • the displacement compartment likewise possesses the form of a spiral, the radial width of which corresponds to the diameter of the circular movement plus the wall thickness of the displacement device.
  • What is particularly disadvantageous with such type spiral pumps is, above all, the extremely difficult manufacturing operations required, because the ideal spiral shape only can be approximately produced with conventional equipment and this approximation does not satisfy the degree of accuracy needed by its operational principle. This also seems to be a reason why the spiral pumps, with very few exceptions, have not previously been widely accepted.
  • the change of the displacement-effective compartment volume contributes to the above-described surge-like operation, that is to say, the medium flowing through the machine is not subjected to any continuous throughput, as such for instance is the case with fluid flow machines.
  • Another important object of the present invention relates to a new and improved construction of displacement machine of the aforementioned general character, in which there are not only overcome the sealing problems between the ends of the displacement device and its vanes and the associated walls of the sections of the displacement compartment, but at the same time there is ensured for a continuous surge-free throughput of the conveyed or taken-up medium, respectively, without having to take into account any limitations with regard to the compressibility of the .medium.
  • the displacement machine of this invention is generally manifested by the features that each of the chamber sections of the displacement chamber or compartment and each of the vanes of the displacement device span in known manner a spanning angle of at least 270, and that a chamber section as well as the vane arranged therein is arranged in rotated or angularly shifted manner, through the 360 complement of the span angle, with regard to the next connected chamber section and its vane.
  • FIGS. 1 and 2 respectively show in markedly schematic illustrations a simple constructional embodiment of displacement machine designed according to the invention with two similar displacement vanes rotating in the same sense and depicted in two respective different movement phases;
  • FIGS. 3 and 4 illustrate an embodiment of displacement machine, similar to the showing of FIGS. 1 and 2, but this time having three similar displacement vanes, likewise showing same in two different movement phases;
  • FIG. 5 illustrates an embodiment of the displacement machine with four similar displacement vanes
  • FIG. 6 illustrates a further embodiment of displacement machine with four displacement vanes, but with a displacement compartment or chamber only divided into two sections;
  • FIG. 7 is an exploded view of a practical exemplary embodiment of displacement machine designed according to the principles of FIGS. 1 and 2.
  • a displacement compartment or chamber subdivided into two sections 10 and 11.
  • Each of the sections 10 and 11 is bounded by a flat or planar floor wall, a flat cover wall (both not illustrated) and by a convex side wall 23 and 24 respectively, each possessing a radius of curvature r and by a concave side wall 22 and 25 respectively, each possessing a radius of curvature R.
  • these side walls possess the form of a cylindrical jacket with axes 27 and 28 respectively disposed perpendicular to the plane of the drawing.
  • the side walls 22 and 23 of the section 10 are coaxially arranged with regard to one another, likewise the-side walls 24 and 25 of the section 11. into one end 12 of the section 10 there opens an inlet opening 13 and from the one end I? n! the rim-tion 11 there merges an outlet opening 18.
  • Both of the rcmaining ends 14 and 16 of the sections 10 and 11 are in flow communication with one another by a throughflow or passage 15.
  • the arrangement of the sections 10 and 11 is mirror-image symmetrical with regard to the plane of symmetry indicated by the line 19.
  • a displacement vane 20 and in section 11 a displacement vane 21.
  • the displacement vanes 20 and 21 each possess the shape of an arc of a cylindrical jacket, which spans an angle of about 270, and if there is neglected the wall thickness, possesses a diameter of R-l-r. As will be apparent from FIGS.
  • both of the displacement vanes 20 and 21 are arranged in offset relationship with one another through an angle of about Both of the displacement vanes 20 and 21 are rigidly connected with one another by any suitable and therefore not particularly illustrated means, for instance a plate which is parallel to the plane of the drawing, and mounted in such a way that they carry out a circular movement in the direction of the arrow 33, wherein the diameter 26 of the rotatory movement (while neglecting the wall thickness of the displacement vane) amounts to Rr.
  • FIG. 2 there is shown a position in which the displacement vanes 20 and 21 have revolved further through about 90 in the counterclockwise direction from the position depicted in FIG. 1.
  • the inner" contact point 29 between the displacement vane 20 and the wall 23 has wandered downward about the axis 27 through an angle of about 90, whereas no contact point exists any longer between the vane 20 and the wall 22. In this case there is therefore realized a direct flow connection between the inlet 13 and the outlet 18.
  • the contact point 31 between the vane 21 and the wall 25 has wandered upwards in the counterclockwise direction through 90 and at the same time there is obtained a new inner contact point 32 between the vane 21 and the wall 24. Consequently, the vnnr 2! in "NW effective in n conveying or driving man ner respectively.
  • FIGS. 3 and 4 A further exemplary embodiment of displacement machine has been illustrated in FIGS. 3 and 4, and which approximately corresponds to that shown in FIGS. 1 and 2 supplemented by the provision of a third displacement vane.
  • a displacement compartment or chamber 36 extending between an inlet 34 and an outlet 35.
  • the displacement compartment 36 is subdivided into three circular ring sector-shaped sections 37, 38 and 39 respectively, each extending through about 270. While the inlet 34 opens into the section 37 and the outlet extends from the end of the section 39, the remaining ends of such sections are connected via throughpassages 40 and 41 with the ends of the central or middle section 38.
  • a respective displacement vane 42, 43 and 44 is arranged in the sections 37, 38 and 39 respectively.
  • the displacement vanes 42 to 44 are connected with one another also by not particularly shown means of any suitable design and mounted so as to be able to carry out a circulatory or revolving movement in the direction of the arrow 45.
  • the geometric conditions concerning the width of the chamber or compartment sections 37, 38 and 39, the radii of curvature of their side walls, and the diameter of the cylinder determined by the displacement vanes 42 to 44 are practically the same as already described in detail in conjunction with the discussion of FIGS. 1 and 2.
  • the displacement vanes likewise cooperate with one another in pairs, namely the displacement vane 42 with the displacement vane 43 and the latter with the displacement vane 44.
  • Each of the displacement vanes 42, 43 and 44 is arranged in angularly offset relationship through about 90 with respect to the neighboring vane.
  • each displacement vane 42, 43 and 44 has both an inner contact point as well as an outer contact point with the walls of the corresponding compartment or chamber section, namely the contact point 46 (inner) and 47 (outer) for the vane 42; contact point 48 (outer) and 49 (inner) for the vane 43 and contact point 50 (outer) and 51 (inner) for the vane 44.
  • all three vanes 42, 43 and 44 are effective in a conveying or driving sense respectively, depending upon the selected mode of operation of the machine, since each vane closes the throughflow or throughpassage in the corresponding chamber or compartment section.
  • FIG. 4 there is illustrated a position in which the displacement vanes 42, 43 and 44 are further angularly shifted or offset in the counterclockwise direction through about with regard to the showing of FIG. 3. Consequently, the inner and outer respective contact points 46, 51 and 47, of the vanes 42 and 44 have wandered further by a corresponding angular magnitude, whereas in the case of the vane 43 there has disappeared the inner contact point 49 and there is only present the outer contact point 48. Consequently, between the throughflow openings or throughpassages 40 and 41 there prevails an unobstructed flow connection via the chamber or compartment section 38, which only remains until the vanes 42 44 have revolved further through an additional 45.
  • FIGS. 3 and 4 to a certain extent can be designated as a series connection of three successive compartment or chamber sections
  • a parallel circuit configuration with the four chamber sections provided for the exemplary embodiment of FIG. 5, wherein in each case two series connected chamber sections in principle correspond to two parallel connected exemplary embodiments of FIGS. 1 and 2.
  • FIG. 5 a chamber section 53 of the compartment, which chamber section is substantially circular ring-sector shaped and extends over about 270 and from an inlet opening 52, which should be imagined as constituting an extension which is perpendicular to the plane of the drawing and extending in the direction of the observer. Fromthis chamber section there extends a further likewise circular ring sector-shaped chamber section 55 which spans about 270 and which, in turn, opens into an outlet 56 which is to be imagined as extending perpendicular to the plane of the drawing but away from the observer instead of towards the observer as above.
  • a further inlet opening 57 which likewise should be imagined as extending perpendicular to the plane of the drawing and towards the observer, a further circular ring sectorshaped chamber section 58 which spans an angle of about 270, and this further circular ring-shaped sector chamber section 58 also opens into an intermediate section 54.
  • Extending from the intermediate section 54 is a fourth chamber section 59 which again has the shape of a circular ring-shaped sector which spans through about 270 and leads to a further outlet 60 which is to be imagined as perpendicular to the plane of the drawing and extending away from the observer.
  • the inlet openings 52 and 57 are in flow communication with one another by a throughpassage (not shown) and lead to the inlet of the machine.
  • the outlets 56, 60 are in flow communication with one another and lead to the outlet of the machine.
  • each of the chamber sections 53, 55, 58 and 59 there is arranged a respective displacement vane 61, 62, 63 and 64.
  • Each of these displacement vanes is of similar design as the displacement: vanes of FIGS. 1 and 2 and FIGS. 3 and 4 respectively, and is angularly rotated or offset with regard to the neighboring vane by 90.
  • the displacement vanes 61-64 are rigidly connected with one another by means of a carrier or support structure which has only been schematically indicated by reference character 65 and mounted in such a way that they conjointly carry out a circulatory or rotatory movement in the direction of the arrow 66 i.e., the counterclockwise direction.
  • the displacement vanes 61 and 64 have the following sealing contact points with the walls of the corresponding chamber sections 53, 55, 58 and 59: the displacement vanes 61 an outer contact point 67 and an inner contact point 68, the displacement vane 62 only an inner contact point 69, the displacement vane 63 both an inner contact point 70 and an outer" contact point 71, and
  • FIGS. 1 to is a throughflow free of pulsation, whether such be as operation as a motor or pump, and specifically without any change in volume, i.e., without any compression and expansion, which renders the disclosed displacement machine especially suitable for operation with liquid media.
  • FIG. 6 there is illustrated an exemplary embodiment of the invention in which four displacement vanes with pairwise similar dimensions work in only two displacement chamber sections 75 and 77.
  • the embodiment depicted in FIG. 6 possesses a displacement chamber 73 leading from an inlet 74 to a chamber section 75 in the form of a circular ring-shaped sector which spans an angle of 270.
  • a connection or throughpassage section 76 merges with the section 75 and with such there again merges a circular ring sector-shaped section 77 which spans an angle of 270, and at which finally merges an outlet 78.
  • All of these displacement vanes 83 86 are circular arc-shaped and span an angle of 270, and wherein those in the chamber section 75 are arranged in angularly offset or shifted relationship by 90 with respect to those in the chamber section 77.
  • the cylinder described by the displacement vanes 83, 85 or so-called inner displacement vanes possesses a diameter of 2r (R r)/2 (the wall thickness being considered to be negligible), the cylinder of the displacement vanes 84 and 86 or the outer displacement vanes a diameter of 2R (R r)/2.
  • the axes of the cylinder of the inner displacement vanes 83 and 85 are designated by reference characters 88' and 90 respectively, those of the outer displacement vanes by 87 and 89 respectively.
  • the arrangement is designed such that between the axes 87 and 88 as well as between the axes 89 and 90 there appears a respective distance or spacing of (R r)/2.
  • both of the displacement vanes and 86 in the chamber section 77 possess the following contact points: the vanes 85 and 86 contact one another at location 94, the larger outer vane 86 additionally contacts the concave side wall 82 at location 95, and the inner vane 85 contacts the convex side wall 81 at location 96.
  • the intermediate section 86 and the outlet 78 in the illustrated position, there is not present any unobstructed flow communication.
  • each of the chamber sections three displacement vanes, an inner, a central, and an outer vane respectively, wherein then the axes of the cylinder formed by the three vanes should be arranged through the corners of .an equilateral triangle with a side length of /2 3 (R r)3, whereas the revolving movement further possesses a diameter of (R r)/3 and the three displacement vanes revolve in the same sense, however with a phase displacement of or one-third of a revolution.
  • FIG. 7 The exemplary embodiment depicted in FIG. 7 in exploded view, as concerns its mode of operation, corresponds to that of FIGS. 1 and 2. Therefore, it can be imagined that the embodiment of FIG. 7 has been realized from that of FIGS. 1 and 2 in that the embodiment of FIGS. 1 and 2 is divided along the line 19 into two halves and both thus resulting halves are displaced without rotation over one another until the chamber sections 10 and 11 are located coaxially above one another.
  • FIG. 7 The embodiment depicted in FIG. 7 will be seen to comprise two housing halves 108 and 101 which sealing engage one another at the sealing surfaces 102 and 103. Both of the housing havles 100 and 101 enclose a displacement compartment or chamber within which revolves a one-piece displacement member 104 which purely for the sake of the illustration has been depicted in three parts.
  • the upper housing half 101 is designed to be practically the mirror symmetrical image of the lower housing half 100, and in the assembled condition is angularly shifted through 90 with respect to such and threaded thereon by means of bolts 105. It is therefore sufficient if only the lower housing half 100 is described, even if such only encompasses one-half of the displacement compartment or chamber.
  • Leading into the displacement compartment is initially an inlet 106 which opens into a circular sector-shaped chamber section 107.
  • the upper edge 108 of this chamber section 107 is located at a planar or flat sealing surface 109 which is rearwardly offset with respect to the sealing edge 102, as shown.
  • the displacement member or device 104 is constructed as a one-piece member and is only illustrated in its exploded condition in FIG. 7 for facilitating understanding. It possesses a first displacement vane 111, the height of which exactly corresponds to the depth of the chamber section 107 and is secured to the flat underside or bottom face of a first closure plate 112. In the mounted condition this flat underside sealingly bears upon the sealing surface 109.
  • the closure plate 112 possesses a continuous bore or port 113, which in the mounted condition of the arrangement comes to bear upon the end region 110 of the chamber section 107.
  • recesses 114 in the form of a quarter of a circle which, in the mounted condition, together with the bolts 105, ensure a guiding action for the displacement member or device 104 for its rotatory or revolving movement.
  • This closure plate 117 is constructed practically identical to the closure plate 114 and is only mounted in angularly shifted or rotated position through 90 relative thereto.
  • a second displacement vane 119 is mounted upon a flat top surface or face of the closure plate 117, the displacement vane 119 being identical to the displacement vane 111 but mounted in angularly offset relationship through 90 with respect thereto.
  • the upper housing half 101 is mirror-image symmetrical to the lower housing half 100 and is shifted angularly with regard thereto through an angle of 90 the displacement vane 119 is effective at the upper housing half at the displacement chamber section.
  • crankshaft 122 offset once in its lengthwise direction, as shown, extends through the components of the assembled machine, namely through the continuous central bore 120 and the lower housing half 100, through the bore 116 of the displacement device 104 and through the continuous central bore 121 of the upper housing half, then the following will be recognized:
  • the machine possesses two circular ring sector-shaped displacement chamber sections (each at the upper and the I lower housing half) which extend through about 270.
  • the chamber sections In the chamber sections there revolves a respective displacement vane which is of circular sector-shaped and spans an angle of 270.
  • the chamber sections and the displacement vanes are angularly offset through about with respect to one another.
  • FIG. 7 The embodiment illustrated by way of example in FIG. 7 can be referred to as a two storey or two tier arrangement and offers the advantage that both displacement vanes 111, 119 can be practically directly driven from one and the same crankshaft.
  • FIGS. 1 and 2 Just as it was possible to modify the basic construction of FIGS. 1 and 2 to attain the practical exemplary embodiment of FIG. 7, it is also possible to modify the exemplary embodiments of FIGS. 3 and 4 into a three tier arrangement and that of FIG. 5 into a four tier arrangement each having only one crankshaft.
  • a displacement machine comprising: a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections, each of said chamber sections being bounded by an outer and inner substantially cylindrical jacket sector and by two substantially planar closure surfaces, a displacevment device arranged for carrying out a revolving movement and having a respective substantially cylindrical sector-shaped vane located in each of the chamber sections of the displacement chamber, each of said vanes having longitudinal edges.
  • each of said vanes independently of its momentary position during the course of said revolving movement, contacting by means of said longitudinal edges said planar closure surfaces and at least with one of its curved surfaces of the associated cylindrical jacket sector of the associated chamber section along a contact line, each of the chamber sections of the displacement chamber and each of the vanes of the displacement device spanning an angle of at least 270, a chamber section and the therein arranged vane being angularly shifted with respect to the connected chamber section and its respective vane by the complement of the span angle for 360, means for dividing said displacement chamber into four sections, and a common intermediate section for parallel connecting in pairs said four sections.
  • a displacement machine comprising: a displacement chamber subdivided into at least two series connected consecutively arranged chamber sections, each of said chamber sections including an inlet and an outlet end, connecting passage means for connecting the outlet end of one chamber section with the inlet end of the other chamber section, each of said chamber sections being bounded by an outer and an inner substantially cylindrical jacket sector and by two substantially planar closure surfaces, a displacement device arranged for carrying out a unidirectional revolving movement and having a respective substantially cylindrical sector-shaped vane located in each of the chamber sections of the displacement chamber with the displacement of each vane being confined to its associated chamber, each of said vanes having longitudinal edges and curved surfaces, each of said vanes, independently of its momentary position during the course of said unidirectional revolving movement, contacting by means of said longitudinal edges said planar closure surfaces and at least with one of its curved surfaces the associated cylindrical jacket sector of the associated chamber section along a contact line, each of the chamber sections of the displacement chamber and each of the vanes of the displacement device spanning an angle of at least
  • vanes constitute vane pairs which are substantially identical to one another.
  • each of the chamber sections of the displacement chamber there is arranged a number of said vanes, wherein the vanes in two successive sections pairwise correspond to one another with respect to their dimensions and wherein the diameter of the revolving movement corresponds to the inner width of the chamber section divided by the number of vanes per section, and wherein the displacement vanes with a phase displacement of 2 7T divided by the number of vanes per section revolve in the same sense.
  • vanes constitute vane pairs which are substantially identical to one another, and wherein there are provided three of said vanes, each of which spans an angle of about 270, and each of which is arranged in a respective one of three consecutively arranged chamber sections of the displacement compartment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Measuring Volume Flow (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Epoxy Compounds (AREA)
  • Rotary Pumps (AREA)
US00312479A 1971-12-10 1972-12-06 Displacement machine Expired - Lifetime US3829256A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1808271A CH561842A5 (xx) 1971-12-10 1971-12-10

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US3829256A true US3829256A (en) 1974-08-13

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US00312479A Expired - Lifetime US3829256A (en) 1971-12-10 1972-12-06 Displacement machine

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US (1) US3829256A (xx)
JP (1) JPS572910B2 (xx)
AT (1) AT314358B (xx)
AU (1) AU460223B2 (xx)
CA (1) CA969028A (xx)
CH (1) CH561842A5 (xx)
CS (1) CS185614B2 (xx)
DE (1) DE2230773B2 (xx)
DK (1) DK135641B (xx)
ES (1) ES409449A1 (xx)
FR (1) FR2164247A5 (xx)
GB (1) GB1380760A (xx)
HU (1) HU173554B (xx)
IT (1) IT971039B (xx)
NL (1) NL7215337A (xx)
NO (1) NO136548C (xx)
SE (1) SE388462B (xx)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5299922A (en) * 1992-12-01 1994-04-05 The United States Of America As Represented By The Secretary Of The Navy Positive displacement rotary pump
US20070036666A1 (en) * 2004-07-09 2007-02-15 Daikin Industries, Ltd. Rotary fluid machine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3671503D1 (de) * 1985-02-27 1990-06-28 Gutag Innovations Ag Verdraengermaschine, insbesondere -pumpe.
CH667497A5 (de) * 1985-04-26 1988-10-14 Bbc Brown Boveri & Cie Rotationskolben-verdraengungsarbeitsmaschine.
DE3719950A1 (de) * 1987-06-15 1989-01-05 Agintec Ag Verdraengermaschine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5299922A (en) * 1992-12-01 1994-04-05 The United States Of America As Represented By The Secretary Of The Navy Positive displacement rotary pump
US20070036666A1 (en) * 2004-07-09 2007-02-15 Daikin Industries, Ltd. Rotary fluid machine
US7534100B2 (en) * 2004-07-09 2009-05-19 Daikin Industries, Ltd. Rotary fluid machine

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Publication number Publication date
SE388462B (sv) 1976-10-04
AU460223B2 (en) 1975-04-24
GB1380760A (en) 1975-01-15
JPS4866207A (xx) 1973-09-11
DK135641C (xx) 1977-12-12
NL7215337A (xx) 1973-06-13
ES409449A1 (es) 1976-03-16
FR2164247A5 (xx) 1973-07-27
DE2230773A1 (de) 1973-06-20
IT971039B (it) 1974-04-30
DK135641B (da) 1977-05-31
CA969028A (en) 1975-06-10
CH561842A5 (xx) 1975-05-15
AU4987472A (en) 1974-06-27
JPS572910B2 (xx) 1982-01-19
DE2230773B2 (de) 1976-04-08
HU173554B (hu) 1979-06-28
NO136548C (no) 1977-09-21
CS185614B2 (en) 1978-10-31
NO136548B (xx) 1977-06-13
AT314358B (de) 1974-04-10

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