EP0532603B1 - A fluid valve device and a positive-displacement pump - Google Patents

A fluid valve device and a positive-displacement pump Download PDF

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Publication number
EP0532603B1
EP0532603B1 EP91910900A EP91910900A EP0532603B1 EP 0532603 B1 EP0532603 B1 EP 0532603B1 EP 91910900 A EP91910900 A EP 91910900A EP 91910900 A EP91910900 A EP 91910900A EP 0532603 B1 EP0532603 B1 EP 0532603B1
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EP
European Patent Office
Prior art keywords
valve
fluid
chamber
valve member
inlet
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
EP91910900A
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German (de)
English (en)
French (fr)
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EP0532603A1 (en
Inventor
Stig Lundbäck
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.)
INOVACOR AB
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INOVACOR AB
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Publication date
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Publication of EP0532603A1 publication Critical patent/EP0532603A1/en
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Publication of EP0532603B1 publication Critical patent/EP0532603B1/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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms

Definitions

  • This invention relates to a fluid valve device for controlling the flow of a fluid and to a positive-displacement pump including such a valve device.
  • the invention relates to a fluid valve device of the kind defined in the precharacterising portion of claim 1 and to a positive-displacement pump of the kind defined in the precharacterising portion of claim 9.
  • valve device Although not limited exclusively to use as an inlet valve in a positive-displacement pump, the valve device according to the invention is particularly useful for such applications. It therefore will be described herein with special reference to its use as an inlet valve in a positive-displacement pump, namely a positive-displacement pump in which a reciprocable displacement member repetitively contracts a pump chamber to expel liquid received in the pump chamber.
  • a positive-displacement pump has a pump chamber which communicates with an inlet and an outlet and includes a movable wall or wall section forming part of or cooperating with the displacement member.
  • An inlet valve controls the flow of fluid into the pump chamber from the inlet by opening and closing a flow passage which opens into the pump chamber.
  • Most positive-displacement pumps also include an outlet valve which prevents backflow of fluid from the outlet into the pump chamber, but in some cases such a valve can be dispensed with.
  • the flow passage through which the fluid being pumped enters the pump chamber often causes a serious limitation of the output and efficiency of the pump.
  • the fluid being pumped enters the inlet and the pump chamber at a relatively low pressure; in many cases the inflow takes place under the action of a partial vacuum in the pump chamber.
  • the inlet valve has to be able to open a flow passage of large cross-section area and of a shape such that the resistance to flow of the fluid is minimized.
  • this requirement is difficult to reconcile with the requirement for small dimensions. This is particularly so in pumps which are to operate at high stroke rates.
  • EP-A-0 374 115 discloses positive-displacement pumps which represent an advantageous solution to the problem of providing for a rapid filling of the pump chamber with small energy losses.
  • An important feature of this solution resides in a gap-like flow passage which extends over the entire circumference, or at least over a substantial portion of the circumference, of the pump chamber and which can be opened over the entire circumferential extent thereof to admit fluid into the pump chamber.
  • variable-volume supply compartment or reservoir is provided adjacent the inlet valve on the upstream side thereof so that a supply of fluid for filling the pump chamber is available very close to the inlet valve; the supply is replenished during the ejection stroke of the pump so as to be available again when the next ejection stroke commences.
  • the flow passage already has a large cross-section area after a short opening movement of the inlet valve, and as the inflow into the pump chamber takes place from all or almost all directions, the flow path is relatively short for most of the fluid that enters the pump chamber.
  • the inlet valve is a mechanical, positively operated valve while in others of the illustrated embodiments a flow-direction controlled non-return valve, namely a flap valve, is used. In certain other embodiments which are not illustrated, the inlet valve is a combination of the two types of valve.
  • a fluid valve device of the kind defined in the precharacterising portion of claim 1 is disclosed in DE-A-2 605 015.
  • a valve member in the form of a diaphragm is maintained in sealing engagement with the valve seat by the pressure existing in the inlet port.
  • the diaphragm is provided with a narrow bleed orifice through which a restricted flow path exists between the inlet port and a valve chamber on the side of the diaphragm which is directed away from the valve seat.
  • the diaphragm is substantially larger than the valve seat and is therefore urged to closed position in engagement with the valve seat by a force which is larger than, and thus prevails over, the oppositely directed force on the other side of the diaphragm which tends to move the diaphragm away from the valve seat.
  • the valve is opened by operation of a pilot valve which responds to a pressure in the inlet port exceeding a set maximum permissible pressure to rapidly depressurise the valve chamber and thereby allow the fluid pressure in the inlet port to force the diaphragm to open position.
  • a positive-displacement pump of the kind defined in the precharacterising portion of claim 9 is shown in DE-C-875 142.
  • the inlet valve comprises a valve member in the form of a diaphragm cooperating with an annular valve seat.
  • the diaphragm which also serves as the displacement member, is operated by a fluid which is independent of the fluid being pumped.
  • Objects of the present invention are to provide fluid valve devices which are useful in positive-displacement pumps, especially positive-displacement pumps of the kind discussed above, and to provide an improved positive-displacement pump.
  • valve device which embodies some of the features of the inlet valves disclosed in EP-A-0 374 115, is neither controlled mechanically by a positively acting valve operating mechanism nor controlled by the direction of the fluid flow through it. Instead, it is controlled by the pressure or the force which the fluid being received by the valve device applies to a valve member that is movable into and out of sealing engagement with a valve seat.
  • the fluid whose pressure controls the displacement of the valve member is received in a valve chamber defined by the valve member and preferably acts on the valve member over a thrust surface located downstream of the flow passage which the valve member opens when it disengages from the valve seat.
  • the fluid valve device shown by way of example in Figs. 1 and 2 comprises a body or housing 11 having an inlet 12 with an associated feed conduit 14 for a fluid, namely a liquid, the passage of which the valve device controls in a two-position or on-off mode (open-closed valve).
  • a vertically extending outlet conduit for the fluid being passed through the valve device is designated by 15.
  • the lower portion 17 of the outlet conduit is flared and has a downwardly facing annular rim 17A which forms a stationary valve seat.
  • a valve chamber 20 in the valve device is defined laterally by a vertically displaceable valve member 21 in the housing 11.
  • the valve member 21 is in the shape of a short length of tube which is constricted at its upper end to form an annular sealing portion 21A adapted to engage and seal against the annular valve seat 17A on the flared lower portion 17 of the outlet conduit 15.
  • valve member 21 The lower end of the valve member 21 is flared and constantly is in sliding sealing engagement with the inner side of a cylindrical, downwardly directed portion 11A of the housing 11.
  • valve member 21 constantly is in sliding sealing engagement with an annular, inwardly directed lip llD of the housing. Between this lip and the flared lower valve member end, the valve member 21 together with the housing portion 11A defines a compartment V which is filled with air and in open communication with the surrounding atmosphere through an opening S. As the valve member 21 moves axially towards and away from the valve seat 17A, the air compartment V accommodates the variations in volume which the valve chamber 20 undergoes.
  • the housing 11 defines a supply compartment or reservoir 22.
  • This compartment or reservoir is open at the top of the housing and holds liquid up to a level which may vary but is here presumed always to be higher than the level of the valve seat 17A. If desired, a water seal (not shown) may be provided on the upstream side of the valve seat.
  • Figs. 1 and 2 show no bottom wall or other downward limitation of the valve chamber 20.
  • a movable bottom wall may be in the form of a pump piston which is movable up and down in the lower housing portion 11A as in the positive-displacement pump described below. It is not necessary, however, for the valve device to include a bottom wall of the valve chamber. What is required is only that the pressure within the valve compartment 20 may be varied in the manner explained below.
  • the liquid pressure in the valve compartment 20 is presumed to be of a value related to the head pressure in the supply compartment or reservoir 22 such that the upwardly directed fluid force applied to the valve member 21 prevails over the downwardly directed fluid force or the sum of the latter and the weight of the valve member (this weight, however, is presumed to be small or fully or almost fully balanced by an Archimedean force and/or a spring force). Consequently, the sealing portion 21A of the valve member 21 is held in sealing engagement with the annular valve seat 17A.
  • the upwardly directed force may result from, for example, the head pressure of a column of liquid in the outlet conduit 17 or a pressure produced by a piston accommodated in the housing portion 11A.
  • the upwardly directed fluid force is applied to the valve member 21 over an annular surface A on the inner side of the valve member.
  • the surface area of this surface A (thrust surface) as projected in the direction of the axis L of the valve device, or, in other words, the surface area which determines, in conjunction with the pressure in the valve chamber 20, the magnitude of the upwardly directed fluid force on the valve member, is determined by the outer diameter D of the valve member and the diameter d of the circular or narrow annular area over which the valve seat 17A is engaged by the sealing portion 21A (for convenience, the radial width of the surface of engagement between the valve seat 17A and the sealing portion 21A of the valve member 21 is disregarded here).
  • the downward fluid force is applied to the valve member 21 over a likewise annular but smaller surface B (thrust surface) on the outer side of the valve member.
  • the surface area of this surface B as projected in the direction of the axis L is determined by the diameter Dd of the cylindrical intermediate portion of the valve member and the above-mentioned diameter d.
  • the air compartment V constantly is in open, unrestricted communication with the surrounding atmosphere and thus is always subjected to the atmospheric pressure. Consequently, the upwardly facing annular surface C on the outer side of the valve member 21 - the axially projected or effective surface area of this surface C is determined by the outer diameter D of the flared lower valve member portion and the outer diameter Dd of the cylindrical intermediate valve member portion - is not acted on by any force tending to displace the valve member upwardly or downwardly.
  • valve chamber 20 When the pressure in the valve chamber 20 drops sufficiently far below the pressure in the supply compartment or reservoir 22, e.g. because a pressure generated by a piston (not shown) in the housing portion 11A disappears and/or the momentum of an upwardly moving liquid column in the outlet conduit 15 tends to produce suction in the valve compartment, a situation develops in which the downward force acting on the valve member 21 prevails and moves the valve member downwardly.
  • annular gap-like flow passage 23 is opened between the valve member 21 and the valve seat 17A, see Fig. 2. Because of the annular configuration of this flow passage 23, the cross-section area the flow passage presents to the liquid flow through it already is substantial after a short downward movement of the valve member. Hence, the liquid in the supply compartment or reservoir 22 can flow into the valve chamber 20 almost unimpededly, that is, without undergoing any significant pressure drop.
  • a following increase of the pressure in the valve chamber 20 with respect to the pressure in the supply compartment or reservoir 22 will cause the upward fluid force acting on the valve member to prevail so that the valve member 21 is returned to the closed position shown in Fig. 1.
  • Such returning of the valve member may take place even before the pressure in the valve chamber 20 exceeds the pressure in the supply compartment or reservoir 22, because the effective (axially projected) surface area of the downwardly facing thrust surface A is larger than the effective (axially projected) surface area of the upwardly facing thrust surface B.
  • Figs. 3-6 which show a positive-displacement piston pump including an inlet valve in the form of a one-way fluid valve device embodying the principles of the invention
  • the reference numerals and letters used in Figs. 1 and 2 are also used to designate pump elements which correspond, in respect of their functions, to the valve elements forming part of the valve device of Figs. 1 and 2.
  • the pump shown by way of example in Figs. 3-6 comprises a rigid, generally circular cylindrical pump housing 11.
  • An inlet opening 12 is provided in the circumferential pump housing wall 11A, and an outlet opening 13 is provided in the top end wall 11C.
  • a radial inlet conduit 14 conveying a substantially continuous stream of liquid opens into the inlet opening 12, and the outlet opening 13, which is located on the vertical axis of the pump housing 11, opens into an upwardly extending axial outlet conduit 15.
  • the pump Inside the pump housing 11 the pump has a sac or bladder 16 of a thin, highly flexible but substantially inextensible film of plastic, such as polyurethane.
  • This sac is sealingly connected with the inlet conduit 14 and, through the intermediary of a flared inlet sleeve 17 attached to the pump housing, with the outlet conduit 15.
  • the sac 16 and the pump housing 11 are designed such that the entire pump, or at least the sac, lends itself to use as a disposable item.
  • its cross-sections taken perpendicularly to the axis L of the pump housing are generally circular or annular.
  • the bottom wall of the sac 16 rests on the top side of a vertically movable displacement member or piston 18 which is caused to reciprocate vertically at a constant or variable rate by a motor 19.
  • the piston may be positively driven in both directions, but in the illustrated embodiment it is positively driven only upwardly through the delivery stroke.
  • the downward movement of the piston results from gravity, i.e. the weight of the piston and the weight of the liquid in the pump chamber 20. A contribution to the downward movement of the piston may also be given by the static or dynamic pressure of the liquid being pumped.
  • the piston does not pull the bottom wall of the sac downwardly during the downward or filling stroke.
  • the lower portion of the sac 16 defines a pump chamber 20 the side wall of which, or at least the upper portion thereof, is configured by a surrounding, substantially rigid, upwardly tapering co11Ar 21 the cross-sections of which taken perpendicularly to the pump axis L are circular.
  • the function of the co11Ar 21, the weight of which is very small is to impart a stable configuration to the side wall of the sac 16 at the upper portion of the pump chamber. This stabilising effect may also be accomplished by other means, e.g. by making the side wall of the sac sufficiently rigid.
  • the co11Ar 21 extends downwardly beyond the top portion of the piston 18, which is arranged such that air can flow freely past the piston into and out of the air compartment V, which is constantly under atmospheric pressure.
  • the co11Ar 21 is freely movable axially within the pump housing 11, that is, it can move up and down together with the adjacent portion of the side wall of the sac 16 without being driven by a positive-acting mechanism; the forces acting on the co11Ar 21 and causing its upward and downward movements are generated by the liquid being pumped, as will be explained in greater detail in conjunction with the description of the operation of the pump.
  • the section of the sac 16 which defines the pump chamber 20 merges, by way of a constriction or waist at the top edge 21A of the co11Ar 21, with a sac section which defines an annular supply compartment or reservoir 22.
  • This reservoir 22 surrounds and is partly defined by the outlet sleeve 17 and communicates with the pump chamber 20 through an annular inlet passage 23 defined between the top edge 21A of the co11Ar 21 and the valve seat 17A at the flared lower end of the sleeve 17.
  • the inlet conduit 14 is constantly in open, unrestricted communication with the reservoir 22 which is expandable by the inflowing liquid.
  • the pressure within the reservoir 22 produced by the thrust ring is very low, however, at least until the reservoir has been substantially expanded and thus has compressed the spring heavily.
  • the inlet passage 23 has a large cross-section area for the inflowing liquid and because its length as measured in the direction of the liquid flow through it, that is, in the radial direction, is very small, it presents an extremely low resistance to the flow of liquid from the inlet opening 12 and the reservoir 22. For that reason, the inflow of liquid into the pump chamber 20 from the reservoir 22 can take place almost entirely independently of the more or less continuous inflow from the inlet opening 12 and the inlet conduit 14. Thus, the inflow from the inlet opening 12 and the inlet conduit 14 is virtually unaffected by the discharging of the reservoir 22.
  • the reservoir 22 can be discharged extremely rapidly, even though the biasing action exerted on the liquid in the reservoir 22 by the thrust plate 24 and the compression spring 25 is not very strong. Factors which contribute to the rapid discharge of the reservoir are:
  • the pump chamber 20 expands, provided that the pump piston 18 is still free to move downwardly.
  • the expansion takes place without any external force tending to pull the bottom wall of the sac 16 downwards and thereby tending to produce a subatmospheric pressure in the pump chamber 20 (but as mentioned, it is within the scope of the invention to provide for such a force to assist in the expansion of the pump chamber).
  • the filling of the pump chamber 20 is governed by the inflow of liquid from the inlet conduit 14 and the reservoir 22.
  • the co11Ar 21 and the constricted upper portion of the side wall 16A of the sac 16 will move upwardly to a position in which they sealingly engage the downwardly facing valve seat 17A on the flared lower portion of the outlet sleeve 17 so that the inlet passage 23 is closed and continued inflow into the pump chamber 20 is prevented. Accordingly, the co11Ar 21 and the associated portion of the sac 16 constitute an inlet valve member for the pump chamber 20.
  • the movement of the co11Ar 21 to the just-mentioned position is governed by the pressure of the liquid in the pump chamber 20 and the pressure in the inlet 12 and the reservoir 22.
  • the pressure of the liquid in the pump chamber 20 applies to the sac 16, and thus to the co11Ar 21, an upwardly directed force over a downwardly facing, axially projected annular thrust surface A on the co11Ar; this annular thrust surface has an outer diameter D and an inner diameter d, see Fig. 3. This force tends to displace the co11Ar 21 upwardly with respect to the pump piston 18.
  • the co11Ar 21 is acted on by, in addition to the fairly small downward force resulting from the weight of the co11Ar, a downward force resulting from the action of the pressure of the liquid in the reservoir 22 on an upwardly facing, axially projected annular thrust surface B of the sac.
  • the inner diameter of the annular thrust surface B is constant and equal to the inner diameter d of the first-mentioned annular thrust surface A, and its outer diameter varies during the movement of the co11Ar 21; as is apparent from a comparison of Fig. 3 and Fig. 4, the outer diameter, and thus the surface area of the annular thrust surface B, is at its maximum when the co11Ar is in its top position (closed valve) and decreases during the downward movement of the co11Ar.
  • the interaction of forces is such that the co11Ar 21 is acted on by a resultant force which maintains the co11Ar in its lowermost position or at any rate at a distance from the valve seat 17A, so that the valve is kept open.
  • the pump should be dimensioned with consideration given to the flow rate of the inflow which it is meant to handle, so that the reservoir 22 can normally accommodate the liquid supplied during the closed phases of the valve without having to expand to near its maximum volume. This prevents the inflow to the pump through the inlet conduit 14 from becoming unduly retarded or even stopped during the discharge or ejection periods when the inlet valve is closed.
  • the flow passage 23 is opened all the way round the pump chamber.
  • Such a continuous flow passage is advantageous, because the maximum cross-section area and an advantageous flow pattern are achieved. It is within the scope of the invention, however, to use a portion of the circumference for a radial outlet from the pump chamber. This outlet may be positioned diametrically opposite to the inlet, but it is also possible to position the inlet and the outlet side by side.
  • valve member in which the fluid is discharged from the pump chamber 20 through a radial outlet and the inlet passage 23 between the valve member 21 and the valve seat 17A thus does not extend all the way round the pump chamber, it may be preferred to mount the valve member such that it can be pivoted about an axis which is in a plane parallel to the plane containing the valve seat and which preferably passes through or near the ends of the inlet passage. In such case, the height of the opened passage will increase gradually from the pivot axis to a maximum at the side of the pump chamber which is diametrically opposite the outlet.
  • the entire fluid force acting on the valve member in the closing direction is applied directly on the valve member
  • the pump piston during its downward movement displaces a fluid volume in the driving device. This displaced fluid volume is used during part of the downward movement of the pump piston, namely toward the completion of the filling of the pump chamber, to cause displacement of a force-transmitting element upwardly and to thereby apply an upward, that is, closing force on the valve member.
  • a biasing force such as a gravity force or a spring force, constantly acting in the closing or in the opening direction on the valve member, so that the valve member always tends to move to a predetermined position, such as the closed position, when the fluid forces which are generated in normal operation are not present.
  • the air compartment V is always under atmospheric pressure, so that the thrust surface C does not contribute to the opening or closing force applied to the valve member.
  • the pressure in the air compartment may be caused to vary over the pumping cycle. This can be accomplished by making the air compartment V a part of the total volume of a fluid system the remaining volume of which is matched with the maximum and minimum volumes of the air compartment V such that the pressure in compartment V varies in a predetermined manner over the pumping cycle and thereby contributes to the fluid forces acting on the valve member in the direction of movement thereof.
  • the thrust surface B facing the valve seat 17A which is provided in the illustrated embodiments and contributes to displacing the valve member in the opening direction, is not indispensable.
  • the diameter of the sealing portion 21A of the valve member 21 may be equal or nearly equal to the diameter which is designated by Dd in the drawings. In such case, the resulting fluid force is determined only by the differential pressure over the thrust surfaces A and C.
  • the positive-displacement pump illustrated by way of example is particularly suitable for use as a blood pump.
  • the inside of the sac 16 and any other surfaces contacted by the blood being pumped should have a lining or coating of human or animal tissue (such as pericardium of swine) so that the surfaces coming into contact with the blood have the best possible compatibility with the blood.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fluid-Driven Valves (AREA)
  • Reciprocating Pumps (AREA)
  • Lift Valve (AREA)
  • Jet Pumps And Other Pumps (AREA)
EP91910900A 1990-06-07 1991-06-07 A fluid valve device and a positive-displacement pump Expired - Lifetime EP0532603B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE9002044A SE9002044L (sv) 1990-06-07 1990-06-07 Fluidventilanordning och foertraengningspump
SE9002044 1990-06-07
PCT/SE1991/000408 WO1991019096A1 (en) 1990-06-07 1991-06-07 A fluid valve device and a positive-displacement pump

Publications (2)

Publication Number Publication Date
EP0532603A1 EP0532603A1 (en) 1993-03-24
EP0532603B1 true EP0532603B1 (en) 1997-11-19

Family

ID=20379709

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91910900A Expired - Lifetime EP0532603B1 (en) 1990-06-07 1991-06-07 A fluid valve device and a positive-displacement pump

Country Status (13)

Country Link
EP (1) EP0532603B1 (ja)
JP (1) JPH05507777A (ja)
AT (1) ATE160427T1 (ja)
AU (1) AU660619B2 (ja)
BR (1) BR9106534A (ja)
CA (1) CA2084681A1 (ja)
DE (1) DE69128246T2 (ja)
DK (1) DK0532603T3 (ja)
ES (1) ES2111568T3 (ja)
PL (1) PL167313B1 (ja)
RU (1) RU2100648C1 (ja)
SE (1) SE9002044L (ja)
WO (1) WO1991019096A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11739846B2 (en) 2020-05-26 2023-08-29 Schwäbische Hüttenwerke Automotive GmbH Separate valve seating

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR879637A (fr) * 1939-07-14 1943-03-01 Perfectionnements aux pompes à mouvement alternatif
DE875142C (de) * 1944-04-22 1953-04-30 Messerschmitt A G Fluessigkeitsfoerdereinrichtung
AU510839B2 (en) * 1975-06-13 1980-07-17 Hickman Engineering & Development Co. Ltd. Diaphram valve
DE2605015A1 (de) * 1976-02-10 1977-08-11 Leinemann Co Flammenfilter Pilotgesteuertes membranventil
GB2226606B (en) * 1988-12-08 1993-05-05 Astra Tech Ab Positive displacement pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11739846B2 (en) 2020-05-26 2023-08-29 Schwäbische Hüttenwerke Automotive GmbH Separate valve seating

Also Published As

Publication number Publication date
ES2111568T3 (es) 1998-03-16
RU2100648C1 (ru) 1997-12-27
ATE160427T1 (de) 1997-12-15
SE9002044D0 (sv) 1990-06-07
BR9106534A (pt) 1993-05-25
DE69128246T2 (de) 1998-06-10
CA2084681A1 (en) 1991-12-08
AU8082491A (en) 1991-12-31
DE69128246D1 (de) 1998-01-02
PL293485A1 (en) 1992-09-07
DK0532603T3 (da) 1998-07-27
EP0532603A1 (en) 1993-03-24
PL167313B1 (pl) 1995-08-31
JPH05507777A (ja) 1993-11-04
AU660619B2 (en) 1995-07-06
SE9002044L (sv) 1992-01-07
WO1991019096A1 (en) 1991-12-12

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