+

WO1998003794A1 - Ensemble rotatif - Google Patents

Ensemble rotatif Download PDF

Info

Publication number
WO1998003794A1
WO1998003794A1 PCT/HU1997/000039 HU9700039W WO9803794A1 WO 1998003794 A1 WO1998003794 A1 WO 1998003794A1 HU 9700039 W HU9700039 W HU 9700039W WO 9803794 A1 WO9803794 A1 WO 9803794A1
Authority
WO
WIPO (PCT)
Prior art keywords
cavity
die
shaft
vane
curved surface
Prior art date
Application number
PCT/HU1997/000039
Other languages
English (en)
Other versions
WO1998003794B1 (fr
Inventor
Ferenc ADORJÁN
Original Assignee
Adorjan Ferenc
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 Adorjan Ferenc filed Critical Adorjan Ferenc
Priority to AU36313/97A priority Critical patent/AU3631397A/en
Publication of WO1998003794A1 publication Critical patent/WO1998003794A1/fr
Publication of WO1998003794B1 publication Critical patent/WO1998003794B1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger

Definitions

  • a further limitation for such pumps is that in case of opeiating with mcompiessible fluids the volume m the slots of the shaft between 01 behmd the vanes (sp ⁇ ng space) changes during the operation of the assembly which requues passageways 01 loose fitting of the vanes into the slots, which dete ⁇ orates die volumet ⁇ c effic ⁇ enc * All such kind of pumps generate a oie or less oscillating fluid flow diat oscillation can onh be lowered by inci easing the number of vanes that causes friction penalty
  • the current invention is aiming at eliminating the above described shortcomings of the known sliding vane rotaiy assembhes by introducing such a general geometrical solution that ensures the reliable close contact between the vane and the internal surface of the cavity regardless of die rotational speed and widiout creating substantial friction forces.
  • die proposed equipment produces (or in case of a hydraulic motor, it requires) oscillation free fluid flow with constant rotational speed of its shaft.
  • the solution proposed in the cu ⁇ ent invention is based on the geometrical discernment that the locus of die endpoints of a straight section which rotates 180 degrees in the plane around a fixed pomt such a way diat said pomt stays on die section widiout bemg fixed to any given point of the section, obviously exists and can easily be created Any plane curve that has been
  • wheie 2c is the length of the coids which he on the coid centre (the angle is measured m ladians) It is obvious that any of such closed curves can freely be defined within an angle range of ⁇ e[0, ⁇ "] and die ot ei half of the curve comes fiom the above equation This option allows
  • the rotary assembly consisting of a housing with a cavity that is bounded by the first and die second planar walls, as well as by a
  • the rotatably mounted shaft with an axis perpendicular to the planes of planar walls, fiirnished by a slot parallel and symmetrical to the axis of the shaft and limited to die section of die shaft inside the parallel walls of the cavity; with one or more vanes fitted into the slot which divide the cavity into two or more sub-sections, - is designed such a way that the end surfaces of the vane (vanes) toward the curved surface of the cavity follow rounded curves in cross section parallel to die pianai walls of the cavity, while in any such cross section of die curved surface of the cavity follows a non-circular curve, having a primary internal fitting point which lies on die rotational axis of the shaft and this non-circular cui"ve is dete ⁇ nined such a way that die rounded end surfaces of the vane are in fluid-tight contact along two opposite generatrices with the curved surface of the cavity regardless the ang
  • a fuithei twin cavity a ⁇ angemeut is chaiacte ⁇ sed with identical cavities, with vanes in diem peipeiidiculai to each othei in piojectiou to a plane peipendiculai to the shaft axis and the mlets of the cavities divide fiom a common inlet, as well as the outlets of the cavities meige mto a common outlet
  • the outlet of the first cavity m its housmg is connected to the inlet of the second cavity and theie is a movable valve body in the connecting channel that opeiates m a synchionised way with the single shaft or the shafts that
  • the invention exhibits seveial advantageous featuies Peihaps the most significant such featui e is that it is possible to ci eate a pump from it that is applicable foi carrying gaseous, hquid or mixed fluids and which is chaiacte ⁇ sed by high volumet ⁇ c efficiency, high head, low energy loss tlirough friction between the cavity wall and the vane, which not only improves its energy efficiency but also mci eases the lifetime of the assembly
  • the same 01 a similar assembly can also be applied as a hydiauhc motor having analogous beneficial quahties
  • the sum of the volumetric flow rate of the two chambers will be constant (oscillation free) if the shape of the internal cavities are deteraiined suitably. This is a characteristic case of satisfying an extra condition by designing the shape of the internal cavity.
  • Figure 1 Side view cioss section of a basic arrangement of the rotary assembly
  • Fig 1 shows a generic a ⁇ angement of the rotary assembly with its housmg 10, its first pianai wall 1 1 and its specially curved surface 13 enclosing the cavity 13a
  • the position of die shaft 20 within the cavity 13a of the housmg 10 is well shown
  • the slot 22 traversmg the shaft 20 holds the (m this
  • the surface of the shaft 20 and the curved surface 13 of die housing 10 has connecting generatrices at the point 13e. Along these generatrices which are
  • Fig. 1 diat die inlet 14 and the outlet 15 openings are situated on the two sides of the connecting generatrix 13e of the surface 13 and the surface of the shaft 20.
  • the inlet 14 and the outlet 15 openings extend down to the zenith 13f and nadir 13g generatrices of die curved surface 13. respectively. These generatrices are defined by the touching lines between the vane 30 and the surface 1 when the vane 30 is in upright position (perpendicular to the plain dete ⁇ nined by the axis 1 and generatrix 13e). Should die inlet 14 and the outlet openings extend further than the generatrices 13f and 13g, die full separation of the input and the output
  • the extension of the inlet 14 and outlet 15 openings to die zenith 13f and the nadir 13g generatrices is a necerney requirement.
  • the inlet 14 and outlet 1 openings have to be created such a way that the curved surface 13 of the housing 10 should go continuously around die openings to control the motion of the vane while the shaft 20 rotates around.
  • the inlet 14 and outlet 15 openings can be designed partially or fully on the planar walls 1 1,12 of the housing by taking into account die above described limitations.
  • Fig 3 shows in an eulaiged scale how the bounding curve 13b can be derived from the equicoid curve 133 when the end surfaces 31,32 of the vane 30 are circular arches in cross section with ladius R This de ⁇ vation is necüy.
  • vane 30 in the cavity 13a and the vane 301 in the cavity 13 1a aie also identical and they are fitted into the slots of the same shaft 20. It is important that in perpendicular projection in the
  • the inlet 14 and the outlet 1 openings of the cavities 13a and 13 1 a may extend partly or fully over the planar walls 1 1.12 and 12a of die cavities assuming that they do not exteud over die plain determined by the zenith 13f and the nadir 13g generatrices.
  • the curved surfaces of the cavities of the twin assembly can be chosen such a way that when the assembly is applied as a pump with some incompressible fluid, then the volume of the displaced fluid will be strictly proportional to rotational angle of the
  • the buffer volume 73 may be connected to any point in the circuit and it is required only
  • Fig. 8 presents a hydrauhc circuitry containing three twin chamber rotary assemblies;: one 71 working in pump mode and die odier two 72, 72a working in motor mode.
  • the high pressure line 76 branches symmetrically into the lines 76a and 76b, which lead to the inlets of the
  • hydrauhc motors 72 and 72a The outlets of die motors 72 and 72a merge into the low pressure line 77, connected to the inlet of the pump 71.
  • the torque produced on die shafts of the two driven motors 72.72a is equal to each other and is proportional to the pressure difference between the high pressure 76 and die low pressure 77 lines.
  • the sum of the rotations of the shafts of the two driven motors 72,72a is proportional to the rotations of the driving pump 71. In summaiy, the behaviour of this cucuit very well corresponds to die classical planetary gear differential driving mechanism.
  • valve 81 The function of this valve is to balance the flow difference between the branches 76a and 76b through a negative feedback. (The details of such a valve do not belong to this invention.)
  • the advantage of applying such a flow balancing valve 81 is that it solves die inherent shortcoming of the mechanical differential drives, the twirling that occurs when the
  • the flow balancing valve tends to decrease the flow rate in the branch passing a higher volumetric flow (and as a result decreasmg the torque on the shaft of that motor) while increases the flow rate in the other branch, causing a higher torque on the shaft of the motor on this side.
  • a further feature of this kind of hydrauhc differential drive is that - in contrary to the traditional mechanical drives - it causes no trouble at all to drive more than two motors in differential mode by creating multiple branches. If a circuit with stepwise binary branching is apphed, the flow balancing valve can also be applied. Such a driving mechanism could especially be advantageous for vehicles designed for heavy terrain with four or more driven wheels.
  • a multiple stage torque converter is obtained which is well suitable for automatic control.
  • a scheme is shown in Fig. 9. containmg three driving side pumps, 71, 71a and 71b.
  • the common shaft 91 of the pumps can be driven e.g. by an internal combustion engine.
  • the driven side as shown in Fig. 9 is a differential driving circuit - corresponding to Fig. 8 - diough it could be any .sub-circuitry containmg some hydraulic motors.
  • the transmission ratio between die shafts of the driving and the driven side can be changed in this hydraulic circuit by using the routing valves 74b, 74c, and 74d. When all the three routing valves are in idling state (as the state of the valve 74c in Fig. 9), then die whole transmission circuit is in idle (neutral) state. When the pump having the smallest
  • the transmission provides the highest transmission ratio, analogue to the lowest gear with mechanical transmissions.
  • this pump switched off and the pump next in volume (e.g. pump 71a) is switched on simultaneously, men die second transmission ratio can be set.
  • the next transmission ratio can be obtained for example keeping the pump 71a on and switching on the pump 71b, as well.
  • the number of different transmission ratios of such a circuit depends on the number of pumps in the circuit and the relative volume ratios of the pumps.
  • the volume ratios are well chosen then with two pumps (71, 71a) three transmission ratios can be obtained, widi diree pumps (71. 71 a, and 71 b) seven and with four pumps 16 different ratios can be obtained.
  • the transmission can have one reverse and six forward stages.
  • FIGs 10 and 1 1 the principle and the operation of an internal combustion engine is presented.
  • the construction shown here consists of two rotary assembhes; both are analogue to one shown in Fig. 1. and are situated in the housings 10 and 100, respectively.
  • the assembly in the housing 100 with its shaft 201, vane 301. and its cavity 131a serves as the combu ⁇ ion
  • valve body 40 which is movably mounted to the housing 10 and/or the housing 100. It seems advantageous if this valve body has a disc like shape.
  • the shafts 20 and 201. as well as the shaft of the valve 40 should rotate exactly at the same speed, keeping their relative rotational angles fixed. These relative angles has to be determined such a way that right after the moment when the edge of the vane 301 of die combustion chamber 13 1 a has left the rim of the connecting passageway 18, die opening 41 of the valve body 40 opens to let dirough the compressed air fiom die cavity 13.a toward die expanding volume of the combustion cavity 13 1a.
  • die vane 30 in die housmg 10 is approaching the rim of the outlet opening 17, but it does uot reach it yet.
  • Fig. 10 represents this position of the vanes 30. 301 and the valve 40.
  • the fuel injection nozzle injects the necessary amount of fuel into the combustion chamber 1 l a.
  • the edge of the vane 30 would pass the rim the outlet
  • valve body 40 closes the passageway 18, confining the compre ⁇ ed air-fuel rnixture in die cavity 131a and die ignition device 60 ignites the mixture upon this moment, starting the expansion, working phase. Aiound this time inside the other end of the vane 30 in die compression chamber 13a confines a new volume of ah' and starts compressing it; while simultaneously on the odier side of die vane toward the inlet opening 14 a new sucking phase is
  • the necày lubrication of the moving parts of the engine can be solved preferably by pressiu the lubricant through appropriate axial passageways within the shafts 20 and 201 toward the long edges of the vanes, which will distribute the lubricant with dieir movement within the
  • the shafts 20 and 201 can be created as a single piece. This form is in fact a more preferred embodiment, though it is more difficult to present in a drawing.
  • the passage channel 18 can be manufactured into the planar separating walls between the two chambers, and the disc-like valve body 40 could be mounted on the common shaft, as well.
  • This construction offers several advantages over the one shown in Figures 10 and 1 1 : no synchronisation equipment is required between the .shafts 20 and 201.
  • the valve body 40 can either be mounted on the common shaft or its driving gearing is
  • chambers allow a great degree of freedom to optimise the expansion characteristics of the engine corresponding to virtually any kind of fuel.
  • the rotary assembly according to this invention can be well applied whenever high performance positive displacement pumps or hydraulic motors are required or pulsation free

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Spinning Or Twisting Of Yarns (AREA)

Abstract

Ensemble rotatif comprenant une enveloppe (10) dotée d'une cavité (13a) qui est délimitée par des première et seconde parois planes (11, 12) ainsi que par une surface intermédiaire fermée et incurvée (13), des orifices d'entrée (14) et de sortie (15) débouchant dans la cavité. Un arbre monté rotatif (20) et présentant un axe perpendiculaire aux plans des parois planes est pourvu d'une fente (22) parallèle à l'axe de l'arbre et symétrique par rapport à cet axe, cette fente étant circonscrite à l'intérieur de la section de l'arbre, en-deçà des parois parallèles de la cavité. Une ou plusieurs ailettes (30) s'adaptant dans la fente divisent la cavité en au moins deux sous-sections.
PCT/HU1997/000039 1996-07-19 1997-07-17 Ensemble rotatif WO1998003794A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU36313/97A AU3631397A (en) 1996-07-19 1997-07-17 Rotary assembly

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HU9601972A HUP9601972A3 (en) 1996-07-19 1996-07-19 Rotary machine
HUP9601972 1996-07-19

Publications (2)

Publication Number Publication Date
WO1998003794A1 true WO1998003794A1 (fr) 1998-01-29
WO1998003794B1 WO1998003794B1 (fr) 1998-03-05

Family

ID=89994139

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/HU1997/000039 WO1998003794A1 (fr) 1996-07-19 1997-07-17 Ensemble rotatif

Country Status (3)

Country Link
AU (1) AU3631397A (fr)
HU (1) HUP9601972A3 (fr)
WO (1) WO1998003794A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1454755A1 (fr) * 2003-03-05 2004-09-08 Brother Kogyo Kabushiki Kaisha Pompe et imprimante à jet d'encre
EP1518693A1 (fr) * 2003-09-25 2005-03-30 Brother Kogyo Kabushiki Kaisha Appareil d'enregistrement à jet d'encre avec pompe, méthode de commande d'un appareil d'enregistrement à jet d'encre et méthode de commande de la pompe
DE102005051875A1 (de) * 2005-10-29 2007-05-24 Zf Lenksysteme Gmbh Flügelzellenmaschine
WO2007003887A3 (fr) * 2005-06-30 2007-05-31 Ea Technical Services Ltd Machines a piston orbiteur
WO2007063569A1 (fr) * 2005-12-01 2007-06-07 Italo Contiero Machine volumetrique rotative a pales
US7360878B2 (en) 2003-10-31 2008-04-22 Brother Kogyo Kabushiki Kaisha Inkjet printer and method of controlling the inkjet printer
ITRN20090010A1 (it) * 2009-03-06 2010-09-07 Leonardo Battistelli Macchina di incremento di volume

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR552920A (fr) * 1922-05-09 1923-05-09 Perfectionnements aux pompes à palettes
GB1139438A (en) * 1965-10-08 1969-01-08 Gen Electric Improvements in rotary-piston engines
FR2353729A1 (fr) * 1975-11-28 1977-12-30 Bepex Corp Pompe a palettes
DE3610703A1 (de) * 1986-03-29 1986-08-21 Herbert 8084 Inning Klausnitzer Scheibenlaeufermotor
US5006053A (en) 1987-03-12 1991-04-09 Seno Cornelio L Vertical single blade rotary pump
DE4031468A1 (de) * 1989-10-07 1991-04-18 Barmag Barmer Maschf Fluegelzellenpumpe
DE4229999A1 (de) * 1992-09-08 1994-03-10 Bruns Hans Hermann Rotationskolbenmotor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR552920A (fr) * 1922-05-09 1923-05-09 Perfectionnements aux pompes à palettes
GB1139438A (en) * 1965-10-08 1969-01-08 Gen Electric Improvements in rotary-piston engines
FR2353729A1 (fr) * 1975-11-28 1977-12-30 Bepex Corp Pompe a palettes
DE3610703A1 (de) * 1986-03-29 1986-08-21 Herbert 8084 Inning Klausnitzer Scheibenlaeufermotor
US5006053A (en) 1987-03-12 1991-04-09 Seno Cornelio L Vertical single blade rotary pump
DE4031468A1 (de) * 1989-10-07 1991-04-18 Barmag Barmer Maschf Fluegelzellenpumpe
DE4229999A1 (de) * 1992-09-08 1994-03-10 Bruns Hans Hermann Rotationskolbenmotor

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1454755A1 (fr) * 2003-03-05 2004-09-08 Brother Kogyo Kabushiki Kaisha Pompe et imprimante à jet d'encre
US7588432B2 (en) 2003-03-05 2009-09-15 Brother Kogyo Kabushiki Kaisha Pump and inkjet printer
EP1518693A1 (fr) * 2003-09-25 2005-03-30 Brother Kogyo Kabushiki Kaisha Appareil d'enregistrement à jet d'encre avec pompe, méthode de commande d'un appareil d'enregistrement à jet d'encre et méthode de commande de la pompe
US7322682B2 (en) 2003-09-25 2008-01-29 Brother Kogyo Kabushiki Kaisha Ink-jet recording apparatus including pump, method for controlling the ink-jet recording apparatus and method for controlling the pump
US7628479B2 (en) 2003-09-25 2009-12-08 Brother Kogyo Kabushiki Kaisha Ink-jet recording apparatus including pump, method for controlling the ink-jet recording apparatus, and method for controlling the pump
US7360878B2 (en) 2003-10-31 2008-04-22 Brother Kogyo Kabushiki Kaisha Inkjet printer and method of controlling the inkjet printer
US7393090B2 (en) 2003-10-31 2008-07-01 Brother Kogyo Kabushiki Kaisha Inkjet printer and method of controlling the inkjet printer
WO2007003887A3 (fr) * 2005-06-30 2007-05-31 Ea Technical Services Ltd Machines a piston orbiteur
DE102005051875A1 (de) * 2005-10-29 2007-05-24 Zf Lenksysteme Gmbh Flügelzellenmaschine
WO2007063569A1 (fr) * 2005-12-01 2007-06-07 Italo Contiero Machine volumetrique rotative a pales
ITRN20090010A1 (it) * 2009-03-06 2010-09-07 Leonardo Battistelli Macchina di incremento di volume

Also Published As

Publication number Publication date
HUP9601972A2 (hu) 1998-04-28
HUP9601972A3 (en) 1999-12-28
HU9601972D0 (en) 1996-09-30
AU3631397A (en) 1998-02-10

Similar Documents

Publication Publication Date Title
US6659744B1 (en) Rotary two axis expansible chamber pump with pivotal link
US3996901A (en) Rotary piston mechanism
US5171142A (en) Rotary displacement machine with cylindrical pretension on disc-shaped partition
US6401686B1 (en) Apparatus using oscillating rotating pistons
KR101177594B1 (ko) 가변 커패시티 제로터 펌프
CA2467479A1 (fr) Moteur rotatif equilibre a combustion interne ou machine volumique a fonctionnement cyclique
WO1998003794A1 (fr) Ensemble rotatif
US4111617A (en) Rotary piston mechanism
US3877850A (en) Spherical power device
US5501182A (en) Peristaltic vane device for engines and pumps
US5992371A (en) Rotary piston machine usable particularly as a thermal engine
US20030192503A1 (en) Rotary machine
US3876348A (en) Rotary engine converter
US5944499A (en) Rotor-type pump having a communication passage interconnecting working-fluid chambers
CA2162678A1 (fr) Systeme rotatif de transmission mecanique a palettes
US3954355A (en) Rotary energy converter
US4552107A (en) Rotary internal combustion engine
CA2300812C (fr) Machine a piston rotatif
FR2720788B1 (fr) Machine volumétrique réversible à piston(s) rotatif(s) sans clapet à usage de compresseur de fluide de moteur et de pompe à fluide.
US4759324A (en) Intake system for rotary piston engine
US4136647A (en) Rotary device particularly useful as a rotary engine
EP1133640A1 (fr) Pompe rotative
US3890941A (en) Rotary energy converter
KR100536468B1 (ko) 로터리엔진
CA1108009A (fr) Mecanisme tournant a aubes axiales

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AU CA CH CZ IL JP KR NO PL RO SI SK US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
CFP Corrected version of a pamphlet front page

Free format text: REVISED ABSTRACT RECEIVED BY THE INTERNATIONAL BUREAU AFTER COMPLETION OF THE TECHNICAL PREPARATIONS FOR INTERNATIONAL PUBLICATION

NENP Non-entry into the national phase

Ref country code: CA

NENP Non-entry into the national phase

Ref country code: JP

Ref document number: 1998506726

Format of ref document f/p: F

122 Ep: pct application non-entry in european phase
点击 这是indexloc提供的php浏览器服务，不要输入任何密码和下载