EP3470177A1 - Dispositif de montage pour un assemblage vissé et procédé de serrage d'un assemblage vissé - Google Patents

Dispositif de montage pour un assemblage vissé et procédé de serrage d'un assemblage vissé Download PDF

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Publication number
EP3470177A1
EP3470177A1 EP17195854.9A EP17195854A EP3470177A1 EP 3470177 A1 EP3470177 A1 EP 3470177A1 EP 17195854 A EP17195854 A EP 17195854A EP 3470177 A1 EP3470177 A1 EP 3470177A1
Authority
EP
European Patent Office
Prior art keywords
rotary ring
sleeve
threaded
threaded bolt
mounting device
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.)
Withdrawn
Application number
EP17195854.9A
Other languages
German (de)
English (en)
Inventor
Nicolas Lagas
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.)
Sulzer Management AG
Original Assignee
Sulzer Management AG
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 Sulzer Management AG filed Critical Sulzer Management AG
Priority to EP17195854.9A priority Critical patent/EP3470177A1/fr
Priority to PCT/EP2018/077426 priority patent/WO2019072817A1/fr
Publication of EP3470177A1 publication Critical patent/EP3470177A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B29/00—Accessories
    • B25B29/02—Bolt tensioners

Definitions

  • the invention relates to a mounting device for a screw and a method for tightening a screw according to the preamble of the independent claim of the respective category.
  • Screw connections are very often used to connect two components in a detachable manner with each other.
  • pumps for industrial purposes are mentioned here, in particular centrifugal pumps of the type used in the energy-producing industry, in the water industry or also in the oil and gas industry.
  • Such pumps usually comprise a housing, which is designed as a pressure-resistant housing and is composed of several components or housing parts. It is essential for the reliable operation and safe operation of the pump that the housing parts are so securely and sealingly connected to each other that these compounds can withstand even the highest delivery pressures and delivery rates reliably.
  • delivery heights of 2000 m, or even more, at delivery rates of 800 m3 / h, or even more may be necessary.
  • the housing parts are connected to each other via a plurality of screw connections, wherein the screw connections - depending on the type of pump - for example, to the shaft of the pump are arranged around, so that the longitudinal axes of the screw extend in each case in the direction of the shaft.
  • the shell casing has a plurality of threaded bolts disposed about the shaft of the pump. After placing the cover on the jacket housing, the threaded bolts pass through the lid. Subsequently, threaded nuts are screwed onto the threaded bolt to connect the lid pressure-tight and sealing with the jacket housing.
  • a plurality of stage housings is typically provided, which are arranged in the direction of the shaft of the pump one behind the other between an inlet-side suction housing and an outlet-side pressure housing.
  • a plurality of tie bolts or tie rods are then provided, each extending parallel to the shaft of the pump through the suction housing and through the pressure housing.
  • On each tie rod is then screwed on both sides, ie on the pressure housing and the suction housing, a threaded nut, whereby the pressure housing and the suction housing and the intermediate step housing are clamped together so that pressure-resistant and tight screw connections between the components are realized.
  • screw connections are tightened according to a predetermined pattern, that is to say in particular in a predetermined sequence, and with predetermined torques.
  • Hytorc Hytorc Clamp
  • Hytorc Clamp is a mechanical clamping element that is assembled or disassembled using a hydraulic mounting device.
  • tensioning element marketed by the Nord-Lock Group under the trade name Superbolt, which is a purely mechanical tensioning device and replaces the conventional threaded nut in a screw connection.
  • Superbolt is a clamping element with multiple screws, which can be tightened or loosened mechanically or pneumatically with conventional tools.
  • For assembly or disassembly of a Superbolt clamping element there is no need for hydraulic assembly tools.
  • Another commercially available tensioning element is the expansion nut sold by the company devotec GmbH under the trade name CLAMP.
  • clamping devices are significantly more expensive compared to conventional threaded nuts, so that the replacement of each threaded nut by such a clamping device represents a very significant cost factor.
  • screw connections for example in a pump, to be subject to special requirements with regard to the material, which may depend on the environment or the operating conditions in which or under which the pump is operated (eg corrosive environment or environments requiring explosion protection). If the known chucks are not then available from materials that are certified or approved for such environments, at least additional and expensive material testing or certification is required.
  • the object of the invention solving this object are characterized by the features of the independent claim of each category.
  • a mounting device for a screw connection with a threaded bolt and one with the threaded bolt cooperating polygonal threaded nut for fastening two components together, which mounting device comprises a rotating ring for rotating the threaded nut, a non-threaded sleeve for receiving the rotary ring, and a tensioning device for torsion-free biasing of the threaded bolt, wherein the rotary ring has a polygonal central opening for enclosing the threaded nut, which Opening is configured such that the threaded nut is rotatable by rotating the rotary ring, wherein the sleeve in an axial direction has a length which is greater than a length of the rotary ring in the axial direction, wherein the sleeve has a first axial end surface for placement on a the components comprises, a second axial end surface on which a force is exerted with the clamping device, a continuous central recess for receiving
  • the inventive mounting device makes it possible in a simple and cost-effective manner to bias a screw torsion and with a high bias accuracy.
  • the preloaded screw can then be tightened by simply turning the nut and secured it. After the threaded nut is tightened, the entire mounting device, including including the rotating ring, the sleeve and the clamping device can be released from the screw again and used for tightening further screw.
  • conventional threaded nuts can be used for the screw connection, without concessions to the torsion-free preload or to the accuracy of the bias voltage are necessary. So it requires no special clamping devices more, which are a permanent part of the screw. In principle, a single clamping device is sufficient to torsionally bias any or at least a very large number of screw connections.
  • clamping device for the inventive mounting device are all known clamping devices for torsionally biasing a screw, so in particular also the clamping devices mentioned above, which are commercially available under the trade name Hytorc Clamp or Superbolt or CLAMP-nut (from the company devotc) , or similar or equivalent clamping devices.
  • the Clamping device can be configured as purely mechanical or as a hydraulic tensioning device or as a hydraulically operated clamping device.
  • the mounting device according to the invention is suitable both for tightening and for loosening a screw connection.
  • the mounting device is designed for the use of conventional threaded nuts.
  • the rotary ring is designed for interaction with a hexagonal threaded nut.
  • the inventive mounting device for large screw that require considerable forces to tighten the screw. Therefore, it is preferred if the rotary ring is designed for cooperation with a threaded nut which corresponds to the thread standard M48 or greater.
  • the mounting device can also be designed for significantly larger nuts, for example, for threaded nuts size M95.
  • a plurality of bores are provided, each of which for cooperation with a tool for rotating the
  • Rotary ring is configured. By this measure, it is particularly easy to rotate the rotary ring in the sleeve with a tool through the longitudinal slot in the sleeve.
  • the central recess has a diameter at the second axial end surface which is smaller than a maximum inner diameter of the central opening of the rotary ring.
  • the central recess in the region of the first axial end surface has a diameter which is adapted to the rotary ring in such a way that the sleeve surrounds the rotary ring with little play.
  • the game is designed so that the turning ring can still easily rotate within the sleeve,
  • a further advantageous measure is that the lateral surface of the sleeve has a plurality of longitudinal slots for rotating the rotary ring in the sleeve, each of which extends in the circumferential direction of the sleeve.
  • the tensioning device is designed as a mechanical tensioning device for torsion-free pretensioning of the threaded bolt.
  • the biasing of the threaded bolt takes place with a mechanical tensioning device or with a mechanical tensioning device which is hydraulically actuated. But it is also possible to perform the preloading with a hydraulic clamping device.
  • the inventive method is particularly suitable for screw in a pump. Therefore, it is a preferred embodiment, when the two components which are fastened to each other, are housing parts of a pump.
  • one of the components may be a jacket of a pump.
  • one of the components is a suction housing or a pressure housing of a link pump.
  • the inventive method is particularly suitable for such screw in which the threaded bolt has a thread diameter of at least 48 mm.
  • Fig. 2 shows an exploded view of an embodiment of an inventive mounting device, which is generally designated by the reference numeral 1.
  • the assembly device 1 is suitable for tightening or loosening the screw 10, which comprises a threaded bolt 11 and a cooperating with the threaded bolt 11 polygonal threaded nut 12, and which to do so serves, two components (see Fig. 1 ) to attach to each other.
  • the threaded bolt 11 is at least in the areas where it enters into operative connection with the threaded nut (s) 12, provided with an external thread
  • the threaded nut 12 is provided with a corresponding internal thread, which cooperates with the external thread is designed.
  • the external thread and the internal thread which are in the Fig. 2 and Fig. 3 are not shown in detail, are preferably standard thread, which are designed according to one of the usual thread standards, for example as a metric ISO thread.
  • threaded nuts 12 or threaded bolts 11 which are designed with threads according to one of the usual thread standards, for example with ISO metric threads, referred to as "conventional”.
  • threaded bolt generally means such components of a screw having an external thread, so for example screws, bolts, threaded rods, rods or bolts, which are provided only over part of their length with an external thread.
  • Fig. 1 Illustrated for a better understanding Fig. 1 in a very schematic representation of an embodiment of a pump, which is generally designated by the reference numeral 100, and which is designed as a centrifugal pump.
  • the pump 100 is configured as a multi-stage ring pump, more particularly as a high pressure stage housing pump.
  • Such pumps 100 are used for example in the power generating industry as feedwater pumps in industrial power plants. They can be designed for capacities of up to 800 m 3 / h (or even more) and delivery heights of 2000 m (or more), and can generate water pressures of a few hundred bar, for example 300 bar. It is understood that the housing of such a pump 100 must be configured as a pressure-resistant housing, which can withstand these enormous loads safely and reliably.
  • the pump 100 includes a suction housing 101, to which an inlet 103 for the fluid to be delivered, for. As water, is provided and a pressure housing 102, on which an outlet 104 is provided for the fluid. Between the suction housing 101 and the pressure housing 102, a plurality of stage housings 106 (stage casing) are provided, which are arranged one behind the other. Typically, an impeller (not shown) for delivering the fluid is provided in the suction housing 101 and in each of the stage housings 106, respectively. All wheels are arranged on a common shaft 105, which in Fig. 1 is indicated only by a line, each impeller rotatably connected to the shaft 105. The shaft 105 is driven by a drive unit, not shown, for example, an electric motor for rotation, as the arrow D in Fig. 1 suggests. By the rotation of the shaft 105 all wheels are driven for rotation.
  • a drive unit not shown, for example, an electric motor for rotation, as the arrow D in Fig. 1 suggests.
  • the pressure-resistant housing of the pump 100 thus includes here the suction housing 101, the pressure housing 102, and arranged therebetween stage housing 106.
  • a plurality of screw 10 is provided by each of which comprises a threaded bolt 11 which is designed as a tension bolt.
  • the threaded bolt 11 extends parallel to the shaft 105 and passes through both the pressure housing 101 and the suction housing 102.
  • the threaded bolt 11 is fixed in each case by a threaded nut 12.
  • the threaded bolt 11 By tightening the threaded nuts 12, the threaded bolt 11 can be tensioned, whereby the suction housing 101, the pressure housing 102 and the intermediate step housing 106 are clamped together so as to form a pressure-tight housing of the pump 100 together.
  • a plurality of such Screw 10 is provided, each threaded bolt 11 each extending parallel to the shaft 105, and wherein the threaded bolts 11 are arranged around the shaft.
  • the invention is not limited to screw in such a designed pump.
  • the invention is particularly suitable for screw in differently designed pumps, for screw between pressure-resistant housing parts of other devices and for screw in general.
  • the invention is also particularly suitable for screw connections in centrifugal pumps, which are configured as casing casing pumps (barrel casing pump).
  • casing casing pumps barrel casing pump
  • the threaded bolts 11 are usually provided at one axial end of the shell, with the threaded bolts 11 each extending parallel to the shaft of the pump, and being arranged around the shaft. On this threaded bolt 11 in the end face of the shell then a lid is placed, which is then secured with threaded nuts 12 on the jacket housing, or is clamped with this.
  • screw 10 is for example such as they are based on Fig. 1 was explained.
  • the threaded bolt 11 is provided at least at its end with an external thread, which is designed according to the metric ISO standard.
  • the threaded bolt 11 is at least of the size M48, but can also be significantly thicker, for example M95.
  • the longitudinal direction in which the threaded bolt 11 extends defines a direction referred to as the axial direction A.
  • the threaded nut 12 is designed as a conventional hexagonal nut and of course of its size or its internal thread of the same thread form and size as the threaded bolt 11, i. also the nut 12 is at least of the size M48.
  • the screw 10 may also comprise an annular disc 13 which is arranged between the threaded nut 12 and the component on which the threaded nut 12 is supported, that is, for example, the suction housing 101 or the pressure housing 102.
  • the mounting device 1 comprises a rotary ring 2 for rotating the threaded nut 12, a threadless sleeve 3, which receives the rotary ring 2, so that the rotary ring 2 is surrounded by the sleeve 3 and is disposed completely within the sleeve 3, and a tensioning device 4 for torsion-free pretensioning of the threaded bolt 11.
  • the rotary ring 2 comprises a polygonal central opening 21 for enclosing the threaded nut 12, wherein the opening 21 is configured so that the threaded nut 12 is rotatable by rotation of the rotary ring 2. Since in the embodiment described here, the threaded nut 12 is designed as a hexagonal threaded nut 12, and the central opening 21 in the rotary ring 2 is designed hexagonal.
  • the inner diameter of the central opening 21 is dimensioned such that the rotary ring 2 can be placed on the threaded nut 12, enclosing it and the hexagonal outer contour of the threaded nut 12 forms an operative connection with the hexagonal, the central opening 21 bounding inner contour of the rotary ring 2, so that by means of the rotary ring 2, a torque on the threaded nut 12 is exercisable.
  • the rotary ring 2 surrounds the threaded nut 12 according to the principle of a ring wrench with annular hexagonal profile.
  • the length L2 of the rotary ring 2 in the axial direction A is smaller than the length LM of the threaded nut 12 in the axial direction A.
  • the rotary ring 2 has an annular outer surface, which is designed as a smooth annular surface.
  • a plurality of holes 22 is provided, wherein the holes 22 are distributed over the circumference of the outer surface.
  • a pin-shaped element of a tool can be used to rotate the rotary ring 2 about the axial direction A.
  • the unthreaded sleeve 3 has a generally cylindrical shape and has in the axial direction A has a length L3 which is greater than the length L2 of the rotary ring 2 in the axial direction A and greater than the length LM of the threaded nut 12 in the axial direction A.
  • the sleeve 3 is bounded by a first axial end surface 31 and by a second axial end surface 32, which are each configured as annular surfaces.
  • the first axial end surface 31 is designed as a contact surface, with which the sleeve 3 contacts one of the components which are fastened to one another by the screw connection 10. In the example of Fig. 1 During assembly, therefore, the first axial end face 31 rests on the suction housing 101 or on the pressure housing 102. On the second axial end surface 32, a force is exerted during tightening of the screw 10 with the clamping device 4.
  • the sleeve 3 further comprises a continuous central recess 33 for receiving the rotary ring 2, which extends from the first axial end surface 31 to the second axial end surface 32.
  • the central recess 33 has a diameter D1, which is slightly larger than the outer diameter of the rotary ring 2, so that the rotary ring 2 can be inserted into the central recess 33 and in the inserted state relative to the sleeve 3 to the axial direction is rotatable.
  • the diameter D1 of the central recess 33 in the region of the first axial end surface 31 is adapted to the rotary ring 2 such that the sleeve 3 surrounds the rotary ring 2 with little play. When inserted, the rotary ring 2 should still be easily rotatable relative to the sleeve 3.
  • the region in which the central recess 33 has the diameter D1, in the axial direction A has an extension which is greater than the length L2 of the rotary ring 2 in the axial direction A.
  • the extent of this region in the axial direction A is such that the Rotary ring 2 and the optional annular disc 13 with respect to the axial direction A can be completely absorbed by the recess 33 of the sleeve 3 and also a free space 34 exists, so that the rotary ring 2 also in the axial direction A in the sleeve 3 and relative to the sleeve. 3 can move.
  • the area of the recess 33, which has the diameter D1, is limited with respect to the axial direction A by an annular shoulder 35, which reduces the diameter of the recess 33 to a value which is smaller than D1.
  • This value is dimensioned such that it is on the one hand greater than the maximum outer diameter of the threaded nut 12 and on the other hand smaller than the outer diameter of the rotary ring 2.
  • the shoulder 35 forms a stop which the displacement of the rotary ring 2 in the axial direction A relative to the sleeve. 3 limited.
  • the central recess 33 has a diameter D2 which is smaller than the maximum inner diameter of the central opening 21 of the Preferably, the diameter D 2 is dimensioned such that on the one hand the threaded bolt 11 can still be easily passed through the second axial end face 32, and on the other hand, the second axial end face 32 comes as close as possible to the threaded bolt 11, the threaded bolt 11 so with a the smallest possible diameter D2 surrounds.
  • the sleeve 3 further has an outer circumferential surface 36, which connects the first and the second axial end surface 31, 32, and which surrounds the central recess 33.
  • the lateral surface 36 In the lateral surface 36 at least one longitudinal slot 37 is provided, which extends in the circumferential direction of the sleeve 3, and which allows rotation of the rotary ring 2 relative to the sleeve 3, when the rotary ring 2 is surrounded by the sleeve 3.
  • the pin-shaped element of a tool can be brought into engagement with one of the bores 22 so as to rotate the rotary ring 2 about the axial direction A.
  • a plurality of longitudinal slots 37 are provided, each of which extends in the circumferential direction of the sleeve 3.
  • a locking ring 38 may be provided in the sleeve 3, which is configured for example as a snap ring, and which prevents slipping out of the rotary ring 2 from the sleeve 3 through the first axial end face 31 therethrough.
  • the locking ring 38 is preferably inserted into a circumferential groove in the interior of the sleeve 3, wherein the circumferential groove is arranged with respect to the axial direction A between the rotary ring 2 and the first axial end face 31 of the sleeve 3.
  • the inner diameter of the locking ring 38 is dimensioned such that it is smaller on the one hand than the outer diameter of the rotary ring 2 and on the other hand, the threaded nut 12 passes through the locking ring 38 passes.
  • each known clamping device 4 is suitable with which a torsion-free biasing of the threaded bolt 11 is possible.
  • the tensioning device 4 may be, for example, a purely mechanical tensioning device 4, or a mechanical tensioning device 4, which is hydraulically actuated, or a hydraulic tensioning device 4.
  • clamping devices described at the outset which are commercially available under the trade names Superbolt, Hytorc Clamp, CLAMP (devotec), or clamping devices which operate on the same or a similar principle, are suitable as clamping device 4 for the inventive mounting device 1. Since such clamping devices 4 are known per se, they need no further explanation here.
  • the optionally provided annular disc 13 is first pushed over the threaded bolt 11.
  • the threaded nut 12 is screwed onto the threaded bolt 11 until the threaded nut 12 or the annular disc 13 rests against the component, that is, for example, against the suction housing 101 or against the pressure housing 102.
  • the sleeve 3 is placed with the rotary ring 2 therein on the threaded nut 12, so that the threaded nut 12 and the rotary ring 2, more precisely, the central opening 21 of the rotary ring 2, intermesh, and the first axial end face 31 of the sleeve 3 to the corresponding Component is present.
  • the threaded bolt 11 is received by the central recess 33 and then protrudes beyond the second axial end surface 32 of the sleeve 3 also.
  • the clamping device 4 is brought into contact with the threaded bolt 11 such that the clamping device 4 rests on the second axial end face 32 of the sleeve 3, and that an operative connection between the clamping device 4 and the threaded bolt 11 is generated.
  • the clamping device 4 is designed, for example, in the form of a Superbolt or a Hyptorc clamp or a CLAMP nut of the company devotec, the clamping device 4 is screwed onto the threaded bolt 11 until the clamping device 4 rests against the second axial end surface 32 of the sleeve 3.
  • the threaded bolt 11 is then biased with a predetermined biasing force, wherein the clamping device 4 is supported on the second axial end surface 32 of the sleeve 3, and the sleeve 3 is supported with the first axial end surface 31 on the component.
  • Through the longitudinal slot 37 through the pin-shaped element of a tool is now brought into engagement with one of the bores 22 in the outer surface of the rotary ring 2, and by turning the rotary ring 2, the threaded nut 12 is tightened until it or the annular disc 13 back to the corresponding Component is present.
  • the mounting device 1 After the predetermined bias of the threaded bolt 11 has been generated and the threaded nut 12 is tightened, the mounting device 1, so the clamping device 4 and the sleeve 3 is removed with the rotary ring 2 disposed therein from the screw 10 and is responsible for tightening the next screw 10th to disposal.
  • the invention thus advantageously combines the advantages of the torsion-free preload with a precisely adjustable preload force by means of a tensioning device 4 with the possibility of using conventional threaded nuts 12 for the screw connection 10.
  • the mounting device 1 with the clamping device 4 does not remain permanently on the pump 100, but only for the assembly (or disassembly), more precisely for the tightening (or loosening) of the screw 10, needed and then removed again becomes.
  • the mounting device 1 since the mounting device 1 is not a permanent part of the pump 100, it requires no qualification or certification for the materials of which the mounting device 1 consists.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Clamps And Clips (AREA)
  • Hand Tools For Fitting Together And Separating, Or Other Hand Tools (AREA)
EP17195854.9A 2017-10-11 2017-10-11 Dispositif de montage pour un assemblage vissé et procédé de serrage d'un assemblage vissé Withdrawn EP3470177A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP17195854.9A EP3470177A1 (fr) 2017-10-11 2017-10-11 Dispositif de montage pour un assemblage vissé et procédé de serrage d'un assemblage vissé
PCT/EP2018/077426 WO2019072817A1 (fr) 2017-10-11 2018-10-09 Dispositif de montage destiné à une liaison à vis et procédé destiné à serrer une liaison à vis

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17195854.9A EP3470177A1 (fr) 2017-10-11 2017-10-11 Dispositif de montage pour un assemblage vissé et procédé de serrage d'un assemblage vissé

Publications (1)

Publication Number Publication Date
EP3470177A1 true EP3470177A1 (fr) 2019-04-17

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP17195854.9A Withdrawn EP3470177A1 (fr) 2017-10-11 2017-10-11 Dispositif de montage pour un assemblage vissé et procédé de serrage d'un assemblage vissé

Country Status (2)

Country Link
EP (1) EP3470177A1 (fr)
WO (1) WO2019072817A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3749362A (en) * 1971-04-09 1973-07-31 Nasa Fastener stretcher
EP0200459A2 (fr) * 1985-04-29 1986-11-05 Hedley Purvis Limited Assemblage piston-cylindre mis en action par un fluide
WO1991001198A1 (fr) * 1989-07-14 1991-02-07 Richard Paul Warren Procede de controle de la compression d'un joint d'etancheite pendant le serrage d'un organe de fixation
US20090293418A1 (en) * 2008-05-30 2009-12-03 Gordon Britton Foundation Bolt Tensioner

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3749362A (en) * 1971-04-09 1973-07-31 Nasa Fastener stretcher
EP0200459A2 (fr) * 1985-04-29 1986-11-05 Hedley Purvis Limited Assemblage piston-cylindre mis en action par un fluide
WO1991001198A1 (fr) * 1989-07-14 1991-02-07 Richard Paul Warren Procede de controle de la compression d'un joint d'etancheite pendant le serrage d'un organe de fixation
US20090293418A1 (en) * 2008-05-30 2009-12-03 Gordon Britton Foundation Bolt Tensioner

Also Published As

Publication number Publication date
WO2019072817A1 (fr) 2019-04-18

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