EP2938881B1 - Flügelzellenpumpe mit variabler verdrängung sowie verfahren zur regelung dieser verdrängung - Google Patents

Flügelzellenpumpe mit variabler verdrängung sowie verfahren zur regelung dieser verdrängung Download PDF

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Publication number
EP2938881B1
EP2938881B1 EP13824386.0A EP13824386A EP2938881B1 EP 2938881 B1 EP2938881 B1 EP 2938881B1 EP 13824386 A EP13824386 A EP 13824386A EP 2938881 B1 EP2938881 B1 EP 2938881B1
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EP
European Patent Office
Prior art keywords
pump
rolling elements
regulation
regulation ring
displacement
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Not-in-force
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EP13824386.0A
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English (en)
French (fr)
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EP2938881A1 (de
Inventor
Matteo Calderoni
Leonardo Cadeddu
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VHIT SpA
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VHIT SpA
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Publication of EP2938881A1 publication Critical patent/EP2938881A1/de
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Publication of EP2938881B1 publication Critical patent/EP2938881B1/de
Not-in-force legal-status Critical Current
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Classifications

    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings

Definitions

  • the present invention relates to variable displacement rotary pumps, and more particularly it concerns a pump of a kind in which displacement regulation is obtained thanks to the variation of the relative eccentricity between a regulation ring and the pump rotor, obtained by varying the relative position of the ring and the rotor depending on the pump operating conditions.
  • the invention also concerns a method of regulating the displacement of such a pump.
  • the present invention is applied in a pump for the lubrication oil of a motor vehicle engine.
  • the regulation movement is a rotation
  • the portion of the region of engagement between the surfaces is configured as a sector of a rolling bearing of which said surfaces form sectors of the inner race and the outer race, respectively, and the rolling elements are arranged within a seat formed in the external surface of the regulation ring.
  • the rolling elements are rollers or needles mounted in a supporting and guiding cage arranged to move in said seat against the action of an opposing resilient member, which is arranged between one end of the cage and one end of the seat and is preloaded so as to keep the cage in contact with the opposite end of the seat in a maximum displacement or rest condition of the pump.
  • the invention also provides a method of regulating the displacement of a pump of the above kind, comprising the steps of:
  • a pump 1 of the above kind comprises a body 10 having a suitably shaped cavity 40 in which stator 11 is mounted so as to be freely rotatable along an arc of circumference, in the illustrated example in clockwise direction, as indicated by arrow A.
  • Reference character B denotes the axis of rotation of stator 11.
  • Stator 11 has a chamber 12 where vane rotor 13 is housed. The rotor is keyed on a shaft 14 arranged off-axis relative to centre C of chamber 12. Also rotor 13 is rotatable in clockwise direction.
  • Reference numerals 41 and 42 denote the ends of the suction and delivery ducts, when rotor 13 rotates in clockwise direction.
  • stator 11 has a pair of radial appendages 17, 18, which project into respective chambers 15, 16 formed by recesses of cavity 40, and which slide in fluid-tight manner on the bases of chambers 15, 16.
  • One of the chambers, for instance chamber 15, is permanently connected to the delivery side of the pump or to the units utilising the pumped fluid (in particular, in the preferred application, to a point of the engine lubrication circuit located downstream the oil filter), through a first regulation duct, not shown in these Figures.
  • the other chamber can in turn be put in communication with the delivery side or with the units utilising the pumped fluid through a valve operated by the electronic control unit of the vehicle and a second regulation duct (not shown). In this manner, appendage 17 is, or both appendages 17, 18 are, exposed to the pressure conditions of the pumped fluid.
  • An end wall of one of the chambers, e.g. chamber 15, may be shaped so as to form an abutment 19 for appendage 17 in the maximum displacement condition.
  • Chamber 16 houses a member 20 opposing the rotation of stator 11. That member, in the example illustrated, comprises two opposite mushroom-shaped elements 21, 22, connected for instance in telescopic manner and biased in opposite directions by a spring 23 arranged between heads 21A, 21B of both elements.
  • Spring 23 is preloaded so as to oppose the rotation of stator 11, and hence to keep it in the position shown in Fig. 1 , as long as the pressure applied to appendage 17 (or the overall pressure applied to appendages 17, 18) is lower than a predetermined threshold, and to subsequently keep the pump displacement at the value corresponding to the pressure threshold.
  • Such a condition is attained when an equilibrium is established between the torques generated by the pressure acting on appendages 17, 18 and the antagonist torque generated by spring 23.
  • Heads 21A, 21B for instance substantially shaped as half cylinders, engage recesses 22A, 22B of complementary shape formed in the opposite surface of appendage 18 with respect to the surface acted upon by the regulating pressure and in a wall of chamber 16, respectively.
  • a pair of articulated joints is formed allowing keeping the ends of spring 23 mutually parallel during the rotation of stator 11, thereby ensuring a good lateral stability of the spring itself.
  • the circumferential extension and the radial size of chambers 15, 16 will be determined depending on the operation characteristics required of the pump.
  • a rotation of stator 11 of the order of about 20° is typical for the preferred application and has been shown in the drawings.
  • the radial size it may be constant over the whole circumferential extension, so that appendages 17, 18 have a constant thrust area and hence generate a constant torque, proportional to the actuation pressure, over the whole arc of rotation.
  • the radial size of one chamber or both chambers may change along the circumferential extension, and appendages 17, 18 have a variable thrust area, so as to generate a variable torque over the arc of rotation of stator 11.
  • Such a solution allows taking into account the fact that the resistant torques encountered during displacement regulation may be variable, for instance because the resistance opposed by opposing spring 20 and/or the rotational frictions vary.
  • Figs. 1 and 2 also show the different forces acting on the components of pump 1 during operation and the reactions caused by such forces. It is to be appreciated that Figs. 1 and 2 only are intended to give a representation of the zones where the different forces act and of the directions of the forces, whereas their magnitudes are not considered. More particularly:
  • Figs. 3 and 4 show the vectors representing forces F P1 - F C mentioned above and their partial and overall resultants in the extreme operating conditions shown in Figs. 1 and 2 .
  • the origin of the axes coincides with centre of rotation B of stator 11.
  • resultants SV1 and SV2, respectively, of the above forces have such orientations that they act in correspondence of a zone S of the mutually engaging surfaces in stator 11 and cavity 40.
  • the fluid under pressure present in chamber 12 creates a hydraulic support bearing.
  • the reaction provided by such a bearing is force R V mentioned above, which has the same magnitude as and opposite direction to the above resultants.
  • a plurality of rolling elements 25, in the illustrated example rollers or needles are arranged between external surface 11A of stator 11 and internal surface 40A of cavity 40, over a portion including zone S where the hydraulic support bearing is created and where resultants SV1, SV2 of the various forces act.
  • rollers 25 are fitted, for instance snap fitted, in respective seats 27 in a supporting cage 26, preferably made of plastic material, which in conventional manner acts as a guide and a spacer for rollers 25.
  • Cage 26 with rollers 25 is housed in a recess of external surface 11A of stator 11, which recess axially extends over the whole axial depth of stator 11 and chamber 40.
  • Recess 28, cage 26 and rollers 25 have such a radial size that the contact between surfaces 11A and 40A is ensured by rollers 25.
  • Typical diameters for the rollers, in the preferred application, are of the order of a few millimetres, for instance 2 - 4 mm.
  • rollers 25 have an axial size (length) slightly shorter than that of cage 26. This gives a labyrinth configuration to the assembly of cage 26 and rollers 25, which configuration allows maintaining the hydraulic support bearing.
  • Cage 26 has an angular extension smaller than the angular extension of recess 28, so that it can move within the recess during the rotation performed by stator 11 for the displacement regulation, and the angular extension of the displacement of cage 26 is smaller than the angular extension of the rotation performed by stator 11 for passing from the maximum displacement position to the minimum displacement position.
  • Recess 28 is defined by two steps or abutments 29A, 29B.
  • One end of cage 26 abuts against one of such abutments, for instance abutment 29A, in the rest condition (maximum displacement) of the pump, shown in Fig. 5 .
  • a resilient member 30 opposing the cage movement e.g. a suitably preloaded leaf spring, is instead arranged between cage 26 and the other abutment 29B and it keeps cage 26 in contact with abutment 29A in the maximum displacement condition.
  • Fig. 5 and 6 clearly show the behaviour of cage 26 with rollers 25 during displacement regulation.
  • three reference points belonging to body 10, stator 11 and cage 26, respectively, have been shown by segments X, Y and Z.
  • the three points are chosen so that their positions coincide in the maximum displacement condition ( Fig. 5 ).
  • point X At the end of the rotation bringing stator 11 to the minimum displacement position ( Fig. 6 ), point X of course has remained stationary, whereas point Z has displaced in clockwise direction and has described an arc that, in the example illustrated, is of about 20°.
  • point Y has performed a rotation in clockwise direction, yet over an arc shorter than that described by point Z. Due to the shorter rotation of cage 26 with respect to stator 11, cage 26 is no longer in contact with abutment 29A at the end of the rotation and spring 30 is more compressed.
  • the invention can be applied also to pumps where the rotation of the stator is achieved in different manner (for instance, through a gear engaging a toothed sector of the external surface of the stator, like in US 5,863,189 ) or to pumps where the regulation movement is different from the rotation of the stator disclosed here ("pendulum" pumps, pumps with oscillating stator, pumps with a translation of the stator ring, and so on).
  • cage 26 will be a linear cage.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

  1. Flügelzellenpumpe mit variabler Verdrängung für Flüssigkeiten, mit
    - einem Rotor (13), der dazu vorgesehen ist, exzentrisch in einem Regelring (11) mit einer relativen Exzentrizität zu rotieren, die sich in Abhängigkeit von den Betriebsbedingungen der Pumpe (1) ändert,
    - Mitteln (17, 18) zum Bewegen des Regelrings (11) in einer Kammer (40), die in einem Pumpenkörper (10) gebildet ist, um die relative Exzentrizität zu variieren und somit die Verdrängung der Pumpe, wenn sich die Betriebsbedingungen ändern, und
    - mehreren Wälzelementen (25), die zwischen einer äußeren Fläche (11A) des Regelrings (11) und einer inneren Fläche (40A) der Kammer (40) angeordnet sind,
    dadurch gekennzeichnet, dass
    - die Wälzelemente (25) in einem stützenden Käfig (26) angeordnet sind und nur über einen Abschnitt eines Wechselwirkungsbereichs zwischen der äußeren Fläche (11A) des Regelrings (11) und der inneren Fläche (40A) der Kammer (40) vorgesehen sind, wobei der Abschnitt eine Zone (S) enthält, in der eine Resultierende (SV1, SV2) von mechanischen und fluidischen Kräften, die in der Pumpe während der Regelung erzeugt werden, wirkt, und
    - die Wälzelemente (25) und der stützende Käfig (26) in dem Abschnitt des Wechselwirkungsbereichs zwischen den Flächen (11A, 40A) so angeordnet sind, dass sie sich als ein integralen Körper entlang der Flächen (11A, 40A) bei der Bewegung des Regelrings (11) bewegen, wobei die Bewegung der Wälzelemente (25) und des stützenden Käfigs (26) eine kleinere Amplitude haben als eine Bewegung, die der Regelring (11) ausführt, um die Pumpe von einer maximalen Verdrängung zu einer minimalen Verdrängung bringen.
  2. Pumpe nach Anspruch 1, wobei die Regelungsbewegung eine Drehung des Regelrings (11) ist und wobei:
    - in dem Abschnitt des Wechselwirkungsbereichs die äußere Fläche (11A) des Regelrings (11) und die innere Fläche (40A) der Kammer (40) zusammen mit den Wälzelementen (25) einen Sektor eines Kugellagers bilden, bei dem diese Flächen Abschnitte eines inneren und eines äußeren Rings bilden, und
    - die Wälzelemente (25) in einem Sitz (28) angeordnet sind, der in der Fläche (11A) des Regelrings (11) gebildet ist und eine größere Ausdehnung als der stützende Käfig (26) hat, in dem die Wälzelemente (25) angeordnet sind.
  3. Pumpe nach Anspruch 1 oder 2, wobei der stützende Käfig (26) dazu vorgesehen ist, sich in dem Sitz zu bewegen, und dadurch die Wälzelemente (25) gegen die Wirkung eines entgegenwirkenden Rückstellelements (30) zu bewegen, das zwischen einem Ende des Käfigs (26) und dem anderen Ende (29B) des Sitzes (28) angeordnet ist und dafür geeignet ist, den Käfig (26) mit dem gegenüber liegenden Ende (29A) des Sitzes (28) bei dem maximalen Verdrängungszustand der Pumpe wieder in Kontakt zu bringen oder in Kontakt zu halten.
  4. Pumpe nach einem der Ansprüche 1 bis 3, wobei die Wälzelemente (25) in dem stützenden Käfig (26) so angeordnet ist, dass sie eine Labyrinthkonfiguration ergeben, die dafür vorgesehen ist, ein fluidisches Stützlager zu erhalten, das in der Zone (S) als eine Reaktion auf die Wirkung der Resultierenden (SV1, SV2) dieser Kräfte gebildet wird.
  5. Pumpe nach Anspruch 4, wobei die Wälzelemente (25) Rollen oder Nadeln sind, und wobei der stützende Käfig (26) eine axiale Tiefe hat, die im Wesentlichen der axialen Tiefe des Regelrings (11) entspricht und die Rollen oder Nadeln (25) eine Länge haben, die kürzer als die axiale Tiefe des Käfigs (26) ist.
  6. Pumpe nach einem der Ansprüche 1 bis 5, wobei die Drehung des Regelrings (11) direkt durch den Druck des gepumpten Fluids gesteuert wird.
  7. Pumpe nach einem der vorstehenden Ansprüche, wobei die Pumpe eine Pumpe für den Schmiermittelkreislauf eines Fahrzeugmotors ist.
  8. Verfahren zum Regeln der Verdrängung einer Flügelzellenpumpe mit variabler Verdrängung für Flüssigkeiten, die einen Rotor (13) hat, der dazu vorgesehen ist, exzentrisch in einem Regelring (11) mit einer relativen Exzentrizität zu rotieren, die in Abhängigkeit von den Betriebsbedingungen der Pumpe (1) veränderbar ist, wobei das Verfahren die folgenden Schritte aufweist:
    - Anordnen von mehreren Wälzelementen (25) zwischen einer äußeren Fläche (11A) des Regelrings (11) und einer inneren Fläche (40A) der Kammer (40), in welcher der Ring (11) angeordnet ist, in einer festgelegten relativen Lage,
    - Bewegen des Regelrings (11) in der Kammer (40), um die relative Exzentrizität und damit die Verdrängung der Pumpe zu verändern, wenn sich die Betriebsbedingungen der Pumpe ändern,
    und dadurch gekennzeichnet ist, dass der Schritt des Anordnens der Wälzelemente (25) in der Kammer (40) die folgenden Schritte aufweist:
    - Anordnen der Wälzelemente (25), die in dem stützenden Käfig (26) vorgesehen sind, nur in einem Abschnitt eines Wechselbereichs zwischen der äußeren Fläche (11A) des Regelrings (11) und der inneren Fläche (40A) der Kammer (40), wobei der Teil eine Zone (S) enthält, in der eine Resultierende (SV1, SV2) von mechanischen und fluidischen Kräften wirkt, die in der Pumpe bei der Regelung erzeugt werden, und
    - während der Regelung die Wälzelemente (25) und der stützende Käfig (26) dazu gebracht werden, sich als ein integraler Körper in dem Abschnitt des Wechselwirkungsbereichs zwischen den Flächen (11A, 40A) zu bewegen, die Bewegung der Wälzelemente (25) und des stützenden Käfigs (26) eine kleinere Amplitude haben als eine Bewegung des Regelrings (11), welche die Pumpe von einer maximalen Verdrängung zu einer minimalen Verdrängung bringt.
  9. Verfahren nach Anspruch 8, wobei die Regelungsbewegung eine Drehung des Regelungsrings (11) und der Schritt des Anordnens der Wälzelemente (25) und des stützenden Käfigs (26) in nur einem Teil des Wechselwirkungsbereichs zwischen den Flächen (11A, 40A) den Schritt des Konfigurierens der Wälzelemente (25) und des stützenden Käfigs (26), der äußeren Fläche (11A) des Regelrings (11) und der inneren Fläche (40A) der Kammer (40) als einen Sektor eines Kugellagers umfasst, dessen Flächen kreisförmige Abschnitte eines Innenrings und eines Außenrings bilden.
  10. Verfahren nach Anspruch 8 oder 9, wobei der Schritt des Veranlassens der Wälzelemente (25) und des stützenden Käfigs (26) sich als ein integraler Körper zu bewegen, das Bewegen der Wälzelemente und des stützenden Käfigs (26) in einem Sitz (28) enthält, der in der Fläche (11A) des Regelrings (11) gebildet ist und eine größere Ausdehnung als die gesamte Ausdehnung der Wälzelemente (25) und des stützenden Käfigs (26) hat.
EP13824386.0A 2012-12-27 2013-12-13 Flügelzellenpumpe mit variabler verdrängung sowie verfahren zur regelung dieser verdrängung Not-in-force EP2938881B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT001149A ITTO20121149A1 (it) 2012-12-27 2012-12-27 Pompa a palette a cilindrata regolabile e metodo per la regolazione della cilindrata di tale pompa.
PCT/IB2013/060918 WO2014102652A1 (en) 2012-12-27 2013-12-13 Variable displacement vane pump and method of regulating the displacement thereof

Publications (2)

Publication Number Publication Date
EP2938881A1 EP2938881A1 (de) 2015-11-04
EP2938881B1 true EP2938881B1 (de) 2017-03-08

Family

ID=47749969

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13824386.0A Not-in-force EP2938881B1 (de) 2012-12-27 2013-12-13 Flügelzellenpumpe mit variabler verdrängung sowie verfahren zur regelung dieser verdrängung

Country Status (5)

Country Link
US (1) US20150322944A1 (de)
EP (1) EP2938881B1 (de)
CN (1) CN104903582A (de)
IT (1) ITTO20121149A1 (de)
WO (1) WO2014102652A1 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762615A (zh) * 2017-02-16 2017-05-31 陕西法士特齿轮有限责任公司 一种单作用式变量叶片泵
CN106969249A (zh) * 2017-04-26 2017-07-21 奇瑞汽车股份有限公司 一种叶片式机油泵
IT201800003344A1 (it) * 2018-03-07 2019-09-07 O M P Officine Mazzocco Pagnoni S R L Pompa rotativa a palette a cilindrata variabile
CN114294354A (zh) * 2021-12-30 2022-04-08 綦江齿轮传动有限公司 一种缓速器油量调节装置

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Publication number Priority date Publication date Assignee Title
US1988213A (en) * 1931-02-12 1935-01-15 Racine Tool & Machine Company Multiple rotary pump
US2348428A (en) * 1939-12-22 1944-05-09 Hydraulic Dev Corp Inc Variable delivery vane pump
DE3542776A1 (de) * 1985-12-04 1987-07-23 Kurt G Dipl Ing Fickelscher Roll-ring-maschine zum verdichten und foerdern von fluiden
US5863189A (en) 1995-07-10 1999-01-26 Coltec Industries Inc Variable displacement vane pump adjustable by low actuation loads
CA2565179C (en) * 2004-05-07 2014-01-21 Magna Powertrain Inc. Vane pump using line pressure to directly regulate displacement
US8047822B2 (en) * 2006-05-05 2011-11-01 Magna Powertrain Inc. Continuously variable displacement vane pump and system
JP2010523896A (ja) * 2007-04-10 2010-07-15 ボーグワーナー・インコーポレーテッド 可変容量型デュアルベーンポンプ

Non-Patent Citations (1)

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Title
None *

Also Published As

Publication number Publication date
ITTO20121149A1 (it) 2014-06-28
WO2014102652A1 (en) 2014-07-03
US20150322944A1 (en) 2015-11-12
EP2938881A1 (de) 2015-11-04
CN104903582A (zh) 2015-09-09

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