EP3280900A2 - Moteur stirling à membrane - Google Patents

Moteur stirling à membrane

Info

Publication number
EP3280900A2
EP3280900A2 EP16736768.9A EP16736768A EP3280900A2 EP 3280900 A2 EP3280900 A2 EP 3280900A2 EP 16736768 A EP16736768 A EP 16736768A EP 3280900 A2 EP3280900 A2 EP 3280900A2
Authority
EP
European Patent Office
Prior art keywords
membrane
stirling engine
gas
engine according
hot
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.)
Granted
Application number
EP16736768.9A
Other languages
German (de)
English (en)
Other versions
EP3280900B1 (fr
Inventor
Jürgen KLEINWÄCHTER
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP21182490.9A priority Critical patent/EP3919729A1/fr
Priority to EP21182497.4A priority patent/EP3919730A1/fr
Publication of EP3280900A2 publication Critical patent/EP3280900A2/fr
Application granted granted Critical
Publication of EP3280900B1 publication Critical patent/EP3280900B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/055—Heaters or coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/057—Regenerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2244/00—Machines having two pistons
    • F02G2244/02—Single-acting two piston engines
    • F02G2244/06—Single-acting two piston engines of stationary cylinder type
    • F02G2244/10—Single-acting two piston engines of stationary cylinder type having cylinders in V-arrangement

Definitions

  • the invention relates to a membrane Stirling engine.
  • Classical Stirling engines consist of arrangements of rigid, pressure-resistant, gas-filled cylinders, heat exchangers for heating and cooling the hermetic enclosed working gas, displacers for periodically shifting the working gas from the cold to the hot side and back, an intermediate heat regenerator, as well as working piston for the transmission of the thermal pressure fluctuations of the Gases generated work to the outside.
  • the present invention has for its object to provide the prior art, an alternative or improvement.
  • the Stirling engine according to the invention has a special, specific design:
  • the working gas of the Stirling engine is located both in its hot part and in its cold part in membrane sleeves with negligible bending stiffness, which are hermetically sealed at one end and with its open end tightly closed, in the hot, or cold room of a regenerator box, open.
  • the gas to be heated is in this case in, for example, bags which are formed by thin-walled membrane casings of negligible bending rigidity. These membrane bags hermetically close the working gas and open into the regenerator box on their front side.
  • the membrane bags arranged to the right and left of the regenerator box together form a gas-tight unit. It is filled as much gas as the gas volume of the regenerator and corresponds to half of the maximum volume of both bags.
  • the membrane bags are in an immersion of hot or cold liquid.
  • the regenerator box separates the hot liquid space from the cold liquid space.
  • the entire unit of gas-filled membrane bags, regenerator box and heat-transferring hot or cold liquid is in turn in one closed, liquid-tight and pressure-resistant housing.
  • the hot fluid space, as well as the cold room, are provided with hydraulic pistons (or similar technical means such as bellows, hydraulic cash registers and the like) which can exactly displace the volume of liquid equal to half the maximum gas volume in the membrane bags.
  • the arranged on both the hot and on the cold side of the pressure-resistant housing hydraulic piston are connected via an eccentric so that they move with a corresponding phase shift (typically: 90 °) to each other.
  • the rotating axis of the eccentric (or an equivalent technical device, such as a swash plate or a cam) is provided with a flywheel.
  • the configuration described corresponds to a Stirling engine of the alpha construction.
  • the membrane Stirling engine avoids the mentioned weaknesses of classic Stirling engines (large ⁇ between heat exchangers and working gas, polytropic expansion and compression of the working gas instead of isothermia, dead volumes) due to the following effects:
  • the pulsating membrane bag causes a periodic reversal of
  • cylindrical tubes are designed as membrane bags.
  • the machine shifts the contents of the membrane bag sent, also the membrane bag is a very good heat exchanger. Because the membrane bag is whenever it is laid flat to a micro-heat exchanger.
  • the thin membrane spanned as flat surfaces on frame.
  • the frames have structures around their inner edges, which the membranes gently cling to as they are squeezed together without leaving any total volume.
  • Similar adaptation profiles are formed in the areas where the membrane bags are connected to the regenerator box in a gastight manner via rigid end profiles.
  • the hitherto described, preferred variant of the membrane Stirling engine according to the invention using plate-shaped stacks frame-supported, gas-filled membrane bag is to realize particularly favorable using thin elastomeric membrane.
  • Particularly suitable here are special, temperature-stabilized silicones, in particular fluorinated silicones, which can be used for continuous temperatures up to 250 ° C.
  • the novel membrane design of a Stirling engine should achieve significantly higher Carnot degrees of implementation than previous machines, which achieve a maximum of 50% of the Carnot efficiency.
  • Isothermal operating machines with low temperature storage between the working gas and the heater or cooler fluid, with minimum dead volume and lowest possible displacement drive line (by hydrostatic deformation of thin membrane), should allow implementation levels of 80% and more. This allows even at relatively low heating temperatures to achieve good mechanical efficiencies.
  • Another advantage of the relatively low temperature level opens the possibility to use simple pressurized water heat storage for cost-effective storage of solar heat and thus to the solar around-the-clock operation of such machines (power and electricity autonomy).
  • chillers / heat pumps manage without climate damaging refrigerants and only with air, water, antifreeze and conventional structural materials (steel or fiber-reinforced plastics) get along.
  • the advantage of the membrane Stirling machines is just in it, only abundant, cost-effective and environmentally friendly materials, and in case of storage use pressureless (T ⁇ 100 ° C) or pressurized water storage tanks (T> 100 ° C).
  • the use of thermal machines has the further advantage of automatically providing power, electricity, cooling or heat and waste heat (combined heat and power) and thus much better decentralized the required range To provide energy forms.
  • solar thermal machines will only have the potential to compete with the inherent, wear-resistant solar semiconductors (photovoltaic, thermoelectrics) if they are inexpensive to manufacture, and extremely durable and low in maintenance. By choosing the material, the price target is achievable.
  • the principle of hydrostatic, gentle deformation of thin, elastic membranes with relatively low operating frequencies (a few hertz) basically offers the potential of extreme longevity, in contrast to the established technologies with classical mechanical moving displacers and necessary seals.
  • the principle of the membrane stiffening motor is not limited to the described preferred topology of membrane film bags.
  • FIG. 7 it is also possible, for example, to use thin-walled hoses in various configurations. These can be wrapped according to the invention so that they are pressure-resistant in the unfolded state at a circular cross-section, and yet (due to their negligible bending stiffness) are virtually hydrostatic deformable force-free.
  • Such hoses can be integrated into a Stirling engine without the need for restraint in frame structures as previously described, and without the need for form-limiting interstices, as shown in FIG.8.
  • regenerator gap Another, particularly simple design of the membrane Stirling engine can be realized by the use of continuous from the hot into the cold space film tubes.
  • the (as wide as possible) film hoses are closed linearly at their open ends by mechanical terminal strips. At these they are fastened by means of springs on the wall of the hot or cold fluid space. In the middle zone of the hoses these are filled with regenerator material.
  • the hot fluid space is thereby separated from the cold fluid space by a gap formed by two heat-insulating plates. Through appropriate slots in these plates, the film tubes are passed ( Figure 9).
  • Such an embodiment of the membrane Stirling engine is particularly well suited for non-pressurized, built into the ground large machines.
  • Fig.10 such a machine is shown schematically.
  • a square pit is inserted into the earth.
  • the walls of this pit are thermally insulated - typically with an unbreakable, closed-cell insulation material such as foam glass.
  • the intermediate channel installed in the middle of the pit, consisting of two vertical foam glass walls, divides the pit into two identical large chambers, one of which is filled with hot water and the other with cold water.
  • the intermediate channel is also filled with water, which is doped with a gelling agent so that the water becomes a gel.
  • the gel water mechanically stabilizes the intermediate channel against the pressure fluctuations in the two working chambers generated by the Stirling cycle, it no longer transports heat by convection. This is important so that the linear temperature coefficient that builds up during operation in the regenerators is not destroyed.
  • a hydraulic auxiliary piston is used to continuously adjust the phase angle between the hot and cold working pistons. This serves three purposes:
  • phase angle is set to 180 ° for this start cycle.
  • Pulsator machines of the type described are particularly well suited as continuously operating base load machines, which receive their thermal energy from large power boilers ("source”) and large chilled water tanks ("sink”). As already described, they are able to supply electric power, mechanical energy for a variety of purposes around the clock, as well as cold and heat (reversible pulsator machine). In order to adapt the load profile to the temporally fluctuating demand profile, the phase angle is adjusted accordingly.
  • the temperatures in the heat accumulators are subject to fluctuations over time. Every temperature needs an optimal phase angle. This can be adjusted automatically via the hydraulic auxiliary piston.
  • the displacement of the fluid can also be realized by introduced into the hot and cold room membrane speakers or piezocrystals.
  • the phase shift between hot and cold space is accomplished in this case according to the invention by a corresponding electronic control of the two actuators.
  • the production of electrical energy is accomplished by a third loudspeaker (or piezocrystal), which is located in the cold liquid space and converts the thermodynamically generated pressure fluctuations via induction into electrical current.
  • a third loudspeaker or piezocrystal
  • Membrane pulsator machines of this type require no mechanical decoupling and are very small due to the high operating frequencies.
  • the "heart" of the membrane Stirling engine rests on flexible, thin-walled bags: periodically move the pulsators, which contain the working gas, and heat and cool it isothermally. Due to their inherent features, in particular those of isothermal compression or expansion of gases, these pulsators also make it possible, according to the invention, to realize other technical units than those of Stirling engines.
  • a typical application of this type is the "isothermal hydraulic accumulator.”
  • a classic hydraulic accumulator is shown schematically in Figure 3. It is typically used to temporarily store the surplus energy accumulated in a system at certain times and at the time when the system requires additional energy. Charge: The oil is pumped into the reservoir under pressure and compresses the gas (n 2 ) in the rubber bubble, which takes place adiabatically.
  • the compressed gas (n 2 ) expands and pushes the oil out of the reservoir.
  • This pressurized oil can then drive actuators such as cylinders and hydraulic motors.
  • An application example of such a hydraulic accumulator is a vehicle whose drive shaft is coupled to a hydraulic pump in such a way that oil is pumped when braking the vehicle and thereby compresses the gas in the memory.
  • the energy stored in this way in the "gas spring" can then, if the vehicle is to be accelerated in a row, be recovered via the pump now operating as a hydraulic motor and supplied to the drive shaft.
  • an actuator (5) presses the fluid (2) (preferably hydraulic oil) into a pressure vessel in which a sufficiently large number of hermetically sealed, gas (N 2 , air, other
  • N 2 hermetically sealed, gas
  • “enough large numbers” refers to the surface of the pulsator bags, which is measured so that the heat of compression in gas generated during hydrostatic compression will be well delivered to the circulating fluid, with its heat capacity being increased by orders of magnitude and thus the desired, quasi-isothermal compression takes place.
  • the "gas springs" realized by the pulsators push the fluid in the reverse direction through the actuator, which now acts not as in the previous power stroke as a pump but as an expander (work machine) and the pneumohydraulic cached energy with high efficiency back into mechanical energy
  • the gas compression heat taken up in the fluid is withdrawn from the circuit at each power stroke via coolers (3 and 4).
  • the caching of mechanical energy over relatively short time intervals can be seen in a further technical use of the pulsator principle according to the invention isothermal air compressor and Compressed air storage are formed.
  • the pulsator bags are not hermetically sealed but periodically whenever the fluid exerts no pressure on them, by means of an auxiliary pump with ambient air at atmospheric pressure filled.
  • the fluid which is ideally water for this application, compresses the air in the Pulsatorenlessnessn in the next working cycle, which flows through a check valve in a compressed air reservoir.
  • the heat released to the water during compression via the pulsator surface is recooled via a cooler (active or passive) when the water is pumped back into the now sucking instead of pushing pump.
  • the arrangement can be expanded in the following manner into an isothermal working machine supplied with energy from the compressed air reservoir: as is apparent from FIG. 15a, compressed air is periodically passed from the reservoir into the pulsator bag via a controlled valve.
  • the water which in this case absorbs the cold generated during the expansion of the compressed air, is reheated via a heat exchanger and makes the working as an expander actuator perform mechanical work.
  • the actuator motor converts its oscillating motion via a crankshaft into rotating energy.
  • a flywheel to equalize the energy output completes the arrangement.
  • Compressed air accumulators with a nominal pressure of> 300 bar which can be easily realized in the current state of the art with lightweight, fiber-wrapped polymer accumulators, achieve stored energy densities of> 200 Wh kg during isothermal loading and unloading. They are better than today's favored Li-ion batteries (150Wh / kg) and have in comparison to these major advantages: no strategically important material components - only water, air, steel, commercial, recyclable membrane
  • the driving energy of the isothermal compressor may originate, for example, from photovoltaic modules.
  • the mechanical energy which can then be withdrawn from the compressed air reservoir via the actuator if necessary has further specific advantages: no inverters are required for generating alternating andpower current - the rotating generator generates this automatically; If required, mechanical energy can be extracted from the unit directly.
  • Fis.16 is shown schematically how solar concentrators (1) on the roof of the garage drive the described isothermal compressor (3) and large, fixed compressed air reservoirs (4) fill.
  • vehicle to be refueled are smaller compressed air reservoirs (preferably formed as structural elements lightweight fiber composite container). These vehicle accumulators can be refueled very quickly with compressed air via compressed air lines from the fixed accumulators (5)
  • Vehicle memories are associated with isothermal actuators as shown in Fig.16b. These operate preferably four integrated in the vehicle wheels, individually controllable hydraulic motors.
  • a key feature of the membrane Stirling engine presented here (which the Applicant plans to market as a "pulsator machine") is that the heat exchange and displacer bodies installed in the transfer fluid, ie the pulsators, consist of elastic, deformable membrane structures.
  • Membrane can serve in the sense of the present patent application in particular a suitable single or multilayer film.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Separation Using Semi-Permeable Membranes (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention concerne un moteur Stirling à membrane comportant un gaz de travail, avec une partie chaude et une partie froide. Le gaz de travail du moteur Stirling se trouve à la fois dans sa partie chaude et dans sa partie froide dans des gaines de membrane qui présentent deux extrémités et qui sont hermétiquement fermées à une extrémité et ouvertes à l'autre extrémité. Lesdites gaines débouchent, avec leur extrémité ouverte, en fermant de manière étanche, dans l'espace chaud ou l'espace froid d'une caisse de régénérateur.
EP16736768.9A 2015-03-13 2016-03-14 Moteur stirling à membrane Active EP3280900B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP21182490.9A EP3919729A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP21182497.4A EP3919730A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015003147 2015-03-13
PCT/DE2016/000108 WO2016146096A2 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP21182497.4A Division EP3919730A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP21182490.9A Division EP3919729A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Publications (2)

Publication Number Publication Date
EP3280900A2 true EP3280900A2 (fr) 2018-02-14
EP3280900B1 EP3280900B1 (fr) 2021-06-30

Family

ID=56403921

Family Applications (3)

Application Number Title Priority Date Filing Date
EP16736768.9A Active EP3280900B1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP21182490.9A Pending EP3919729A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP21182497.4A Pending EP3919730A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP21182490.9A Pending EP3919729A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane
EP21182497.4A Pending EP3919730A1 (fr) 2015-03-13 2016-03-14 Moteur stirling à membrane

Country Status (9)

Country Link
US (1) US11047335B2 (fr)
EP (3) EP3280900B1 (fr)
CN (1) CN107532541B (fr)
DE (1) DE112016001190A5 (fr)
ES (1) ES2891796T3 (fr)
MA (1) MA41914A (fr)
MX (1) MX2017011696A (fr)
PT (1) PT3280900T (fr)
WO (1) WO2016146096A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11035596B2 (en) * 2019-07-12 2021-06-15 King Abdulaziz University Solar energy powered Stirling duplex machine with thermal storage tank
CN111692056A (zh) * 2020-07-01 2020-09-22 中国石化集团胜利石油管理局有限公司新能源开发中心 一种地热发电装置
WO2022195556A1 (fr) 2021-03-19 2022-09-22 Hurst Ronald Alan Moteurs thermiques et pompes à chaleur dotées de séparateurs et déplaceurs
WO2023249505A2 (fr) * 2022-06-21 2023-12-28 Arpad Torok Nouveau procédé pour les compression et détente isothermes de gaz et dispositifs pour son application

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US1007422A (en) * 1911-02-16 1911-10-31 Otto Berger Lubricator for elevator-guides.
FR1007422A (fr) * 1948-12-27 1952-05-06 Philips Nv Machine à gaz chaud
US3478695A (en) * 1968-02-13 1969-11-18 Mc Donnell Douglas Corp Pulsatile heart pump
US3597766A (en) * 1968-07-11 1971-08-10 Atomic Energy Commission Artificial heart pumping system powered by a modified stirling cycle engine-compressor having a freely reciprocable displacer piston
FR2417653A1 (fr) * 1978-02-15 1979-09-14 Cloup Jean Capsule isotherme et machines thermiques realisees a partir de ladite capsule
US4490974A (en) * 1981-09-14 1985-01-01 Colgate Thermodynamics Co. Isothermal positive displacement machinery
GB2296047B (en) * 1994-12-15 1998-04-08 Jonathan Maxwell Boardman Diaphragm stirling engine
US6591609B2 (en) * 1997-07-15 2003-07-15 New Power Concepts Llc Regenerator for a Stirling Engine
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US6725670B2 (en) * 2002-04-10 2004-04-27 The Penn State Research Foundation Thermoacoustic device
US7067933B2 (en) * 2002-11-12 2006-06-27 Terry Edgar Bassett Waste oil electrical generation system
JP4867635B2 (ja) * 2006-12-20 2012-02-01 有富 奥野 スターリングエンジン用体積変動部材
CN101498290A (zh) * 2009-02-20 2009-08-05 武汉工程大学 外激励双驱动行波热声热机
DE102010023672A1 (de) * 2010-06-12 2011-12-15 Forschungszentrum Jülich GmbH Diskontinuierlicher Schubantrieb und Stirlingmotor
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CN103629009B (zh) * 2013-11-26 2015-04-22 万斌 一种基于液体放射性废料浓缩物的斯特林热机

Also Published As

Publication number Publication date
CN107532541A (zh) 2018-01-02
WO2016146096A9 (fr) 2017-04-06
EP3919729A1 (fr) 2021-12-08
PT3280900T (pt) 2021-10-01
WO2016146096A2 (fr) 2016-09-22
MX2017011696A (es) 2018-06-15
EP3919730A1 (fr) 2021-12-08
DE112016001190A5 (de) 2017-11-30
US11047335B2 (en) 2021-06-29
EP3280900B1 (fr) 2021-06-30
WO2016146096A3 (fr) 2016-12-08
US20180119638A1 (en) 2018-05-03
CN107532541B (zh) 2020-11-20
ES2891796T3 (es) 2022-01-31
MA41914A (fr) 2018-02-13

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