WO2018114274A1 - Dispositif de dosage d'un combustible gazeux vers un injecteur - Google Patents

Dispositif de dosage d'un combustible gazeux vers un injecteur Download PDF

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Publication number
WO2018114274A1
WO2018114274A1 PCT/EP2017/081035 EP2017081035W WO2018114274A1 WO 2018114274 A1 WO2018114274 A1 WO 2018114274A1 EP 2017081035 W EP2017081035 W EP 2017081035W WO 2018114274 A1 WO2018114274 A1 WO 2018114274A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
gas
control
shut
Prior art date
Application number
PCT/EP2017/081035
Other languages
German (de)
English (en)
Inventor
Dirk Vahle
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to CN201780079114.1A priority Critical patent/CN110114568A/zh
Publication of WO2018114274A1 publication Critical patent/WO2018114274A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663—Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0673—Valves; Pressure or flow regulators; Mixers
    • F02D19/0678—Pressure or flow regulators therefor; Fuel metering valves therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/0663—Details on the fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02D19/0684—High pressure fuel injection systems; Details on pumps, rails or the arrangement of valves in the fuel supply and return systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
    • F02D19/10—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels peculiar to compression-ignition engines in which the main fuel is gaseous
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

Definitions

  • the invention relates to a device for metering a gaseous fuel to an injector, in particular a gas-powered internal combustion engine, wherein the device has at least one valve.
  • Such a device for metering a gaseous fuel to an injector of a gas-fueled internal combustion engine is known from CA 2 884 945 A1.
  • This gas-powered internal combustion engine has an injector designed as a dual-fuel fuel injector, with which a diesel fuel and a gaseous fuel can be introduced into a combustion chamber of the internal combustion engine.
  • the device has at least one valve for each fuel branch, with which the respective fuel supply to the dual-fuel fuel injector can be adjusted.
  • the invention has for its object to provide a device for metering a gaseous fuel to an injector of a particular gas-powered internal combustion engine, in which an over the prior art, especially in terms of their construction effort improved means for metering the gaseous fuel is provided to the injector.
  • the device is a pressure control unit with a shut-off valve, a pressure control valve and a shut-off valve, and that the shut-off valve, the pressure control valve and the shut-off valve is designed as a unit functional unit.
  • This pressure control unit with the three valves allows an individual adjustment of the gaseous fuel to be supplied to the respective combustion chamber of the internal combustion engine.
  • the shut-off valve By means of the shut-off valve, the gas flow to the injector can be completely shut off, while in the pressure control valve, the gas pressure of the gas flow can be adjusted to the injector.
  • the injector is designed to introduce the gaseous fuel into a combustion chamber of the internal combustion engine.
  • the gas pressure prevailing in the structural unit can be lowered to a low pressure level.
  • the assembly accordingly comprises the previously illustrated three valves and can be configured in particular more compact and also more reliable than the corresponding individual valves. In addition, the manufacturing costs can be reduced.
  • the unit has a common actuator for the shut-off valve, the pressure control valve and the shut-off valve. This refinement also contributes to a compact construction of the structural unit and thereby enables reliable control of the gaseous fuel.
  • the actuator is an electro-hydraulic and / or electro-pneumatic actuator. These are the preferred embodiments, but in principle also other controllers come into consideration here.
  • a hydraulic flow is adjusted by an electric actuator.
  • the hydraulic fluid may be, for example, a fuel, in particular diesel fuel.
  • the actuator is a diesel pressure control valve. This embodiment is the most preferred embodiment.
  • the assembly on a control valve body, a gas valve body and a gas valve body cover all the components forming the aforementioned valves can be integrated in these housing components.
  • the actuator is mounted on the control valve body, and dominated by the actuator control chamber is adjacent to a pressure plate inserted into the gas valve body of a seal separately.
  • the attachment or integration of the actuator on or in the control valve body contributes to a further increase in the compactness of the assembly thus formed and its construction cost.
  • the pressure difference at the seal is small due to the configuration of the device which is specified and explained below, and is only 10 bar to 20 bar, for example. Because of this low pressure difference, it is possible to use a seal in the form of a metal corrugated bellows for media separation of the operating materials, a first operating medium pressure being present on the corrugated bellows and a second operating medium pressure being present on the outside.
  • the advantage of a metallic bellows is an absolute gas tightness and the possibility of applying a defined biasing force by its elasticity or bias between adjacent components. This eliminates a separate biasing spring.
  • the seal can also be designed as a conventional membrane, preferably in the form of a flat membrane, wherein the possible lower diffusion of the possible pressure results in a possible diffusion of pending gaseous or liquid
  • the pressure plate cooperates with a control piston guided in the gas valve body.
  • the control piston is as separate
  • This stepped piston is easy to produce, for example, as a rotating part and has a low mass at a planned slim diameter.
  • the control piston has a further development of the invention, an annular stroke stop and opposite to a contact surface adjacent to the pressure plate to a pressure surface. Such a trained control piston is easy to manufacture.
  • the control piston forms a guide for a sealing sleeve.
  • the sealing surface on the control piston in the region between the contact surface to the pressure plate and the stroke stop is axially movable by the length of the control piston by a defined amount is less than the length of the control piston between the contact surface and the stroke stop.
  • the sealing sleeve hubanschlags briefly a cooperating in a sealing seat surface in the gas valve body sealing seat.
  • the sealing sleeve thus formed is also in turn easily produced, for example, as a rotating part and also has a low mass due to its slim design.
  • the attacking friction forces consisting of sliding friction and static friction, low and thus the adjustment forces required for adjusting are also reduced. This has the advantage that only to overcome the frictional forces less force to actuate ultimately the entire device must be applied.
  • the pressure surface of the control piston cooperates with a high pressure piston of a high pressure valve. This interaction is ultimately determined by the adjustment of the printing plate.
  • shut-off valve and the pressure control valve are formed by the high-pressure valve.
  • FIG. 1 shows a schematic representation of a gas system and a diesel fuel system, which interact together with an injector
  • Figure 2 is an illustration of a pressure control unit of a gas system with a
  • FIG. 3 shows a representation of a pressure control unit of a gas system with a
  • shut-off valve a pressure control valve and a shut-off valve, which together form a second embodiment of a structural unit.
  • FIG. 1 shows a schematic representation of a gas system and a diesel fuel system, both of which interact with an injector 1.
  • the aforementioned systems or components are part of a gas-powered internal combustion engine, wherein by means of the injector 1 in a combustion chamber of the internal combustion engine fuel gas and diesel can be introduced to operate the internal combustion engine. In the combustion chamber burn the fuel gas and / or the diesel with the addition of incorporated Brennluit generating power delivered to a crankshaft work.
  • the internal combustion engine is preferably installed in a vehicle and / or a machine for operating the vehicle or the machine.
  • the diesel fuel system is designed, for example, as a common rail system and has a diesel fuel tank 2, in which fuel is stored in the form of diesel, which is conveyed by a high-pressure diesel pump 3 into a high-pressure diesel accumulator 4.
  • diesel is stored under a pressure of, for example, up to 1000 bar (100 MPa), wherein the pressure in the high-pressure diesel accumulator 4 is set or adjusted for example by a diesel pressure control valve 5 to the aforementioned pressure.
  • the injector 1 is connected to the high-pressure diesel accumulator 4 via a high-pressure diesel line 6 and the injector 1 has an internal diesel control device for determining the amount of diesel injected into the combustion chamber by the injector 1.
  • the injector 1 further has a diesel return line 7, which finally ends in the diesel fuel tank 2. det. Furthermore, the high-pressure diesel accumulator 4 is connected via a diesel high pressure line 6a with an oil pressure valve designed as a diesel pressure control valve 8, which is used to control a pressure control unit of the gas system represented by a dashed border and thus is an essential component of the pressure control unit thus formed.
  • the pressure control unit consists of a shut-off valve 9, a pressure control valve 10 and a shut-off valve 11 for the fuel gas and the diesel pressure control valve 8.
  • the shut-off valve 9 and the pressure control valve 10 thereby form a high-pressure valve. With the diesel pressure control valve 8, the aforementioned three valves are controlled, with details thereof will be explained in more detail below.
  • the gas system has a gas tank 12, in which the fuel gas is stored and wherein a high-pressure gas pump 13 promotes fuel gas in a buffer memory 14.
  • the pressure control unit consisting of the diesel pressure control valve 8, the shut-off valve 9, the pressure control valve 10 and the shut-off valve 11 is connected or downstream of this.
  • the pressure control valve 10 and the shut-off valve 9 are connected in series and connect the buffer memory 14 with a high-pressure accumulator 15, which in turn is connected via a high-pressure line to the injector 1 designed as Zweistoffinjektor.
  • the arrangement of the pressure regulating valve 10 and the shut-off valve 9 may also be reversed.
  • the shut-off valve 11 connects a connected to the high-pressure accumulator 15 gas outlet 27 from the pressure control unit in turn with the gas tank 12th
  • Pressure control valve 10 and the shut-off valve 11 is described in more detail in two embodiments.
  • the pressure control unit is configured as a functional unit forming a structural unit and has a control valve body 16, a gas valve body 17 and a gas valve body cover 18.
  • the diesel pressure control valve 8 is attached to the control valve body 16 and adjusts the fuel pressure in a control room 19.
  • a predetermined amount of diesel is initially supplied to the control chamber 19 via a diesel access 20 (see also FIG. 1) connected to the diesel high-pressure line 6 a and a diesel oil nozzle 21.
  • From the diesel pressure control valve 8 is then determined from the control chamber 19 amount of diesel for adjusting the fuel pressure is determined or set.
  • a connection between the control chamber 19 and a diesel outlet 22 (see also FIG. 1) is established or set by the diesel pressure control valve 8.
  • the diesel outlet 22 is connected to the diesel fuel tank 2 via the diesel return line 7.
  • the control chamber 19 is embedded in the gas valve body 17 and adjoins the end face of a pressure plate 23, which in turn cooperates with a formed as a corrugated bellows 24 a seal.
  • the bellows 24a is tightly connected to the outer periphery of the pressure plate 23, for example, welded, and opposite with a
  • the control chamber 19 extends - except for a small annular stop surface in the control valve body 16 - over almost the entire, the control chamber 19 facing end face of the pressure plate 23 and is connected to a corrugated bellows 24 a surrounding annular control chamber 19 a.
  • the control chamber 19a essentially allows only the unimpeded change in length of the bellows 24a with an adjustment of the pressure plate 23.
  • the bellows also assumes a spring action, which presses the pressure plate 23 in the direction of the control chamber 19.
  • the pressure plate 23 requires no machined precise support geometry and a risk of damage to the bellows due to material defects or
  • a gas control pressure chamber 26 is formed, which is throttle-free connected to the gas outlet 27. This throttle-free connection is the undisturbed adjustment of the
  • Pressure plate 23 and further components explained below.
  • a control piston 28 In the gas control pressure chamber 26 projecting a control piston 28 is guided axially movable in a recessed into the gas valve body 17 guide 29.
  • the control piston 28 is designed as a stepped piston and accordingly has an annular stroke stop 30.
  • the stroke stop 30 forms a stop for a sealing sleeve 31, which is pushed onto the control piston 28 and axially displaceable in relation to the control piston 28 on this.
  • the sealing sleeve 31 is pressed by a compression spring 32, which is supported on the pressure plate 23, with a sealing seat 33 against a sealing seat surface 34 in the gas valve body 17. presses if this allows the stroke stop 30 by adjusting the control piston in the direction of the gas valve body cover 18.
  • the control piston 28 has, opposite to the stroke stop 30, a pressure surface 35 cooperating with the pressure plate 23. As the pressure in the control cavity 19 increases, the pressure plate 23 becomes increasingly to the right in the direction of the
  • Gas valve body 18 adjusted and thus simultaneously displaces the control piston 28 in the direction of the gas valve body cover 18.
  • the sealing sleeve 31 is simultaneously moved to the right by the action of the compression spring 32 until the sealing seat 33 engages in the sealing seat surface 34.
  • a flow connection between the gas outlet 27 and a gas outlet connection 36 is open (see also FIG. 1), which is connected to a gas outlet line 37 cooperating with the sealing seat surface 34. Only when this connection is closed, the control function of the pressure control valve 10 is initiated.
  • control piston 28 is displaced with an end face 38 opposite to the pressure surface 35 to the right in the direction of the gas valve body cover 18 until the contact surface 38 comes to a high pressure piston 39 of the high pressure valve, which forms the check valve 9 and the pressure control valve 10 to the plant.
  • the high pressure piston 39 is to the right to a
  • the high pressure piston 39 has a high pressure piston sealing surface 41, which cooperates in the closed state of the high pressure valve with a sealing surface in a high pressure body 42.
  • the contact surface 38 pushes the high-pressure piston 39 to the right, the high-pressure piston sealing surface 41 is pressed out of the sealing surface in the high-pressure body 42 and gas flows from the gas inlet according to the adjustment into the gas outlet 27. During this phase, the connection to the gas shut-off port 36 is blocked.
  • control piston 28 is again adjusted so far to the left in the direction of the control chamber 19 that the high-pressure piston 39 is moved from the gas pressure in the gas inlet 40 and supported by a high-pressure piston closing spring 43 again so far to the left until the high-pressure piston sealing surface 41 rests in the sealing surface in the high-pressure body 42 and thus the connection from the gas inlet 40 to the gas outlet 27 is closed.
  • the sealing sleeve 31 is lifted with the sealing seat 33 from the sealing seat surface 34 and made a connection between the gas outlet 27 and the Gasabberichtan gleich 36. This further lowers the pressure in the system.
  • FIG. 3 corresponds functionally to that of Figure 2, in which case a membrane 24b is clamped as a seal between the control valve body 16 and the gas valve body 17, the end face of the pressure plate 23.
  • a pressure plate spring 44 is then additionally provided which presses the pressure plate 23 to the left in the direction of the control chamber 19 instead of the corrugated bellows.
  • This pressure plate spring 44 may in principle also be present in the embodiment according to FIG.
  • no control chamber 19a according to FIG. 1 is present, but rather this space is part of the gas control pressure chamber 26.
  • the diesel pressure control valve 8 is activated and lowers the control pressure in the control chamber 19 via the control of diesel into the diesel outlet 22. Due to the thus changing force conditions on the pressure plate 23, this moves - possibly supported by the force of the pressure plate spring 44 - toward the control chamber 19.
  • the control piston 28 and the high pressure piston 39 is the first closed between the sealing seat 33 and the sealing seat surface 34 formed flow connection. Immediately thereafter opens - depending on the distance of the contact surface 38 to the high-pressure piston 39, the flow connection between the gas inlet 40 and the gas outlet 27.
  • a leakage amount from the gas outlet 27 to the gas discharge connection 37 can flow off via a guide 45 of the sealing sleeve 31 on the control piston 28.
  • the game of the guide 45 should be low and, for example, in the order of 1 to 10 ⁇ .
  • the compression spring 32 is clamped between the sealing sleeve 31 and the pressure plate 23 and holds the sealing sleeve 31 and the control piston 28 in the pressureless state in a defined starting position. From a functional point of view, the
  • Compression spring 32 are also removed.
  • a pressure stage over the diameter Dl and D2 is incorporated in the control piston 28.
  • the pressure stage must fulfill the condition Dl ⁇ D2.

Abstract

L'invention concerne un dispositif de dosage d'un combustible gazeux vers un injecteur (1), en particulier d'un moteur à combustion interne fonctionnant au gaz, ledit dispositif comprenant au moins une soupape et l'injecteur (1) servant à introduire le combustible gazeux dans une chambre de combustion du moteur à combustion interne. Le but de l'invention est de fournir un dispositif de dosage du combustible gazeux vers l'injecteur (1) qui soit amélioré par rapport à l'état de la technique, en particulier du point de vue de sa complexité de construction. Cet but est atteint par le fait que le dispositif est une unité de régulation de pression munie d'une soupape d'arrêt (9), d'une soupape régulatrice de pression (10) et d'une soupape de décharge (11), et que la soupape d'arrêt (9), la soupape régulatrice de pression (10) et la soupape de décharge (11) forment un module.
PCT/EP2017/081035 2016-12-20 2017-11-30 Dispositif de dosage d'un combustible gazeux vers un injecteur WO2018114274A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201780079114.1A CN110114568A (zh) 2016-12-20 2017-11-30 用于将气态燃料配量给喷射器的装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016225580.0A DE102016225580A1 (de) 2016-12-20 2016-12-20 Einrichtung zur Zumessung eines gasförmigen Brennstoffs zu einem Injektor
DE102016225580.0 2016-12-20

Publications (1)

Publication Number Publication Date
WO2018114274A1 true WO2018114274A1 (fr) 2018-06-28

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Application Number Title Priority Date Filing Date
PCT/EP2017/081035 WO2018114274A1 (fr) 2016-12-20 2017-11-30 Dispositif de dosage d'un combustible gazeux vers un injecteur

Country Status (3)

Country Link
CN (1) CN110114568A (fr)
DE (1) DE102016225580A1 (fr)
WO (1) WO2018114274A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018210899A1 (de) * 2018-07-03 2020-01-09 Robert Bosch Gmbh Gasdruckregler zum Regeln eines Gasdrucks
CN113561763A (zh) * 2020-04-28 2021-10-29 未势能源科技有限公司 燃料处理单元和具有它的燃料储存和供应系统

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3221374A1 (de) * 1982-06-05 1983-12-22 Motoren-Werke Mannheim AG vorm. Benz Abt. stationärer Motorenbau, 6800 Mannheim Einrichtung zur einspritzung von zuendkraftstoff einerseits und hauptkraftstoff anderseits fuer dieselmotoren
US4693267A (en) 1986-03-31 1987-09-15 Tescom Corporation Self-venting pressure reducing regulator
CA2441641A1 (fr) * 2003-09-23 2004-03-01 Westport Research Inc. Circuit d'alimentation en combustible gazeux a haute pression pour moteur a combustion interne et methode de scellement des raccords entre les composants pour empecher les fuites d'un combustible gazeux a haute pression
EP2602525A1 (fr) * 2010-08-06 2013-06-12 Kawasaki Jukogyo Kabushiki Kaisha Soupape de régulation de pression de gaz
US20140116523A1 (en) * 2012-10-31 2014-05-01 Caterpillar Inc. Fuel system having dual fuel pressure regulator
CA2884945A1 (fr) 2015-03-13 2015-05-15 Michael C. Wickstone Injecteur pour carburant gazeux a actionnement hydraulique

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006021736A1 (de) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Kraftstoffinjektor mit druckausgeglichenem Steuerventil
ITMO20070004A1 (it) * 2007-01-11 2008-07-12 Landi Renzo Spa Regolatore di pressione
CA2633846C (fr) * 2008-06-27 2009-12-29 Westport Power Inc. Soupape d'injection de carburant et methode de co-injection d'un liquide et d'un carburant gazeux dans la chambre de combustion d'un moteur a combustion interne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3221374A1 (de) * 1982-06-05 1983-12-22 Motoren-Werke Mannheim AG vorm. Benz Abt. stationärer Motorenbau, 6800 Mannheim Einrichtung zur einspritzung von zuendkraftstoff einerseits und hauptkraftstoff anderseits fuer dieselmotoren
US4693267A (en) 1986-03-31 1987-09-15 Tescom Corporation Self-venting pressure reducing regulator
CA2441641A1 (fr) * 2003-09-23 2004-03-01 Westport Research Inc. Circuit d'alimentation en combustible gazeux a haute pression pour moteur a combustion interne et methode de scellement des raccords entre les composants pour empecher les fuites d'un combustible gazeux a haute pression
EP2602525A1 (fr) * 2010-08-06 2013-06-12 Kawasaki Jukogyo Kabushiki Kaisha Soupape de régulation de pression de gaz
US20140116523A1 (en) * 2012-10-31 2014-05-01 Caterpillar Inc. Fuel system having dual fuel pressure regulator
CA2884945A1 (fr) 2015-03-13 2015-05-15 Michael C. Wickstone Injecteur pour carburant gazeux a actionnement hydraulique

Also Published As

Publication number Publication date
CN110114568A (zh) 2019-08-09
DE102016225580A1 (de) 2018-06-21

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