WO2017005177A1 - Coupleur hydraulique de type boîtier composite, et démarreur - Google Patents

Coupleur hydraulique de type boîtier composite, et démarreur Download PDF

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Publication number
WO2017005177A1
WO2017005177A1 PCT/CN2016/088741 CN2016088741W WO2017005177A1 WO 2017005177 A1 WO2017005177 A1 WO 2017005177A1 CN 2016088741 W CN2016088741 W CN 2016088741W WO 2017005177 A1 WO2017005177 A1 WO 2017005177A1
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Prior art keywords
gear
input
output
carrier
coupled
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Ceased
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PCT/CN2016/088741
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English (en)
Chinese (zh)
Inventor
吴志强
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Individual
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Individual
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Priority to CN201680039168.0A priority Critical patent/CN108243617A/zh
Publication of WO2017005177A1 publication Critical patent/WO2017005177A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the present invention is in the field of fluid couplings and starting, and more particularly, it is a composite tank type fluid coupling and starter for various ground vehicles, ships, railway locomotives, and machine tools.
  • the fluid coupling is designed according to the principles of hydrostatics, etc. It can transmit little power and is not efficient; in addition, the cost is high.
  • the invention overcomes the deficiencies of the prior art, and provides a composite box type fluid coupling and a starter which prolong the service life of the engine, has a simple structure, is convenient to operate, has low cost, is energy-saving and high-efficiency.
  • a composite tank type fluid coupling and starter comprising an input shaft (1), an input gear (3), an input gear pair (4), an output shaft (5), an empty gear mechanism (6), a box Body fluid coupling (7), fixed one-way clutch (8), starter gear pair (9), overrunning clutch (10), starting gear pair (11), electromagnetic clutch (12), coupling shaft (13)
  • the input shaft (1) and the output shaft (5) are provided with a planetary gear (20), an input carrier (21), an input gear (22), an output large ring gear (23), and an input ring gear ( 24), fixed carrier (25), output ring gear (26), coupled input planet carrier (27), fixed gear (28), output gear (29), input shaft (1) and start gear pair (11)
  • the output gear (112) and the input end (101) of the overrunning clutch (10) are coupled, the output end (102) of the overrunning clutch (10) and the input gear (22) and the output gear (92) of the starter gear pair (9)
  • the output gear (92) of the starter gear pair (9) cooperates with the input gear (91) of the starter
  • the planetary gear (20) coupled to the input carrier (27) cooperates with the fixed gear (28) and the output gear (29) to fix the carrier (25), the fixed gear (28) and the fixed one-way clutch ( 8)
  • the input end (81) is coupled to the stationary element
  • the output gear (29) is coupled to the input end (71) of the tank-type fluid coupling (7)
  • the end (82) and the input planet carrier (21) is coupled.
  • a composite tank type fluid coupling comprising an input shaft (1), a one-way clutch (3), a tank type fluid coupling (4), an output shaft (5), an input gear pair (6), The output gear pair (7) and the output gear pair (8) are coupled, and a planetary gear (20), an input small ring gear (21), and an input large tooth are disposed between the input shaft (1) and the output shaft (5).
  • a ring 22
  • an output planet carrier 23
  • an output gear 24
  • a fixed planet carrier 25
  • an input gear 26
  • an input planet carrier 27
  • an input pinion 28
  • the output ring gear (29) is coupled to the input small ring gear (21) and the input gear (81) of the output gear pair (8), and the output gear (82) of the output gear pair (8) is small with the input.
  • the gear (28) is coupled, and the input small ring gear (21) cooperates with the input large ring gear (22) and the output planet carrier (23) through the planetary gear (20) on the output carrier (23), and outputs the planet carrier ( 23) coupled to the input gear (71) of the coupled output gear pair (7), coupled to the output gear (72) of the output gear pair (7) and the input gear (27) and the input gear of the input gear pair (6) (61)
  • the coupling gear (62) of the input gear pair (6) is coupled to the input gear (26), and the input gear (26) is fixed by the planetary gear (20) and the output gear (24) fixed on the carrier (25).
  • the planet carrier (25) cooperates with each other, the fixed carrier (25) and the input end (31) of the one-way clutch (3) are fixed to the fixed component, and the output gear (24) and the box type fluid coupling (4)
  • the input end (41) is coupled
  • the output end (42) of the tank type fluid coupling (4) is coupled with the output end (32) of the one-way clutch (3) and the input large ring gear (22), and the input carrier (27)
  • the planetary gear (20) and the input through it Wheel (28), an output ring gear (29) cooperate with each other, the output ring gear (29) and the output shaft (5) is coupled.
  • the elements that need to be coupled, and the elements that are separated by several other elements, can be connected to or through several other elements by means of a hollow or a coupling frame; when the coupled elements are gears or ring gears, Then, meshing or coupling; the gear ratio of each gear pair and the shifting mechanism is designed according to actual needs.
  • the tank type fluid coupling can be replaced by a double pump wheel hydraulic torque converter.
  • the air-locking mechanism can select a clutch instead.
  • the present invention When the present invention is applied to a vehicle, it is possible to automatically change the output torque and the speed change depending on the magnitude of the resistance that the vehicle is subjected to while traveling.
  • the invention enables the engine and the starter to operate in the region of the tempering speed, that is, the engine operates in a range of very small pollution discharge speeds, thereby avoiding the engine discharging a large amount of exhaust gas during idle speed and high speed operation, thereby reducing the number of exhaust gases.
  • the emission of exhaust gas is conducive to protecting the environment;
  • the invention can utilize the effect of internal speed difference to buffer and overload protection, which is beneficial to prolonging the service life of the engine and the drive train and the starter.
  • speed up which is beneficial to improve the driving performance of the vehicle;
  • the invention makes the input power uninterrupted, can ensure the vehicle has good acceleration and high average vehicle speed, reduces the wear of the engine, prolongs the overhaul interval mileage, and is beneficial to improving productivity;
  • the invention reduces the transmission mechanism of the current starter machine and reduces the manufacturing cost. After the engine is started, only the braking and separating measures of the starting motor are required to stop the transmission.
  • the present invention is a composite type tank type fluid coupling and starter for various ground vehicles, ships, railway locomotives, and machine tools.
  • FIG. 1 is a structural view of a first embodiment of the present invention
  • FIG. 2 is a structural diagram of a second embodiment of the present invention.
  • connection between the two elements is indicated by a thick solid line, and the thin solid line indicates that the two elements can be rotated relative to each other.
  • Embodiment 1 is a diagrammatic representation of Embodiment 1:
  • a composite tank type fluid coupling and a starter include an input shaft 1, an input gear 3, an input gear pair 4, an output shaft 5, an idle gear mechanism 6, and a tank type liquid.
  • the output gear 112 of the start gear pair 11 and the input end 101 of the overrunning clutch 10 are coupled, and the output end 102 of the overrunning clutch 10 is coupled to the input gear 22 and the output gear 92 of the starter gear pair 9, the output gear 92 of the starter gear pair 9
  • the input gear 91 of the starter gear pair 9 cooperates with each other.
  • the input gear 22 cooperates with the input carrier 21 and the output large ring gear 23 through the planetary gear 20 on the input carrier 21, and outputs the large ring gear 23 and the input tooth.
  • Ring 24 meshes, coupling shaft 13 Coupling with the input ring gear 24, the input end 121 of the electromagnetic clutch 12, and the input gear 41 of the input gear pair 4, the output gear 42 of the input gear pair 4 is coupled to the input end 61 of the neutral gear mechanism 6, the idle gear mechanism 6
  • the output end 62 is coupled to the output shaft 5, and the output end 122 of the electromagnetic clutch 12 is coupled to the input gear 111 of the start gear pair 11.
  • the input ring gear 24 passes through the planetary gear 20 on the fixed carrier 25 and the fixed carrier 25, and the output ring gear.
  • the output ring gear 26 meshes with the input gear 3
  • the input gear 3 is coupled with the coupling input carrier 27, and the planetary gear 20 coupled to the input carrier 27 cooperates with the fixed gear 28 and the output gear 29 to cooperate with each other.
  • the fixed planet carrier 25, the fixed gear 28 and the input end 81 of the fixed one-way clutch 8 are coupled to a fixed element
  • the output gear 29 is coupled to the input 71 of the tank-type fluid coupling 7, the tank-type fluid coupling 7
  • the output end 72 and the output end 82 of the fixed one-way clutch 8 are coupled to the input carrier 21.
  • the idle gear mechanism 6 Before the engine is started, the idle gear mechanism 6 is disengaged and the electromagnetic clutch 12 is engaged.
  • the input power of the starter is transmitted to the input gear 22 via the starter gear pair 9, and the input gear 22 is transmitted to the output through the planetary gear 20 on the input carrier 21.
  • the ring gear 23, the output large ring gear 23 is transmitted to the input shaft 1 through the input ring gear 24, the coupling shaft 13, the electromagnetic clutch 12 and the start gear pair 11, and is transmitted to the crankshaft of the engine, and the generated driving force is sufficient to overcome the engine starting resistance.
  • the input gear 22 transmits the power transmitted from the engine to the input shaft 1 and the overrunning clutch 12 through the planetary gear 20 input to the carrier 21, and is transmitted to the output.
  • the ring gear 23, the output large ring gear 23 is transmitted to the input ring gear 24, and the input ring gear 24 diverts the power transmitted thereto into two paths, one pass through the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6 to The output shaft 5 of the present invention; the other path is transmitted to the output ring gear 26 through the planetary gear 20 on the fixed carrier 25, and the output ring gear 26 is transmitted to the coupled input carrier 27 through the input gear 3, coupled to the input carrier 27 and passed
  • the planetary gear 20 on it is transmitted to the transmission
  • the output gear 29, the output gear 29 is transmitted to the input carrier 21 through the tank type fluid coupling 7, the power transmitted to the input carrier 21, and the power transmitted from the engine to the input gear 22 via the input shaft 1 and the overrunning clutch 10,
  • the planetary gear 20 on the input carrier 21 is transmitted to the output large ring gear 23, and the large ring gear 23 is outputted, and the repeated cycle of the shifting is continuously performed between the respective components, wherein the output of the tank type fluid coupling 7 is output.
  • the rotational speed continuously shifts steplessly as the input power and the running resistance change, so that the output rotational speed of the output large ring gear 23 also constantly changes, and through the input ring gear 24, the coupling shaft 13, the input gear pair 4, and the air
  • the gear shifting mechanism 6 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine power through the output shaft 5.
  • the torque on the input carrier 21, the output large ring gear 23, and the output shaft 5 varies with the change of the rotational speed thereof, and the lower the rotational speed, the transmission to the input carrier 21 and the output.
  • the idle gear mechanism 6 is disengaged, the electromagnetic clutch 12 is engaged, and the engine speed is zero.
  • the starter is started, the input power of the starter is transmitted to the input gear 22 through the starter gear pair 9, wherein Since no power flows into the input carrier 21 at this time, and the input end 81 of the fixed one-way clutch 8 is coupled to the fixed component, the steering is restricted, so that the input carrier 21 cannot rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input gear 22 is transmitted to the output large ring gear 23 through the planetary gear 20 input to the carrier 21, and the large ring gear 23 is output through the input ring gear 24, the coupling shaft 13, and the electromagnetic clutch. 12 and the starter gear pair 11 is transmitted to the input shaft 1 and then to the engine crankshaft.
  • the input power, input speed and load of the engine are unchanged, that is, the speed and torque of the input shaft 1 are constant.
  • the idle gear mechanism 6 is engaged, the electromagnetic clutch 12 is separated, and the output shaft 5 is rotated.
  • the input power of the engine is transmitted to the input gear 22 via the input shaft 1 and the overrunning clutch 10, wherein since no power flows into the input carrier 21 at this time, and the input end 81 of the fixed one-way clutch 8 is coupled to the fixed member,
  • the function of restricting the steering is such that the input carrier 21 cannot rotate opposite to the engine, and the rotational speed is zero.
  • the power transmitted to the input gear 22 is transmitted to the output through the planetary gear 20 input to the carrier 21.
  • the large ring gear 23, the output large ring gear 23 is transmitted to the input ring gear 24, and the input ring gear 24 diverts the power transmitted thereto into two paths, one pass through the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6.
  • the other path is transmitted to the output ring gear 26 through the planetary gear 20 on the fixed carrier 25, and the output ring gear 26 is transmitted to the joint through the input gear 3.
  • the input carrier 27 is coupled to the input carrier 27 and transmitted to the output gear 29 through the planetary gear 20 thereon.
  • the output gear 29 is transmitted to the input carrier 21 through the tank type fluid coupling 7 and transmitted to the input carrier 21.
  • the power and the power transmitted from the engine through the input shaft 1 and the overrunning clutch 10 to the input gear 22 are transmitted to the output large ring gear 23 through the planetary gear 20 on the input carrier 21, and the large ring gear 23 is output between the respective components.
  • the repeated cycle of the shifting is continuously performed, wherein the output rotational speed of the tank type fluid coupling 7 is continuously steplessly changed in accordance with the change in the running resistance, so that the output rotational speed of the output large ring gear 23 is also constantly changed.
  • the input ring gear 24, the coupling shaft 13, the input gear pair 4, and the idle gear mechanism 6 are transmitted to the output shaft 5 of the present invention, so that the torque of the output shaft 5 is reduced as the number of revolutions increases.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • a composite tank type fluid coupling includes an input shaft 1, a one-way clutch 3, a tank type fluid coupling 4, an output shaft 5, an input gear pair 6, and a coupling output gear.
  • Sub 7 , output gear pair 8, the input shaft 1 and the input A planetary gear 20, an input small ring gear 21, an input large ring gear 22, an output carrier 23, an output gear 24, a fixed carrier 25, an input gear 26, an input carrier 27, and an input pinion 28 are disposed between the output shafts 5.
  • the output ring gear 29 is coupled to the input small gear ring 21 and the input gear 81 of the output gear pair 8.
  • the output gear 82 of the output gear pair 8 is coupled to the input pinion 28, and the input small ring gear 21 is passed through the output carrier.
  • the planetary gear 20 on the 23 cooperates with the input large ring gear 22 and the output carrier 23, the output carrier 23 is coupled with the input gear 71 of the coupled output gear pair 7, and the output gear 72 of the output gear pair 7 is coupled to the input carrier. 27 and the input gear 61 of the input gear pair 6 are coupled, the output gear 62 of the input gear pair 6 is coupled to the input gear 26, and the input gear 26 is matched with the output gear 24 and the fixed carrier 25 by the planetary gear 20 on the fixed carrier 25.
  • the fixed carrier 25 and the input end 31 of the one-way clutch 3 are fixed to the fixed element, and the output gear 24 is coupled to the input 41 of the tank type fluid coupling 4, the output of the tank type fluid coupling 4 42 and one-way clutch Output 3 and an input terminal 32 coupled to the ring gear 22, input planet carrier 27 through the planetary gear 20 on the input pinion 28, output gear 29 cooperate with each other, the output gear 29 and the output shaft 5 is coupled.
  • the input small ring gear 21 and the input large ring gear 22 converge the respective power transmitted through the planetary gears 20 on the output carrier 23 to the output carrier 23, since the box type fluid coupling 4 is coupled to the input large ring gear 22. Therefore, the rotational speed of the input large ring gear 22 can be constantly changed in accordance with the change in the rotational speed of the tank type fluid coupling 4, so that the rotational speed of the output carrier 23 also changes.
  • the input power is split into two paths through the input shaft 1, one is transmitted to the input small ring gear 21, the other is transmitted to the input pinion 28 via the output gear pair 8, and the input small ring gear 21 passes the power transmitted thereto through the output carrier 23.
  • the upper planetary gear 20 merges with the output carrier 23, and the output carrier 23 is split into two paths by coupling the output gear pair 7, and is transmitted to the input carrier 27 at one time. At this time, the input carrier 27 and the input pinion 28 transmit The respective powers are converge to the output ring gear 29 through the planetary gears 20 on the input carrier 27, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing the external output of the engine power through the output shaft 5.
  • the power of the other path transmitted to the input gear 26 through the input gear pair 6 increases, and the input gear 26 passes through the planetary gear 20 on the fixed carrier 25.
  • the power is transmitted to the output gear 24, and the output gear 24 is transmitted to the input large ring gear 22 through the tank type fluid coupling 4, that is, the input power of the input large ring gear 22 is increased, and the small ring gear 21 is input.
  • the input large ring gear 22 converges the planetary gears 20 transmitted to the respective powers through the output carrier 23 to the output carrier 23, and the output carrier 23 repeats the above process to continuously change the rotational speed transmitted to the input carrier 27.
  • the input carrier 27 and the input pinion 28 converge the planetary gear 20 transmitted to the respective power through the input carrier 27 to the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing The power of the engine is externally output through the output shaft 5.
  • the rotational speed input to the carrier 27 varies with the input power or running resistance of the vehicle, and the lower the resistance, the higher the rotational speed transmitted to the input carrier 27.
  • the input power, the input rotational speed and the load of the engine are constant, that is, the rotational speed and torque of the input shaft 1 are constant, and before the vehicle starts, the rotational speed of the output shaft 5 is zero, and the input power of the engine passes through the input shaft 1
  • the split is two paths, one is transmitted to the input small ring gear 21, the other is transmitted to the input pinion 28 via the output gear pair 8, and the input small ring gear 21 converges the power transmitted thereto through the planetary gears 20 on the output carrier 23.
  • the output planet carrier 23 is split into two paths by coupling the output gear pair 7, one way to the input planet carrier 27, at this time, the input planet carrier 27 and the input pinion 28 merge the planetary gear 20 transmitted to the respective power through the input carrier 27 to the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention, thereby realizing the power of the engine. It is output to the outside through the output shaft 5.
  • the vehicle starts to accelerate.
  • the resistance of the output shaft 5 decreases, the other passes through the input gear.
  • the power delivered by the secondary 6 to the input gear 26 is increased, the input gear 26 transmits power to the output gear 24 via the planet gears 20 on the fixed planet carrier 25, and the output gear 24 passes through the tank-type fluid coupling 4
  • the input power to the input large ring gear 22, i.e., the input large ring gear 22, increases, and the input small ring gear 21, the input large ring gear 22, transmits the respective power through the planetary gear 20 on the output carrier 23.
  • the output carrier 23 repeats the above process, so that the rotational speed transmitted to the input carrier 27 is constantly changing, and the input carrier 27 and the input pinion 28 transmit the respective powers through the input carrier 27.
  • the planetary gear 20 merges with the output ring gear 29, and the output ring gear 29 is transmitted to the output shaft 5 of the present invention.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
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Abstract

L'invention concerne un coupleur hydraulique de type boîtier composite et un démarreur présentant ledit coupleur hydraulique de type boîtier composite ; un arbre d'entrée (1) est relié à une paire d'engrenages de démarrage (11) et à un embrayage à roue libre (10) ; l'embrayage à roue libre (10) est relié à un engrenage d'entrée (22) et à une paire d'engrenages de démarreur (9) ; une grande couronne de sortie (23) vient en prise avec une couronne d'entrée (24) ; un arbre de raccordement (13) est relié à la couronne d'entrée (24), à un embrayage électromagnétique (12) et à une paire d'engrenages d'entrée (4) ; la paire d'engrenages d'entrée (4) est reliée à un mécanisme de changement de vitesse nul (6) ; le mécanisme de changement de vitesse nul (6) est relié à un arbre de sortie (5) ; l'embrayage électromagnétique (12) est relié à la paire d'engrenages de démarrage (11) ; une couronne de sortie (26) s'engage avec un engrenage d'entrée (3) ; l'engrenage d'entrée (3) est connecté à un porte-satellites d'entrée de raccordement (27) ; un engrenage de sortie (29) est connecté à un coupleur hydraulique de type boîtier (7) ; le coupleur hydraulique de type boîtier (7) et un embrayage unidirectionnel fixe (8) sont raccordés à un porte-satellites d'entrée (21).
PCT/CN2016/088741 2015-07-07 2016-07-06 Coupleur hydraulique de type boîtier composite, et démarreur Ceased WO2017005177A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680039168.0A CN108243617A (zh) 2015-07-07 2016-07-06 一种复合型箱体式液力偶合器以及起动器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510389853.3A CN104976303B (zh) 2015-07-07 2015-07-07 一种复合型箱体式液力偶合器
CN201510389853.3 2015-07-07

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WO2017005177A1 true WO2017005177A1 (fr) 2017-01-12

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WO2018185267A1 (fr) 2017-04-06 2018-10-11 Novozymes A/S Compositions de nettoyage et leurs utilisations
WO2018185285A1 (fr) 2017-04-06 2018-10-11 Novozymes A/S Compositions de nettoyage et utilisations correspondantes
WO2018185269A1 (fr) 2017-04-06 2018-10-11 Novozymes A/S Compositions de nettoyage et leurs utilisations
WO2019154954A1 (fr) 2018-02-08 2019-08-15 Novozymes A/S Variants de lipase et compositions en comprenant

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CN107869562A (zh) * 2015-07-07 2018-04-03 广州市志变制能科技有限责任公司 一种复合型双泵轮液力变矩器

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CN104595437A (zh) * 2010-07-07 2015-05-06 吴志强 一种复合型无级变速器
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GB624858A (en) * 1942-01-09 1949-06-17 Borg Warner Improvements in or relating to variable-speed transmissions and control mechanisms therefor
DE19809464A1 (de) * 1998-03-06 1999-09-16 Voith Turbo Kg Anfahrvarianten für 6-Gang-Wandlerautomatgetriebe
WO2003016751A1 (fr) * 2001-08-17 2003-02-27 Korotkov Eduard Konstantinovic Transmission holonome universelle a variation infinie de couple
CN102358159A (zh) * 2011-08-05 2012-02-22 上海中科深江电动车辆有限公司 具有液力变矩器的混合驱动系统
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CN104534053A (zh) * 2014-12-12 2015-04-22 吴志强 一种复合型液力传动器以及起动器
CN104976303A (zh) * 2015-07-07 2015-10-14 吴志强 一种复合型箱体式液力偶合器以及起动器

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018185267A1 (fr) 2017-04-06 2018-10-11 Novozymes A/S Compositions de nettoyage et leurs utilisations
WO2018185285A1 (fr) 2017-04-06 2018-10-11 Novozymes A/S Compositions de nettoyage et utilisations correspondantes
WO2018185269A1 (fr) 2017-04-06 2018-10-11 Novozymes A/S Compositions de nettoyage et leurs utilisations
WO2019154954A1 (fr) 2018-02-08 2019-08-15 Novozymes A/S Variants de lipase et compositions en comprenant

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CN107448574A (zh) 2017-12-08
CN107869564A (zh) 2018-04-03
CN108243617A (zh) 2018-07-03
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CN104976303A (zh) 2015-10-14
CN107869562A (zh) 2018-04-03
HK1211668A1 (en) 2016-05-27

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