EP3081743B1 - Pompe a engrenages interieurs et vehicule dote d'une telle pompe - Google Patents

Pompe a engrenages interieurs et vehicule dote d'une telle pompe Download PDF

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Publication number
EP3081743B1
EP3081743B1 EP16000805.8A EP16000805A EP3081743B1 EP 3081743 B1 EP3081743 B1 EP 3081743B1 EP 16000805 A EP16000805 A EP 16000805A EP 3081743 B1 EP3081743 B1 EP 3081743B1
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EP
European Patent Office
Prior art keywords
area
tooth
rotor chamber
internal
rotor
Prior art date
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Active
Application number
EP16000805.8A
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German (de)
English (en)
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EP3081743A1 (fr
Inventor
Steffen Tröbst
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.)
MAN Truck and Bus SE
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MAN Truck and Bus SE
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Publication date
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Publication of EP3081743A1 publication Critical patent/EP3081743A1/fr
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Classifications

    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • 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
    • 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
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C2240/80—Other components
    • F04C2240/806—Pipes for fluids; Fittings therefor

Definitions

  • the invention relates to an internal gear pump, in particular a trochoid pump, according to claim 1 and a vehicle, in particular a commercial vehicle, with an internal gear pump according to claim 11.
  • Internal gear pumps are used in a variety of ways, for example as operating fluid pumps in vehicles. When used in this way, operation that is as quiet and quiet as possible is required so that no psychoacoustic noise is transmitted into a driver's cab or passenger cell.
  • a well-known internal gear or trochoid pump consists of a pump housing with a cylindrical rotor chamber with an external rotor with internal teeth arranged rotatably in the rotor chamber.
  • a rotary-driven inner rotor with external teeth is located in the outer rotor, with the inner and outer teeth interlocking in a trochoidal shape.
  • the inner rotor has one fewer external tooth compared to the internal teeth of the outer rotor.
  • an outer tooth of the inner rotor and an inner tooth of the outer rotor lie against each other on the head side in a tooth adjoining area.
  • the pump chambers become larger in a suction chamber formed on the front side of the rotor chamber. Subsequently, after passing through the reference plane at the second dead center position, the pump chambers become smaller again in a pressure chamber also formed on the front side of the rotor chamber, so that the fluid sucked and taken up in the suction chamber in the pump chambers is compressed in the pressure chamber by reducing the size of the pump chambers and pumped out through an outlet opening.
  • the tooth or trochoidal shapes of the external teeth and internal teeth are selected so that the tooth surfaces rolling against one another lie closely together in order to achieve high pump efficiencies with the lowest possible fluid mechanical losses.
  • this has the disadvantage that volumes of the fluid to be conveyed are trapped in the transition from the pressure chamber to the suction chamber, which can only escape through crushing between tooth flanks of the rotors in the area of the first dead center position.
  • the object of the invention is to develop a generic internal gear pump so that it can be operated with a high fluid-mechanical efficiency and low noise emissions.
  • a further object of the invention is to propose a vehicle, in particular a commercial vehicle, with such an internal gear pump.
  • an internal gear pump in particular a trochoid pump, is proposed for a vehicle, with a pump housing with a rotor chamber in which a toothed ring having internal teeth with internal teeth is accommodated.
  • This toothed ring can be brought into engagement with an internal gear that is mounted eccentrically to the toothed ring and has external teeth with external teeth in such a way that, based on a basic or starting position or based on a dead center position, at least one of the external teeth is in a tooth engagement area between two
  • the internal tooth space located between the internal teeth is located, in particular adapted to the shape and contour, the volumes forming the pump chambers between the internal teeth and the external teeth in a rotor chamber area assigned to a suction space, starting from the tooth engagement area up to a tooth adjoining area, preferably opposite the tooth engagement area, in which at least an external tooth adjoins or rests on the head side of an internal tooth, become larger and become smaller again in a rotor chamber area assigned to a pressure chamber, starting from the
  • at least one relief channel is now provided, which forms a flow connection between the tooth engagement area and the pressure chamber, so that a fluid or a squeeze flow can flow or flow out from the tooth engagement area to the pressure chamber.
  • the at least one external tooth lies in the tooth engagement area preferably in the internal tooth space in such a way that it is essentially completely or completely accommodated therein and pump chambers with a zero volume or almost a zero volume are therefore formed there.
  • the at least one external tooth in the tooth engagement area preferably lies completely or essentially gap-free and / or adapted to the shape and contour in the internal tooth space.
  • the suction chamber and the pressure chamber are spaced apart from the tooth engagement area and/or from the tooth adjacent area and separated from one another in a rotor chamber wall which adjoins, in particular directly adjacent, the front side of the toothed ring and the gear (in particular to the tooth areas of the toothed ring and the gear formed by the toothing). of the pump housing or open there.
  • the at least one relief channel is formed in a wall region of the rotor chamber wall of the pump housing that is adjacent to, in particular immediately adjacent to, the tooth engagement region and, starting from there, is formed or opens at a distance therefrom in the rotor chamber wall Pressure room is guided.
  • the at least one relief channel is preferably designed as a groove that is open to the rotor chamber and thus to the toothed ring/gear.
  • the at least one relief channel is designed in such a way that its tooth engagement area side channel end in the tooth engagement area is assigned only to the outer tooth of the internal gear.
  • the at least one relief channel is dimensioned in terms of its channel cross section such that at least 60% of a squeezing flow in a tooth engagement area can be diverted out of it into the pressure chamber. This ensures that the largest possible amount of squeezing flow flows away from the tooth engagement area towards the pressure chamber.
  • the special design of the at least one relief channel provides targeted optimization options for a current pump design. This allows psychoacoustic noise to be minimized, particularly in terms of loudness in the frequency groups Bark 5-15 and in terms of roughness.
  • the at least one relief channel can be designed with regard to its channel cross-section and/or its channel length in such a way that the specific loudness of the pump during operation in the frequency groups Bark 5-15 is reduced in such a way that it is a maximum of 3 sone/Bark and/or as a result in the range of frequency groups Bark 5-15 results in a maximum roughness of 1.2 asper/Bark.
  • At least one additional channel is provided, which forms a flow connection between the tooth adjacent area and the pressure chamber.
  • the at least one additional channel is formed in a wall region of the rotor chamber wall which is adjacent to the tooth adjacent region, in particular immediately adjacent, and is guided from there to the pressure chamber which is also formed and/or opens out in the rotor chamber wall at a distance therefrom, it can preferably be provided that the at least an additional channel is designed as a groove open towards the rotor chamber.
  • the special design of the at least one additional channel also provides targeted optimization options for a current pump design.
  • the at least one additional channel is preferably designed in terms of its channel cross-section and/or its channel length in such a way that the specific loudness of the pump during operation in the frequency groups Bark 3-10 is reduced in such a way that it is a maximum of 4 sone/Bark and/or this results in a maximum roughness of 2 asper/Bark in the range of frequency groups Bark 3-10.
  • the suction chamber and the pressure chamber lie on opposite sides of a reference plane defined by the tooth engagement area and the tooth adjacent area (the tooth engagement area and the tooth adjacent area advantageously lying opposite one another) and are each spaced apart from these areas in one of the rotor chambers End wall of the pump housing.
  • this reference plane can also be set by one or more axes of rotation of the toothed ring or internal gear, at least one of which is designed to be rotatable.
  • the specific loudness and roughness can be defined in such a way that, in addition to a significant reduction in the pressure pulsation and reduction in the emitted sound pressure level, there is a significant optimization of the psychoacoustic parameters, which does not cause any loss of efficiency.
  • the internal gear pump is a trochoid pump in which the teeth mesh with one another in a trochoidal shape.
  • a further preferred embodiment is one in which the internal gear has one fewer external tooth compared to the internal teeth of the toothed ring. Particularly advantageous results were achieved in this context with a trochoid pump in which the gear ring has seven internal teeth and an internal gear has six external teeth.
  • the toothed ring is, for example, an external rotor rotatably arranged in the rotor chamber.
  • the internal gear can be designed as a rotationally driven internal rotor.
  • Particularly preferred is an embodiment in which both the toothed ring as an external rotor and the internal gear as an internal rotor are rotationally driven.
  • Fig. 1 is a top view of an internal gear pump designed as a trochoid pump 1 (without housing cover) and in Fig. 2 a sectional view along reference plane 2 (line AA). Fig. 1 shown.
  • the trochoid pump 1 has a pump housing 3 with a preferably cylindrical rotor chamber 4, which is protected by a chamber cover 5 (see Fig. 2 ) is closed in operating mode.
  • a chamber cover 5 see Fig. 2
  • the chamber lid 5 is omitted to provide a view of the chamber interior.
  • an external rotor 6 is rotatably mounted with a preferably identical cylindrical circumference, which is designed as a toothed ring with several, here only by way of example seven, inwardly directed internal teeth 7a to 7g.
  • the cylinder axis of the rotor chamber 4 or the axis of rotation for the outer rotor 6 is marked with the reference number 8.
  • An inner rotor 11 is arranged or mounted eccentrically in the outer rotor 6 and is driven in rotation about a drive axle 10 by means of a drive shaft 9.
  • the inner rotor 11 is here preferably provided with one fewer external teeth and thus, in the example shown here, with six external teeth 12a to 12f.
  • the inner teeth 7a to 7g and the outer teeth 12a to 12f mesh with each other in a trochoidal shape.
  • the reference plane 2 passes through the middle of a first (upper) dead center position 13, through the two axes 8 and 10, which are eccentrically offset from one another, and through a second, essentially opposite and lower dead center position 14.
  • a first (upper) dead center position 13 there is an external tooth in a tooth engagement area 13a 12a in an internal tooth space (here between the internal teeth 7a and 7g) essentially completely or completely, that is, essentially gap-free or adapted to the shape and contour.
  • an external tooth 12d lies in a tooth adjacent region 14a on the head side of the internal tooth 7d or borders there.
  • the suction chamber 17 is shown here only in dashed lines and is formed in a rotor chamber wall 4a of the rotor chamber 4, at the end adjacent to the tooth areas of the inner rotor 11 and outer rotor 6 (a fluid connection line as an inlet is not shown for reasons of clarity).
  • the pump chambers 16 are reduced in size during a movement towards the first dead center position 13, whereby the fluid taken up in the suction chamber 17 from the pump chambers 16 into a pressure chamber 18 is pressed and derived from this with a pump line (not shown for reasons of clarity).
  • the pressure chamber 18 is also shown here schematically in dashed lines and (like the suction chamber 17) is formed on the front side adjacent to the outer rotor 6 and inner rotor 11 in a rotor chamber wall 4a of the rotor chamber 4.
  • the suction chamber 17 and pressure chamber 18 can, as in Fig. 1 shown, be formed in or on the same rotor chamber wall 4a or alternatively also be formed on different rotor chamber walls 4a, for example, as in Fig. 2 shown, be arranged on opposite rotor chamber walls 4a.
  • both the suction chamber 17 and the pressure chamber 18 have a defined distance from the tooth engagement region 13a and from the tooth adjacent region 14a, so that the rotor chamber walls 4a essentially directly adjoin there. This can lead to the formation of the already mentioned squeezing flows in the tooth engagement area 13a or the generation of pressure surges in the tooth adjacent area 14a.
  • Both the relief channel 19 and the additional channel 20 can be designed as a groove open towards the rotor chamber 4, but if necessary also can be designed as a channel running inside the rotor chamber wall 4a.
  • the relief channel 19 runs as a flow channel into the pressure chamber 18, starting from the reference plane 2 and thus starting from the middle of the tooth engagement area 13a. This avoids squeezing flows in the tooth engagement area 13a and leads them into the pressure chamber 18, thereby advantageously reducing psychoacoustic noise in particular.
  • the additional channel 20 extends from the center of the tooth adjacent area 14a as a flow channel also in the pressure chamber 18. This reduces pulse-like pressure surges at this point at the transition from the suction chamber 17 to the pressure chamber 18, whereby a further reduction in noise is achieved.

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

Claims (11)

  1. Pompe à engrenages intérieurs, notamment pompe trochoïde, pour un véhicule, avec un boîtier de pompe (3) avec une chambre de rotor (4), dans laquelle est logée une bague dentée (6) présentant une denture intérieure avec des dents intérieures (7a-7g), qui peut être mise en prise avec une roue dentée (11) montée de manière excentrée par rapport à la bague dentée (6) et présentant une denture extérieure avec des dents extérieures (12a-12f) de telle sorte que, dans une zone d'engrènement (13a), au moins l'une des dents extérieures (12a) s'insère dans une zone interdentaire intérieure située entre deux dents intérieures (7a ; 7g),
    les volumes formant des chambres de pompe (16) entre les dents intérieures (7a-7g) et les dents extérieures (12a-12f) devenant plus grands dans une zone de chambre de rotor associée à une chambre d'aspiration (17), en partant de la zone d'engrènement (13a) jusqu'à une zone de délimitation de dents (14a), dans laquelle au moins une dent extérieure (12d) est adjacente à une dent intérieure (7d) du côté de la tête ou s'applique contre elle, et devenant à nouveau plus petits dans une zone de chambre de rotor associée à une chambre de pression (18), en partant de la zone de délimitation de dents (14a) jusqu'à la zone d'engrènement (13a),
    au moins un canal de décharge (19) étant prévu, qui forme une liaison d'écoulement entre la zone d'engrènement (13a) et la chambre de pression (18),
    caractérisée en ce que
    au moins un canal supplémentaire (20) est prévu, qui forme une liaison d'écoulement entre la zone de délimitation de dents (14a) et la chambre de pression (18), l'au moins un canal supplémentaire (20) étant formé dans une zone de paroi de la paroi de chambre de rotor (4a) adjacente à la zone de délimitation de dents (14a) et étant guidé à partir de là vers la chambre de pression (18) formée et/ou débouchant également dans la paroi de chambre de rotor (4a) à distance de celle-ci.
  2. Pompe à engrenages intérieurs selon la revendication 1, caractérisée en ce que la chambre d'aspiration (17) et la chambre de pression (18) sont formées à distance de la zone d'engrènement (13a) et/ou de la zone de délimitation de dents (14a) ainsi que séparément l'une de l'autre dans une paroi de chambre de rotor (4a) de la chambre de rotor (4) adjacente, notamment directement adjacente, frontalement à la bague dentée (6) et à la roue dentée (11), et/ou y débouchent.
  3. Pompe à engrenages intérieurs selon la revendication 2, caractérisée en ce que l'au moins un canal de décharge (19) est formé dans une zone de paroi de la paroi de chambre de rotor (4a) adjacente, notamment directement adjacente, à la zone d'engrènement (13a), et est guidé à partir de là vers la chambre de pression (18) également formée et/ou débouchant dans la paroi de chambre de rotor (4a) à distance de celle-ci.
  4. Pompe à engrenages intérieurs selon la revendication 2 ou 3, caractérisée en ce que l'au moins un canal de décharge (19) est configuré sous forme de rainure ouverte vers la chambre de rotor (4).
  5. Pompe à engrenages intérieurs selon la revendication 3 ou 4, caractérisée en ce que l'au moins un canal de décharge (19) est configuré de telle sorte que son extrémité de canal du côté de la zone d'engrènement est associée uniquement à la dent extérieure (12a) de la roue dentée intérieure (11) dans la zone d'engrènement (13a).
  6. Pompe à engrenages intérieurs selon l'une quelconque des revendications précédentes, caractérisée en ce que l'au moins un canal de décharge (19) est dimensionné, en ce qui concerne sa section transversale de canal, de telle sorte qu'au moins 60 % d'un écoulement par écrasement de la zone d'engrènement (13a) peut être évacué dans la chambre de pression (18).
  7. Pompe à engrenages intérieurs selon l'une quelconque des revendications précédentes, caractérisée en ce que l'au moins un canal supplémentaire (20) est configuré sous forme de rainure ouverte vers la chambre de rotor (4).
  8. Pompe à engrenages intérieurs selon l'une quelconque des revendications précédentes, caractérisée en ce que la chambre d'aspiration (17) et la chambre de pression (18) sont situées sur des côtés opposés d'un plan de référence (2) défini par la zone d'engrènement (13a) et la zone de limitation de dents (14a) et débouchent respectivement à distance de ces zones (13a, 14a) dans une paroi de chambre de rotor (4a) du boîtier de pompe (3) associée à la chambre de rotor (4).
  9. Pompe à engrenages intérieurs selon l'une quelconque des revendications précédentes, caractérisée en ce que la bague dentée (6) est un rotor extérieur agencé de manière rotative dans la chambre de rotor (4) et/ou la roue dentée intérieure (11) est un rotor intérieur agencé de manière entraînée en rotation dans le rotor extérieur.
  10. Pompe à engrenages intérieurs selon l'une quelconque des revendications précédentes, caractérisée en ce que la pompe à engrenages (1) est une pompe trochoïde dans laquelle les dents s'engrènent de manière trochoïde et/ou la roue dentée (11) présente une dent extérieure (12) de moins par rapport aux dents intérieures (7) de la bague dentée (6).
  11. Véhicule, notamment véhicule utilitaire, avec une pompe à engrenages (1) selon l'une quelconque des revendications précédentes.
EP16000805.8A 2015-04-18 2016-04-08 Pompe a engrenages interieurs et vehicule dote d'une telle pompe Active EP3081743B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015004984.4A DE102015004984A1 (de) 2015-04-18 2015-04-18 Innenzahnradpumpe und Fahrzeug mit einer Innenzahnradpumpe

Publications (2)

Publication Number Publication Date
EP3081743A1 EP3081743A1 (fr) 2016-10-19
EP3081743B1 true EP3081743B1 (fr) 2023-11-22

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Application Number Title Priority Date Filing Date
EP16000805.8A Active EP3081743B1 (fr) 2015-04-18 2016-04-08 Pompe a engrenages interieurs et vehicule dote d'une telle pompe

Country Status (5)

Country Link
EP (1) EP3081743B1 (fr)
CN (1) CN106050651B (fr)
BR (1) BR102016008536B1 (fr)
DE (1) DE102015004984A1 (fr)
RU (1) RU2719005C2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU199143U1 (ru) * 2020-04-22 2020-08-19 Публичное акционерное общество «Авиационная корпорация «Рубин» Героторный насос

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3034448A (en) * 1959-05-19 1962-05-15 Robert W Brundage Hydraulic pump
DE3933978A1 (de) * 1989-10-11 1991-05-02 Eisenmann Siegfried A Sauggeregelte zahnringpumpe
JP3109405B2 (ja) * 1995-02-24 2000-11-13 三菱マテリアル株式会社 内接型ギヤポンプ
UA44827C2 (uk) * 1998-07-28 2002-03-15 Відкрите Акціонерне Товариство "Гідросила" Шестеренна гідромашина
JP2004092637A (ja) 2002-07-11 2004-03-25 Yamada Seisakusho Co Ltd トロコイドポンプ
DE10255271C1 (de) * 2002-11-21 2003-12-04 Joma Hydromechanic Gmbh Rotorpumpe
JP4087309B2 (ja) * 2003-07-25 2008-05-21 株式会社山田製作所 トロコイド型オイルポンプ
CA2550313C (fr) * 2004-02-18 2012-10-02 Aisin Aw Co., Ltd. Pompe a huile et transmission automatique comportant une telle pompe
JP4319617B2 (ja) * 2004-12-27 2009-08-26 株式会社山田製作所 トロコイド型オイルポンプ
JP5479934B2 (ja) * 2010-02-05 2014-04-23 アイシン・エィ・ダブリュ株式会社 オイルポンプ
JP5681571B2 (ja) * 2011-06-06 2015-03-11 株式会社山田製作所 オイルポンプ
CN102434455A (zh) * 2011-12-31 2012-05-02 张洪领 一种摆线转子泵

Also Published As

Publication number Publication date
BR102016008536A2 (pt) 2016-11-16
BR102016008536B1 (pt) 2022-11-08
CN106050651A (zh) 2016-10-26
RU2016114430A (ru) 2017-10-19
RU2016114430A3 (fr) 2019-10-07
RU2719005C2 (ru) 2020-04-15
CN106050651B (zh) 2020-06-26
EP3081743A1 (fr) 2016-10-19
DE102015004984A1 (de) 2016-10-20

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