WO2016019959A1 - Betätigungsvorrichtung mit im antriebslosem zustand selbst sperrendem radial wirkendem federmechanismus - Google Patents
Betätigungsvorrichtung mit im antriebslosem zustand selbst sperrendem radial wirkendem federmechanismus Download PDFInfo
- Publication number
- WO2016019959A1 WO2016019959A1 PCT/DE2015/200418 DE2015200418W WO2016019959A1 WO 2016019959 A1 WO2016019959 A1 WO 2016019959A1 DE 2015200418 W DE2015200418 W DE 2015200418W WO 2016019959 A1 WO2016019959 A1 WO 2016019959A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- actuating device
- parking brake
- unit
- drive
- Prior art date
Links
Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
- F16D63/008—Brakes acting on a linearly moving member
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
Definitions
- the invention relates to an actuating device for a clutch of a motor vehicle, such as a car, truck, bus or agricultural utility vehicle, namely for opening and closing the clutch, with a rotatably driven by a drive unit rotor and with a slidable in the axial direction slide unit, which is coupled to the rotor by means of a plurality of rolling elements having screw drive, wherein the rolling elements in a rotation of the rotor by means of a drive unit applied by the first drive force within a threaded portion of the carriage unit, under an axial displacement of the carriage unit, unroll.
- a motor vehicle such as a car, truck, bus or agricultural utility vehicle
- DE 10 2012 207 325 A1 discloses a device and a method for driving a motor vehicle.
- the drive device as disclosed herein is designed for motor vehicles and has an actuating device for establishing and releasing a rotationally fixed connection between at least one input device and at least one output device of a clutch device.
- the actuating device of the coupling device has a mechanical energy store, which is provided for producing the torque transmission, in the coupling device to apply a first contact pressure between the at least one input device and the at least one output device.
- an actuating device for a clutch which further comprises a stator and a rotatably arranged to the stator device rotor device.
- a clutch By rotation of the rotor device in the axial direction at least a limited displaceable carriage device is movable.
- a lever element such as a plate spring is moved.
- the Slide device is in this case urged by a biasing unit on the lifting element.
- this is achieved by providing a locking brake device on the rotor which, in a first position, in which the drive unit is in a non-driven state, for axially holding the carriage unit, automatically fixes the rotor to the threaded section.
- the actuating device By such a configuration of the actuating device, it is possible to reliably implement a displacement between the carriage unit and the rotor in an unactuated state of the actuator unit.
- the actuator unit can be completely deactivated in the respective positions of the actuating device, whereby the actuator unit then consumes no electrical energy in these positions. The efficiency is thereby significantly improved.
- the parking brake device is particularly simple. Does the parking brake device in the radial direction at least partially displaceable, resilient locking element / spring element, the non-positively in the first position, preferably frictionally engaged on the threaded portion is applied, the parking brake device can be easily attached to the rotor or integrated into this.
- the blocking element is also designed as a, preferably (sheet-metal) strip-shaped / leaf-shaped spring element, which is connected to a first portion fixed to the outer peripheral surface of the rotor and is mounted elastically deformable with a second portion in the radial direction.
- a kind of leaf spring element can be implemented, which is deformable in the radial direction, and is particularly inexpensive to produce.
- it is particularly space-saving integrated in the rotor.
- the parking brake device can be implemented particularly effectively according to the mode of action of a drum brake, wherein the already existing structure of the threaded section can be used directly to engage with the Locking element frictionally engaged in contact.
- the parking brake device (as an actuator) has a coaxial with the rotor and rotatable relative to the rotor adjusting ring, which adjusting is biased resiliently in two directions of rotation relative to the rotor.
- Such an adjusting ring can continue to be integrated in a particularly space-saving manner in the rotor. As a result, further space is saved.
- the parking brake device has a displaceable in the radial direction mounted in the rotor adjusting pin which is pressed against a radially inner side against the locking element.
- the adjusting ring has on its radial outer side an actuating contour, preferably a cam-like elevation, which the blocking element in the first position pushes / presses against the threaded portion.
- this cam-like elevation is arranged such that it presses on the adjusting pin and this in turn on the locking element.
- any position of the carriage unit relative to the rotor can be determined / blocked in a simple manner by means of the adjusting brake device.
- a clutch with an actuator according to at least one of the aforementioned embodiments is hereby included, whereby the entire coupling can be improved, particularly in terms of efficiency.
- an arrangement for self-locking of the actuating device which is preferably designed as an electrical central release, is implemented.
- This self-locking can take place in any state, even without rotor operation.
- the rotor with the spindle (ball screw) / the threaded portion via two circumferential springs in the unactuated state, held in a central position.
- a blocking element between the rotor and ball screw is arranged, which blocking element exerts a radial blocking force on the spindle.
- the locking element may be a system of pin and plate spring / leaf spring or the like. In the central position, the spring presses radially on the pin.
- Fig. 1 is an isometric view of a cut longitudinally
- Assembly unit as it is used in the actuator according to the invention according to a first embodiment, has been dispensed with the detailed representation of the carriage unit and in this case, in particular, the threaded portion is seen, which is arranged radially around the rotor,
- Fig. 2 is an isometric view of that already shown in Fig. 1
- Fig. 3 is a front view of the assembly unit shown in Fig. 1 of
- Actuator wherein the actuating device is switched in a second position in which two spring elements used for the bias of the adjusting ring are deformed such that an adjusting pin cooperating with the adjusting, is in a retracted state, so that the locking element is spaced from the threaded portion .
- FIG. 4 shows a detailed view of the area marked IV in FIG. 3, in which the actuating contour introduced into the adjusting ring is particularly well visible,
- Fig. 5 in turn, a front view of the actuator, as can already be seen in Fig. 3, wherein the parking brake device of Actuator not, as in Fig. 3, is located in a second position in which the rotation between the threaded portion and the rotor is freely possible, but is located in a first position in which the rotation between the threaded portion and the rotor by means of Blocking element is blocked,
- Fig. 6 is a detail view of the already shown in Fig. 4 area in an isometric Daregna, wherein the first position of Fig. 5 is switched and in particular the position of the adjusting pin and the locking element of the parking brake device, can be seen by displacement by a survey on the adjusting ring .
- Fig. 7 is a front view of the actuating device according to the invention according to one of Figs. 1 to 6, which is similar to Figure 3 figure and again the blocking element occupies the second position, but wherein the rotor is now against the adjusting ring not in a first rotational direction, as in Fig. 3, but is rotated in an opposite thereto second rotational direction, and the adjusting pin is retracted in another recess in the adjusting ring, so that the rotor can rotate freely relative to the threaded portion, and
- Fig. 8 is a longitudinal sectional view of that shown in Fig. 1
- Actuating device with particularly good the position of the adjusting pin and the locking element relative to the rolling elements of the screw drive can be seen.
- the actuating device 1 shown in FIGS. 1 to 8 is provided for opening and closing a clutch.
- the clutch is a clutch of a Motor vehicle and preferably designed for a hybrid drive.
- the actuating device 1 is designed as an electrical Gottausschreiber.
- FIGS. 1 to 8 are limited to an assembly / an assembly unit between a rotor 2 and a threaded portion 6 of a screw drive 5 for clarity.
- the actuating device 1 has not only the drive unit, not shown for clarity, namely an electric drive unit, such as an electric motor, rotatably driven rotor 2, but also a slidable in the axial direction carriage unit.
- the slide unit not shown for clarity and is coupled to the rotor 2 by means of, a plurality of rolling elements 4 having screw drive 5 motion-coupled.
- a plurality of rolling elements 4 having screw drive 5 motion-coupled.
- a first axial position of the carriage unit is selected so that the clutch is preferably in an engaged position
- a second axial position of the carriage unit which is displaced / spaced from the first axial position is selected so that the clutch in a disengaged position is located. Between these two positions is switched such that the rotor 2 is rotated in a first direction of rotation or in an opposite second direction of rotation.
- a Parking brake device 3 is provided / attached to the rotor 2.
- the parking brake device 3 is at least in a first position, in a non-driven state of the drive unit, in which the driving force is smaller than the strictlyverstellkraft, arranged such that it automatically sets the rotor 2 on the threaded portion 6 / holds.
- the threaded portion 6 is formed as a spiral-shaped spring wire, wherein a thread is defined by two adjacent turns.
- the threaded portion 6 extends radially outside of the rotor 2 circumferentially around the rotor 2 around.
- the rotor 2 has on its radial outer side 7, namely a radial outer circumferential surface, a continuous guide groove 8 extending around the circumference. Within this guide groove, the rolling elements 4 are received and stored along rollable.
- the rotor 2 is designed substantially sleeve-shaped. In an axial region of the rotor 2, this has a radial bearing 9, by means of which it is rotatably arranged with respect to a component fixed to the housing.
- the radial bearing 9 is in this case designed as a rolling bearing, namely as a deep groove ball bearing in the form of a double deep groove ball bearing.
- a stator of the drive unit (not shown here for clarity) is arranged, which rotatably drives the rotor 2 as a function of the operating position of the drive unit.
- the threaded portion 6 is fixedly connected in the axial direction with the carriage / the carriage unit. In a rotation of the rotor 2 relative to the threaded portion 6, it is therefore both an axial displacement of the threaded portion 6, as well as an axial displacement of the carriage unit.
- the more detailed embodiment of the parking brake device 3 is shown particularly well in connection with FIGS. 2 to 7.
- the parking brake device 3 has on the one hand an adjusting ring 10, which is arranged on a radial inner peripheral side of the rotor 2, namely between the rotor 2 and the stator.
- the adjusting ring 10 is inserted with its outer peripheral side in the inner circumferential surface of the rotor 2 and guided by the inner peripheral surface of the rotor 2, wherein the adjusting ring 10 and rotor 2 form a kind of clearance between them.
- the substantially sleeve-shaped adjusting ring 10 is thus rotatable and coaxial relative to the rotor 2, disposed radially inside the rotor 2.
- the adjusting ring 10 is fixedly connected in the axial direction with the rotor 2.
- the adjusting ring 10 is rotatably driven by the rotor 2.
- the adjusting ring 10 In a first circumferential region, the adjusting ring 10 on its outer peripheral surface 11 on an actuating contour 12 which is formed in the form of two axially extending recesses 13.
- a first recess 13a extends in this case by a certain axial distance parallel to a second recess 13b.
- the two recesses 13a, 13b are geometrically separated by means of a web section 14. Both recesses 13a, 13b are formed in the form of grooves.
- the web portion 14 is formed as a cam-shaped elevation / cam. The web portion 14 extends in the radial direction just to the extent that it has the same outer radius as the usual, circular area of the outer peripheral surface 11, which adjoins the recesses 13a and 13b along the circumference.
- an adjusting pin 15 displaceably mounted in the radial direction acts together.
- the adjusting pin 15 is in the form of a pin.
- the adjusting pin 15 is aligned in the direction of its longitudinal axis in the radial direction and displaceable between a retracted and an extended position.
- a blocking element 16 is mounted in the form of a friction element.
- the blocking element 16 is designed as a resilient Sheet metal / a resilient metal strip formed.
- this locking element 16 With a first axial region of this locking element 16 is fixedly inserted in a, along the circumference partially extending recess 17 in the outer peripheral surface of the rotor 2.
- the thickness of the blocking element 16 corresponds to the depth of the recess 17.
- the blocking element 16 With a further, second section, the blocking element 16 is loose / unconnected to the outer peripheral surface of the rotor 2 and is thus removable with this second portion 19 of the rotor 2 in the radial direction.
- the blocking element is essentially curved.
- On a radial inner side of this first portion 18 is a first end face of the adjusting pin 15 at. With a second end face of the adjusting pin 15 abuts the actuating contour 12.
- two spring elements 20a and 20b are supported in both directions of rotation of the adjusting ring 10 on the adjusting ring 10.
- the two spring elements 20a and 20b are designed as helical springs and preferably designed the same with respect to their spring length and spring hardness. Both spring elements 20a and 20b extend longitudinally along the circumference. With a first side, the two spring elements 20a and 20b are each supported on a stop 21 of the rotor 2. With a second end opposite this first end, the two spring elements 20a and 20b are respectively supported on a first or a second counterstop 22a, 22b of the adjusting ring 10.
- the first counter stop 22a and the second counter stop 22b of the adjusting ring 10 are each designed as a web extending in the radial direction.
- the two counterstops 22a and 22b are circumferentially / circumferentially spaced by a certain amount.
- the stop 21 of the rotor 2 is arranged.
- the first spring element 20a is located in a gap between the first counter-stop 22a and the stop 21 and the second spring element 20b in a second space between the stop 21 and the second counter-stop 22b.
- the two spring elements 20a and 20b are matched with respect to their spring hardness such that the rotor 2 in a first drive state of the drive unit (driving force greater than the réelleverstellkraft and acting in a first direction of rotation), as shown in Fig. 3, in a first Direction of rotation relative to the adjusting ring 10 is rotated.
- the adjusting pin 15 is in a retracted position within the second recess 13b on the adjusting ring 10 fitting.
- the blocking element 16 is spaced from the threaded section 6 in this state designated as the second position of the parking brake device 3, and the rotor 2 can be rotated relative to the threaded section 6, so that the threaded section 6 is displaced in the axial direction.
- the drive unit is switched to a second drive state (drive force greater than the minimum displacement force and acting in a second rotational direction)
- the rotor 2 is rotated relative to the adjusting ring 10 in a second rotational direction.
- the adjusting pin 15 is displaced in the first recess 13a in the adjusting ring 10.
- the second spring element 20b is stretched / compressed, wherein the first spring element 20a is relaxed.
- the blocking element 16 is again spaced from the threaded section 6 in this state designated as the second position of the parking brake device 3, so that the threaded section 6 can be rotated relative to the rotor 2.
- the state designated as the first position of the parking brake device 3 is finally reached in FIGS. 5 and 6.
- the first spring element 20 is relaxed and the adjusting ring 10 is rotated such that the adjusting pin 15 is moved by the cam-shaped projection / the web portion 14 radially outwardly in its extended position and is pressed against the locking element 16.
- the two spring elements 20a and 20b in Essentially extended the same way.
- the blocking element 16 is pressed in the first position of the parking brake device 3 in the second portion 19 in the radial direction outwards, so that it firmly, namely frictionally engaged with a friction lining attached to it on the threaded portion 6.
- adjusting pin 15 and the blocking element 16 are preferably arranged in an axial direction next to the guide groove 8, namely preferably on a radial bearing 9 side facing away from the guide groove. 8
- this is an actuator in the form of an electrical Primaaus Wegers implemented.
- the ball screw 5 In order to avoid energization in the respective positions / holding positions of the carriage unit, the ball screw 5 should have a safe design, which provides a undoubted OrganichemmungsSh in retroactivity mode or indirect efficiency mode, or ⁇ ' ⁇ 0. Since a reliable self-locking by the own Kugelgewindetriebs-Kontrutation is not given (rolling elements / balls have a coefficient of friction p generally from 0.3 to 0.6 on), an extra self-locking device (parking brake device 3) must be added. This is fixed in the drive motor / rotor, or integrated.
- the rotor 2 of the drive unit / the electric drive motor is rotatably mounted in the ball screw 5, and reset by two opposing springs 20a, 20b in a defined central position (first position) without energization of the electric drive motor.
- the cam 14 exerts a radial force which is transmitted to the leaf spring 16 by the radial pin 15, slidably disposed in the ball screw 5.
- This force provides for the extension of the leaf spring 16 between the ball screw to exert a frictional force or clamping force in the ball screw nut which causes the rotation prevents the ball screw to ball screw nut.
- the rotation of the electric drive motor first initiates the rotation of this cam 14 within the ball screw 5, which simultaneously biases a circumferentially arranged spring 20a, 20b, and causes the retraction of the pin 15 and the leaf spring 16, respectively.
- a circumferentially arranged spring 20a, 20b When one of the tangential springs 20 a or 20 b is sufficiently biased, the leaf spring 16 is no longer in contact with the ball screw nut 6 and its inner race, and the cam 14 is rotationally engaged (mechanical stop) with the ball screw 5, so that the electric - Drive motor can transfer its drive torque directly to the ball screw 5 without obstruction.
- the cam 14 is part of the electric drive motor.
- This cam 14 is rotatably mounted to the ball screw, and its central position is achieved by two circumferentially opposed springs 20a, 20b.
- This cam 14 can transfer the drive torque by two circumferential mechanical stops on the ball screw.
- the leaf spring 16 contacts the inner race of the ball screw nut and is actuated by a radially 29iebar arranged pin 15.
- the leaf spring 16 has the task of exerting a restoring force inwardly on the pin 15, and also exert a compressive force against the ball screw nut in the extended position of the pin 15.
- the lower part of the radial pin 15 touches the cam contour 12, so that the pressure effect, or the clamping action of the leaf spring 16 in the central angular position of the cam 14 is achieved to the ball screw.
- the pin 15 is immersed, and the clamping action is lost.
- the prevention of the clamping action ensures that upon actuation of the ball screw 5 no unnecessary drag torque, which is necessary at standstill of the system to Ensuring the self-locking, is generated, and thus increases the overall efficiency of the clutch actuator.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112015003623.7T DE112015003623A5 (de) | 2014-08-06 | 2015-07-24 | Betätigungsvorrichtung mit im antriebslosem zustand selbst sperrendem radial wirkendem federmechanismus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014215598.3 | 2014-08-06 | ||
DE102014215598.3A DE102014215598B4 (de) | 2014-08-06 | 2014-08-06 | Betätigungsvorrichtung mit im antriebslosem Zustand selbst sperrendem radial wirkendem Federmechanismus |
Publications (1)
Publication Number | Publication Date |
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WO2016019959A1 true WO2016019959A1 (de) | 2016-02-11 |
Family
ID=53900723
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/DE2015/200418 WO2016019959A1 (de) | 2014-08-06 | 2015-07-24 | Betätigungsvorrichtung mit im antriebslosem zustand selbst sperrendem radial wirkendem federmechanismus |
Country Status (2)
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DE (2) | DE102014215598B4 (de) |
WO (1) | WO2016019959A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106004818A (zh) * | 2016-05-30 | 2016-10-12 | 魏伯卿 | 紧急辅助制动装置 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2031264A2 (de) * | 2007-08-30 | 2009-03-04 | Honeywell International Inc. | Rücksetzbarer mechanischer Trennschalter mit Kugelgewinde |
DE102012207325A1 (de) | 2011-05-23 | 2012-11-29 | Schaeffler Technologies AG & Co. KG | Vorrichtung und Verfahren zum Antrieb eines Kraftfahrzeuges |
DE102013207210A1 (de) * | 2012-05-11 | 2013-11-14 | Schaeffler Technologies AG & Co. KG | Verfahren zum Betrieb einer Betätigungsvorrichtung für eine Kupplung und Betätigungsvorrichtung für eine Kupplung |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4320204A1 (de) * | 1993-06-18 | 1994-12-22 | Fichtel & Sachs Ag | Stellantrieb für eine Kraftfahrzeug-Reibungskupplung |
DE10035516A1 (de) * | 2000-07-21 | 2002-01-31 | Mannesmann Sachs Ag | Ausrückeranordnung |
DE102008012894A1 (de) * | 2008-03-06 | 2009-09-10 | Zf Friedrichshafen Ag | Betätigungseinrichtung für eine Reibungskupplungseinrichtung und von diesen gebildete Drehmomentübertragungseinrichtung |
DE102013204435A1 (de) * | 2012-04-03 | 2013-10-10 | Schaeffler Technologies AG & Co. KG | Spindeltrieb mit Formfeder |
-
2014
- 2014-08-06 DE DE102014215598.3A patent/DE102014215598B4/de active Active
-
2015
- 2015-07-24 WO PCT/DE2015/200418 patent/WO2016019959A1/de active Application Filing
- 2015-07-24 DE DE112015003623.7T patent/DE112015003623A5/de not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2031264A2 (de) * | 2007-08-30 | 2009-03-04 | Honeywell International Inc. | Rücksetzbarer mechanischer Trennschalter mit Kugelgewinde |
DE102012207325A1 (de) | 2011-05-23 | 2012-11-29 | Schaeffler Technologies AG & Co. KG | Vorrichtung und Verfahren zum Antrieb eines Kraftfahrzeuges |
DE102013207210A1 (de) * | 2012-05-11 | 2013-11-14 | Schaeffler Technologies AG & Co. KG | Verfahren zum Betrieb einer Betätigungsvorrichtung für eine Kupplung und Betätigungsvorrichtung für eine Kupplung |
Also Published As
Publication number | Publication date |
---|---|
DE112015003623A5 (de) | 2018-01-04 |
DE102014215598B4 (de) | 2016-03-31 |
DE102014215598A1 (de) | 2016-02-11 |
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