EP2173524B1 - Hydraulischer abbauhammer - Google Patents

Hydraulischer abbauhammer Download PDF

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Publication number
EP2173524B1
EP2173524B1 EP08779510A EP08779510A EP2173524B1 EP 2173524 B1 EP2173524 B1 EP 2173524B1 EP 08779510 A EP08779510 A EP 08779510A EP 08779510 A EP08779510 A EP 08779510A EP 2173524 B1 EP2173524 B1 EP 2173524B1
Authority
EP
European Patent Office
Prior art keywords
piston rod
channel
chamber
piston
created
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08779510A
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German (de)
English (en)
French (fr)
Other versions
EP2173524A1 (de
Inventor
Stefan KONECNÍK
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.)
Konek sro
Original Assignee
Konek sro
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 Konek sro filed Critical Konek sro
Priority to PL08779510T priority Critical patent/PL2173524T3/pl
Publication of EP2173524A1 publication Critical patent/EP2173524A1/de
Application granted granted Critical
Publication of EP2173524B1 publication Critical patent/EP2173524B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/16—Valve arrangements therefor
    • B25D9/20—Valve arrangements therefor involving a tubular-type slide valve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/04—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously of the hammer piston type, i.e. in which the tool bit or anvil is hit by an impulse member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
    • B25D9/265—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof with arrangements for automatic stopping when the tool is lifted from the working face or suffers excessive bore resistance
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D2209/005—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously having a tubular-slide valve, which is coaxial with the piston
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/035—Bleeding holes, e.g. in piston guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/125—Hydraulic tool components
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/131—Idling mode of tools

Definitions

  • the technical solution relates to hydraulic excavating hammers belonging to the category of percussive and pressurized fluid driven portable impacting devices. It is about a piston hammer in which a pulse element - firing pin strikes a working tool - chisel. Such a hydraulic Abbanhammer is from the WO 02/06 014 A known.
  • WO 02/06014 A discloses a hydraulic excavation hammer composed of a monolithic support housing, a cylindrical piston rod, a striker and a work tool and provided with a supply and discharge of pressurized liquid, wherein in a part of support housing is a piston rod immovably inserted with a piston on an axle stiff firing pin is pushed, and wherein in the second part of the support housing, a working tool is inserted.
  • the previously known solutions are based on a hydraulic control of firing pin.
  • the firing pin has the shape of a continuous piston rod.
  • the piston rod has in its middle part an enlarged diameter, which assumes the function of a weakly sealed by a cylinder gap piston. Because the firing pin is statically over-defined after any contact of the piston member with the cylinder in its storage, the gap must be sufficiently large, causing large flow losses. It has the greatest influence on efficiency reduction of hammers of today's world production.
  • the pressure oil supply is guided by the control of the support housing in the working chambers of the cylinder through channels, which reduce with their resistance, the effectiveness of hammer, especially in the impact movement of the firing pin.
  • a switching pulse of the control in upper position is succeeded by the control channel in the cylinder.
  • the channel does not allow a cuff seal of the firing pin piston. For that reason, the diameter of firing pin is as small as possible. In order to achieve a target mass, so that the firing pin length increases. A reduction of axle stiffness and thereby a reduction of impact rate at the same speed achieved are the consequences.
  • support housings of hammers are constructed of several parts and connected with long screws, which by their elasticity, destroys destructive effects on the lower part of the hammer and the boom of the working machine. These screws are so strained that it comes not only to plastic deformation of nuts but also to screw break itself. The plastic deformation of nuts and bolts is eliminated during operation by regular tightening of the nuts. The residual energy of the working instrument is absorbed by a transverse pin. This results in damage to journal bearing in the tool and the pin itself. The weakened shank of the tool causes it to break during a lever action.
  • the working tool is stored in thermally hardened steel bushes in the lower part of the hammer.
  • the result is a dust and Unreingkeiteneintritt in the storage and not least an emergence of eccentric blows of the firing pin on the tool head.
  • For underwater work compressed air is therefore fed into the tool storage room.
  • Today solutions are known where the problem is solved by an elastic seal with simultaneous interval Fetzuschreib from Agregat the working machine.
  • the working tool transfers the pressing force of the working machine on the hammer over the circular ring surface, which resulted from reduction of the diameter of the tool head.
  • this makes the tool head weaker, which can be a cause of its demolition or smashing.
  • hammers for mechanical protection are encapsulated in another cabinet attached to the machine by means of an adapter.
  • the solutions are known, where to reduce adverse effects on the machine, the hammer is resiliently encapsulated in a cabinet. Or is it designed to prevent blank space.
  • the concept works with a continuous outflow flow and when the function starts up, the pressure in the hydraulic system increases up to the safety pressure value. That works unfavorable to the entire hydraulic system with simultaneous overheating of working fluid.
  • the cabinet is equipped with a Schalldammstoff to dampen the outer noise of the hammer.
  • a common feature of the hammer of world production is its very sophisticated technology, great mass, dimensions and sensitivity to rough treatments.
  • the above-mentioned ironing eliminates the invention with an inverse concept when serving as a firing pin cylinder, which is attached to a fixedly connected to a support housing piston rod.
  • the control comes from a hydraulic tilt circuit, which reacts only to the two end positions of the firing pin.
  • a mounted in the piston rod control switches at high speed the flow direction of the pressure working fluid. It is hydraulically braked in the end positions. In the case when the work tool leaves its work area, the pressure of liquid in the system decreases. This breaks the hammer action. There will be no idle strokes and the working fluid will not overheat.
  • a Hochdruckakkumulator used in other hammers is here replaced by a pressure transducer with a cylinder and a piston.
  • the piston has on one side a common with the firing pin low-pressure gas chamber.
  • the piston On the other side, the piston has a compensation chamber, which is connected only in its initial position with the gas chamber.
  • the cylinder of the pressure transducer is connected to the supply line of the working fluid.
  • the core of the hydraulic excavation hammer according to the invention is that in the upper part of the rotary support housing immovable piston rod is inserted with the piston.
  • a valve ring and a firing pin are pushed on the piston rod of the pressure transducer piston.
  • the firing pin is inserted in a box inserted to the inside of the support housing.
  • a continuous supply channel is arranged with branch paths. He is finished with a control canteen.
  • a jerk channel is set up with a branch line. Through the channels, the working fluid flows.
  • the piston rod further openings from its surface are created in the control canals.
  • a switching element of shell construction is inserted.
  • valve ring equipped with an internal recess is pushed with its underside onto the piston rod in the region of its reduced diameter.
  • the upper side of the valve ring is slid in the part on the piston rod body, where its diameter is not reduced.
  • the first channel is opened by control channels.
  • the working tool is applied from the second (lower) side, which is embedded in cans free of food.
  • the rifles are protected from the outside against the working environment. They are compacted and closed by a lid.
  • the short and stiff firing pin causes a greater rapidity of the blow.
  • the head diameter is therefore inversely increased.
  • the tool does not chip for a safety pin.
  • the tool of new form is unbreakable when levering.
  • the hammer allows underwater work without compressed air supply. With a sudden resistance breakthrough, the tool is axially cushioned. against idle beats the hammer is equipped with a safety circuit. When the striker goes into an out-of-work position, the pressure in the hydraulic system when using the circuit does not increase, contrary to the known solutions, to the value of safety pressure.
  • the control flip-flop is switched at full speed, it is in end positions hydraulically braked. It does not depend on hydraulic resistances. Very laborious decompression of hammer, which was previously realized by its superimposition in a cabinet superficially, is moved directly to the source of acoustic performance (firing pin - working tool) into its interior. Another advantage is small dimensions and less than half the mass of the known hammer, which extends its use in a larger scope of work machines.
  • the hammer contains no screw connections. The hammer parts are held together after assembly in the whole with sufficiently large forces, which are caused by the pressure of the filling gas. The filling gas is usually nitrogen. The hammer does not need maintenance. A smearing of rifles of the working tool comes from the low-pressure return line self-active.
  • Figure 1 shows schematically a longitudinal average of the hydraulic excavating hammer of the first example of the realization.
  • Fig. 2 shows an enlarged detail of the control unit from Fig. 1.
  • Fig. 3 shows schematically the hammer in a longitudinal average with another safety circuit according to the second embodiment.
  • the hydraulic mining hammer is assembled from four main parts. They are: a monolithic rotary support housing 1, a piston rod 2, a firing pin 3 and a working tool 4.
  • the piston rod 2 is immovably inserted. It is secured with a retaining ring 5 against a feed.
  • the firing pin 3 is pushed bewegich on the piston rod 2 . It is made as a rotary body which is axially drilled according to the diameter of piston rod 2 and has an internal recess.
  • After the use of the firing pin 3 on the piston rod 2 its cavity is divided by a sealed piston 21 into the first chamber 41 and the second chamber 42 .
  • the piston rod 2 has a reduced diameter at a portion in the region of the first chamber 41 .
  • valve ring 23 is pushed onto the piston rod 2 .
  • the length of valve ring 23 is greater than the length of the section where the piston rod 2 has its reduced diameter.
  • the valve ring 23 is adapted to the situation so that its end on the side closer to the piston 21 has an axis hole which corresponds to the diameter of the piston rod 2 in its non-reduced part.
  • the valve ring 23 has on its opposite side a forehead with an axis opening which corresponds to the diameter of the piston rod 2 in its reduced part.
  • the valve ring 23 has an inner recess between the two Endstirnen. After placement of valve ring 23 on the piston rod 2 , the recess between the two bodies forms a ring cavity 46.
  • a continuous supply channel 6 with the first branch 7, the third branch 9 and the fourth branch 10 is configured inside the piston rod 2 .
  • a subsequent room is linked.
  • the switching element 20 is designed as a ring with graduated outside and inside diameters so that the total area of its lower (left in the picture) forehead is greater than the total area of its upper (right in the picture) forehead.
  • a passage 14 and an inlet opening 15 is configured in the switching element 20 .
  • four cavities are provided in the inserted next following space. They include: the lower lumen 47, the lumen 48, the middle lumen 49 and the upper lumen 50.
  • the lower lumen 47 is connected to the lumen 46 through the first channel 16 .
  • the small cavity 48 is connected in the first chamber 41 to the surface of piston rod 2 through the lower nozzle 22 and the second channel 17 .
  • the fourth branch path 10 of the supply channel 6 is initiated. From the switching element side, the inlet port 15 is connected to it.
  • the upper cavity 50 is connected to the supply duct 6 through its third branch path 9 . With the surface of the piston rod 2 , it is connected through the fifth channel 31 and the upper nozzle 11 . From the surface of the piston rod 2 to the switching element 20 each carries a channel on the two sides of the piston 21; the third channel 18 leads out of the first chamber 41, the fourth channel 19 leads out of the second chamber 42. Through the third channel 18 and the passage 14 , the first chamber 41 is permanently connected to the return channel 12 configured in the piston rod 2 .
  • the firing pin 3 is inserted into a metal-free sealed axially displaceable sleeve 24 , which is pushed into the support housing 1 .
  • a small-scale pressure converter is still assembled in the upper (right) part of the piston rod 2 . It consists of a bell-shaped collet 25, a sealed cylinder 43 and a compensation chamber 44 so that the cylinder 43 is made from the walls of the piston 25 and the piston rod 2 and connected to the first branch path 7 of the supply channel 6 .
  • the sealed compensation chamber 44 is created between the piston 25 and the cover of piston rod 2 .
  • a gas chamber 45 is configured in the space defined by the support housing 1, sleeve 24, striker 5, piston rod 2 and pressure transducer piston 25 .
  • the compensation chamber 44 is connected to the gas chamber 45 through a connection channel 26 .
  • the working tool 4 is eilitz in the support housing 1 by means of a metal-free sleeve 27 , which is made in the realization example as a three-part 27.1, 27.2, 27.3 , wherein in its central part a spring insert 27.2 is used.
  • the sleeve 27 is sealed to the tool 4 with a Wegabstreifring 28 .
  • the wiper ring 28 has a support housing 1 against axially immovable seal.
  • the lower lid 29 is secured with a retaining ring 30 against extension.
  • the retaining ring 30 has by forces of gas pressure in the gas chamber 45 to a permanent bias.
  • the hammer is equipped with a safety circuit which is made by means of a connection of the bore 51 with the supply channel 6 through the first safety channel 53 and with the return channel 12 through the second safety channel 54 .
  • the bore 51 is made from the lower end of the piston rod 2 into its interior in the longitudinal axis direction of the piston rod 2 .
  • a movable piston 52 is inserted in the bore 51 in the bore 51 .
  • gas Prior to using the hydraulic excavating hammer, gas is forced into the gas chamber 45 at the required pressure through a not-shown passage and a shutter in the piston rod 2 .
  • the high-pressure gas pushes the firing pin 3 in the position in which he leans the sleeve 27 . Due to the movement, the head of the working tool 4 also delays from the end of the piston rod 2 .
  • the body of the firing pin 3 covers the upper nozzle 11 and the fifth channel 31.
  • the working fluid acts on the bottom of bore 51 to a pressure on the flask 52 and pushes it into a permanent contact with the tool 4.
  • the firing pin 3 pushes it out of the hammer so far out that the piston 52, following the movement of the tool 4, at its opposite end the previously closed by it connection of the supply channel 6 with the return channel 12th through the first and second safety channels 53, 54 opens. At that moment, the hammer loses the working pressure of the liquid, if it has become available earlier. As a result of the connection, the hammer is inoperable.
  • the piston 52 pushes into the piston rod 2 until it thereby to the interruption of the connection of the supply channel 6 with the return channel 12 in the bore 51 is coming.
  • the pressure increases.
  • the annular cavity 46 is filled with the hydraulic fluid through the first channel 16 : The hydraulic fluid moves the valve ring 23 in the lower (left) position until it stops.
  • the valve ring 23 In the position of the small cavity 48 with the first chamber 41 through the lower nozzle 22 and the second channel 17 are connected. Because the first chamber 41 is permanently connected to the return channel 12 , so also the small cavity 48 remains without increased pressure.
  • the end faces of switching element 20 thus creates an imbalance of forces, which brings the switching element 20 in rapid movement towards the lower cavity 47 .
  • the working fluid flows from the small cavity 48 through the second channel 17 and the lower nozzle 22 into the first chamber 41.
  • the pressure in the small cavity 48 is increased, causing intensive braking of the switching element 20 .
  • the tip-over of switching element 20 is terminated at a low speed in the emptying of small cavity 48 into the first chamber 41 only by the lower nozzle 22 .
  • the inlet port 15 is connected to the fourth channel 19 and the connection of the fourth channel 19 to the passage 14 of the switching element 20 is interrupted.
  • the pressure increases, which brings the firing pin 3 in a movement in the direction of the gas chamber 45 against the gas pressure.
  • the heavy firing pin 3 starts slowly.
  • the cylinder 43 of the light pressure transducer prevents an increase of pressure peak. It absorbs a deviation of the steady flow of working fluid supplied from the working machine.
  • the pressure transducer piston 25 thereby moves against the movement of the firing pin 3. After the start of the firing pin 3 at the speed corresponding to the feeding flow, the pressure transducer piston 25 is brought to a standstill due to increased gas pressure in the gas chamber 45 .
  • the lower nozzle 22 connects with the movement of the valve ring with the annular cavity 46 and the second channel is covered 17 from the valve annulus, the pressure increases in the small cavity 48. Because the joint end surface of switching element 20 in the sub-cavity 47 and the small cavity 48 is greater as the common end face in the central cavity 49 and upper cavity 50, the switching element 20 moves in the direction of the upper cavity 50 despite the high pressure of working fluid in all cavities The speed of its movement is increased by the connection of the second channel 17 with the annular cavity 46 in steps. During the movement, the second chamber 42 is separated from the supply passage 6 and connected to the first chamber 41 through the fourth passage 19, the passage 14 and the third passage 18 .
  • the safety circuit consists of the second branch track 8, a return branch track 13 and a safety chamber 40.
  • the second branch track 8 is drilled from the supply channel 6 to the surface of piston rod 2 .
  • the returning branch line 13 leads from the return channel 12 to the surface of the piston rod 2.
  • the securing chamber 40 is configured in the upper part of the firing pin 3 in its interior.
  • the second branch 8 and also the back branch 13 are configured in a plane perpendicular to the hammer longitudinal axis. The rest of Hammer's composition is identical to the previous example.
  • gas Prior to using the hydraulic excavating hammer, gas is forced into the gas chamber 45 at the required pressure through a not-shown passage and a shutter in the piston rod 2 .
  • the high-pressure gas pushes the firing pin 3 in the position in which he leans the sleeve 27 . Due to the movement, the head of the working tool 4 also delays from the end of the piston rod 2 .
  • the body of striker 3 conceals the upper nozzle 11 and the fifth channel 31.
  • the safety chamber 40, the second branch 8 and the return branch 13 connect the inlet channel 6 to the return channel 12.
  • connection of the supply channel 6 with the return channel 12 is thus interrupted.
  • the pressure increases.
  • the annular cavity 46 is filled with the pressurized working fluid through the first channel 16 .
  • the working fluid pushes the valve ring 23 in the lower (left) position until it stops. This starts the hammer action described in the first example.
  • the function of the safety circuit is the same even if the work object breaks through.
  • the working tool 4 is brought to a standstill. Spaces from Hammer are excluded.
  • An advantage of the hydraulic mining hammer according to the invention is its significantly increased performance due to high reaching to 90% of the effective force and an increased impact rate, which is caused by repeated axial stiffness of the firing pin 3 .
  • the hammer are predestined in the most difficult conditions without labor restrictions.
  • High switching speed in lower position of striker 3 strikingly reduces a momentum of retreat force.
  • Small dimensions and mass of hammer and great resistance to damage make it possible to use a hammer size on all machines up to the mass of 12.5 t.
  • the support housing 1 is only a rotating body without screw and transverse openings.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)
EP08779510A 2007-07-09 2008-07-08 Hydraulischer abbauhammer Not-in-force EP2173524B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL08779510T PL2173524T3 (pl) 2007-07-09 2008-07-08 Młot hydrauliczny rozruchowy

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SK93-2007A SK932007A3 (sk) 2007-07-09 2007-07-09 Hydraulické rozrušovacie kladivo
PCT/SK2008/000008 WO2009008844A1 (de) 2007-07-09 2008-07-08 Hydraulischer abbauhammer

Publications (2)

Publication Number Publication Date
EP2173524A1 EP2173524A1 (de) 2010-04-14
EP2173524B1 true EP2173524B1 (de) 2010-10-20

Family

ID=39865357

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08779510A Not-in-force EP2173524B1 (de) 2007-07-09 2008-07-08 Hydraulischer abbauhammer

Country Status (9)

Country Link
US (1) US8789617B2 (pl)
EP (1) EP2173524B1 (pl)
AT (1) ATE485133T1 (pl)
DE (1) DE502008001610D1 (pl)
ES (1) ES2357333T3 (pl)
PL (1) PL2173524T3 (pl)
RU (1) RU2449882C2 (pl)
SK (1) SK932007A3 (pl)
WO (1) WO2009008844A1 (pl)

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CN110359173A (zh) * 2019-08-14 2019-10-22 浙江慈鑫机械有限公司 一种电脑横机保护机构
KR102317232B1 (ko) * 2020-01-08 2021-10-22 주식회사 현대에버다임 유압 브레이커
CN113027447B (zh) * 2021-03-11 2023-04-18 重庆工程职业技术学院 一种煤矿开采机电设备

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CA2506840A1 (en) * 2004-05-17 2005-11-17 Bernard Lionel Gien Pneumatic hammer
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SK932007A3 (sk) * 2007-07-09 2009-02-05 Konek, S. R. O. Hydraulické rozrušovacie kladivo

Also Published As

Publication number Publication date
ES2357333T3 (es) 2011-04-25
US20100193212A1 (en) 2010-08-05
SK932007A3 (sk) 2009-02-05
RU2449882C2 (ru) 2012-05-10
ATE485133T1 (de) 2010-11-15
PL2173524T3 (pl) 2011-04-29
EP2173524A1 (de) 2010-04-14
DE502008001610D1 (de) 2010-12-02
RU2010103146A (ru) 2011-08-20
US8789617B2 (en) 2014-07-29
WO2009008844A1 (de) 2009-01-15

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