WO2002025119A1 - Agencement hydraulique - Google Patents

Agencement hydraulique Download PDF

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Publication number
WO2002025119A1
WO2002025119A1 PCT/SE2001/001941 SE0101941W WO0225119A1 WO 2002025119 A1 WO2002025119 A1 WO 2002025119A1 SE 0101941 W SE0101941 W SE 0101941W WO 0225119 A1 WO0225119 A1 WO 0225119A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
valve
valve body
chamber
conduit
Prior art date
Application number
PCT/SE2001/001941
Other languages
English (en)
Inventor
Håkan OLSSON
Original Assignee
Morphic Technologies Aktiebolag
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 Morphic Technologies Aktiebolag filed Critical Morphic Technologies Aktiebolag
Priority to AU2001288154A priority Critical patent/AU2001288154A1/en
Publication of WO2002025119A1 publication Critical patent/WO2002025119A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/22—Synchronisation of the movement of two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors

Definitions

  • the invention relates to a hydraulic device for the synchronization of two interacting hydraulic pistons, preferably two counter-impacting pistons for moulding at a high speed, comprising a first hydraulic piston and a second hydraulic piston, respectively; a first and a second hydraulic cylinder, respectively; one to each hydraulic piston arranged pressing portion/impact portion; a return surface and a working surface; a return chamber and a working chamber provided in each cylinder; a hydraulic conduit connected to each chamber; and at least a valve device for controlling the flow of oil to at least one of said conduits to synchronize the movements of the hydraulic pistons, characterized in that said valve device is connected between the conduit to the return chamber of the first hydraulic cylinder and to the working chamber of the second hydraulic cylinder, and that the conduit to the working chamber of the first hydraulic cylinder is connected to the conduit to the return chamber of the second cylinder.
  • Impact machines for working of principally metal utilizing high kinetic energy are machines for working in the first place metal, such as cutting, punching, plastic forming of powder components, powder compaction, and similar operations, wherein the velocity of a ram, which may be a press piston, may be essentially higher than in conventional presses. Also polymeric and ceramic working materials may be conceivable, as well as different composites of metals, polymers and cerams.
  • the working principle is based on the development of a very high kinetic energy of short duration instead of a high static press force of long duration.
  • the dynamic forces of short duration which are generated at the ram impact and which in impact machines of prior art are conveyed around in the system via stands and foundations, may be several thousand times larger than with conventional presses and implies that considerable amounts of energy are lost in stands and foundations in stead of being utilized in an optimal manner for an effective work.
  • impact machines of prior art are equipped with very strong and heavy stands and foundations according to the principles which are common in connection with conventional presses. Nevertheless, the dynamic, force pulses of shock type that are generated in impact machines are not damped in such heavy, conventional systems.
  • a hydraulic device for the synchronization of two interacting hydraulic pistons preferably two counter-impacting pistons for moulding at a high speed, comprising a first hydraulic piston and a second hydraulic piston, respectively; a first and a second hydraulic cylinder, respectively; a to each hydraulic piston arranged pressing portion/impact portion; a return surface and a working surface; a return chamber and a working chamber provided in each cylinder; a hydraulic conduit connected to each chamber; and at least one valve device for controlling the flow of oil • to at least one of said conduits to synchronize the movements of the hydraulic pistons, characterized in that said valve device is connected between the conduit to the return chamber of the first hydraulic cylinder and the working chamber of the second hydraulic cylinder, and that the conduit to the working chamber of the first hydraulic cylinder is connected to the conduit to the return chamber of the second cylinder. Due to this solution a reliable and a cost efficient device for the synchronization of two hydraulic pistons can be achieved.
  • a refilling conduit connects to the connection between the working chamber of the first hydraulic cylinder and the return chamber of the second cylinder; - the pressure P2 in said refilling conduit is essentially lower than the pressure PI supplied to said valve device, and a non-return valve is provided in said refilling conduit;
  • a pressure sensing cut-off valve is provided in series with said non-return valve.
  • valve device 1 comprises a valve housing 1 with a valve body 2 movably arranged within the valve housing, and at least a control mechanism 4 for controlling said movable valve body 2, wherein the valve body 2 is essentially sleeve-shaped and provided within the valve housing 1 ;
  • valve body 2 is provided within the valve housing 1 in such a manner that it is essentially, preferably completely, counter-balanced in respect of hydraulic forces, acting in the radial direction;
  • valve body 2 is provided with a plurality of apertures 252, 261, 262 to enable the flow of hydraulic liquid in the radial direction through the valve body 2;
  • 272A, 272B interact with the edge portions 103C, 104C and the channels 160, 164 provided inside the valve housing 1 in such a manner that hydraulic liquid is allowed to flow from each of said channels and beyond and between each of said edge portions, when the valve body 2 is positioned within the valve housing 1 to allow flow of oil to and from said hydraulic chamber 115, and that said edge portions at a different position of the valve body 2 interacts in a sealing manner, so that hydraulic liquid cannot flow to and from said hydraulic chamber 115;
  • - the maximal, necessary movement of the valve body 2 within the valve housing 1 to move the valve body 2 from a completely closed position to a completely open position is between 0.1 and 3 % of the outer diameter D of the sleeve, preferably below 2 %, and more preferred below 1 %;
  • - me adjustment time for the valve body 2 from one end position to the other end position is below 10 msec, preferably below 5 msec;
  • said device is part of an impact/pressing means intended to perform rapid impacts and/or to transmit heavy forces, wherein the valve body 2 has at least an inner diameter between 3 and 500 mm, preferably exceeding 50 mm, and more preferred exceeding 80 mm.
  • Fig. 1 shows a principal connection diagram for a hydraulic device according to the invention
  • Fig. 2 shows a preferred embodiment of a valve device according to the invention
  • Figs. 3 to 5 show different cross sections of a valve device according to Fig. 2
  • Fig. 6 shows the principal construction of an impact machine, which advantageously is provided with a hydraulic device according to the invention.
  • FIG. 1 a principal connection diagram of a hydraulic device according to the invention is shown.
  • a first hydraulic piston 400 and a second hydraulic piston 500, respectively, and a first 410 and a second 510 hydraulic cylinder, respectively, are shown.
  • a press portion/impact portion 501 and 401, respectively, a return surface 402 and 502, respectively, and a working surface 403 and 503, respectively, are shown.
  • a return chamber 411 and 511, respectively, and a working chamber 412 and 512, respectively, are provided in each cylinder.
  • a hydraulic conduit 420, 430, 520, 530 are connected to each chamber 411, 412, 511, 512.
  • a valve device 1 is connected between the conduit 430 to the return chamber 411 of the first hydraulic cylinder, and to the working chamber 512 of the second hydraulic cylinder. Further it is shown, that the conduit 420 to the working chamber 412 of the first hydraulic cylinder is connected to the conduit 530 to the return chamber 511 of the second cylinder. Pressurized oil PI is transmitted through the valve device 1 at a high pressure (e.g. about 300 bars) to one or the other of the connected conduits 430 and 520, respectively. Further it is shown that a refilling conduit 600 connects to the connection 420, 530 between the working chamber 412 of the first hydraulic cylinder and to the return chamber 511 of the second cylinder. The pressure P2 in said refilling conduit 600 is essentially lower (e.g.
  • a non-return valve 601 is provided in said refilling conduit 600 to prevent a return flow. Further, a pressure sensitive cut-off valve 603 is provided in series with said non-return valve 601, so that the refilling conduit only opens when a certain comparatively low pressure exists in the connection conduit 420, 530.
  • the device of Fig. 1 functions such that when the upper conduit 430, as regarded from the valve, is pressurized, oil will be supplied to the return chamber 411 of the upper piston at 300 bars. Simultaneously, the working chamber 512 of the lower piston opens to the tank through a conduit 520. Then, a return stroke will begin, wherein oil is pressed out of the working chamber 412 of the upper piston and further through the connection conduit 430, 520 to the return chamber 511 of the lower piston. Thereby a synchronous return movement is thus achieved.
  • the piston have moved the entire return stroke and have been positioned in an exactly correct starting position (preferably through stop lugs, not shown, provided within the cylinder or through position sensors), the working stroke may begin.
  • valve device 1 is reversed, so that the pressure PI is directed to the lower conduit 520 while the upper conduit is connected to the tank.
  • the working chamber 512 will then be filled with highly pressurized oil, which will press against the larger working surface A2, so that the piston starts to move inwardly (upwardly in the figure).
  • the oil in the upper chamber 511 is then pressed out and flows through the connection conduit 530 into the working chamber 412 of the second cylinder, whereby a synchronous working stroke may be performed.
  • a direction valve of standard type be used as the valve device 1, but in order to be able to perform such a working stroke at a heavy force/high, kinectic energy it is advantageous that very rapidly be able to create the necessarily large flow paths, which implies certain requirements on the valve device 1, which are not met without problems by such devices according to prior art.
  • a preferred valve device is shown, which should be used in a hydraulic device according to Fig. 1 (it is, however, realized that the invention is not limited to the use of such a valve).
  • valve device 1 in a longitudinal cross section, according to a preferred embodiment of the invention.
  • the device comprises a valve housing 100, a valve body 2 movably arranged within the valve housing, and a control mechanism 4.
  • the valve housing 100 consists of a plurality of assembled parts, comprising an upper cover 102, an inner valve seat portion 103 , and an outer valve seat portion 104. At the lower end of both said portions 103, 104 a lower cover 106 is provided. At the very back of the valve housing 1 a lower and an upper, respectively, cavity/chamber 115 and 116, respectively, is provided, being separated by a wall portion 34, which is parallel to a plane PI across the longitudinal direction of the valve housing 100. There is a conduit 430 and 520, respectively, in communication with each cavity/chamber 115 and 116, respectively, (see Fig. 1).
  • annular channel 151 In the outer valve seat portion 104 there is provided at least one inlet 107 for hydraulic liquid. In direct connection to the inlet 107 an annular channel 151 is provided (see also Fig. 3, which is a cross section along the line A-A of Fig. 2). In connection to said annular channel 151 there is a slot shaped cylindrical space 129, between the outer valve seat portion 104 and the inner valve seat portion 103, intended for the valve body 2, which is sleeve-shaped.
  • annular edge portions 103,A, 103B, 104A, 104B interact with corresponding edge portions 271 A, 271B, 273A, 273B on the axially movable valve body 2.
  • valve housing 104, 103 and the valve body 2, respectively, are provided with four such annular edge means, arranged in pairs, of which only two interacts at a • time in an opening manner while the other two pairs interact in a closing manner.
  • valve body 2 is provided with radial apertures 252, 261, 262, 263 ,264 to enable the desired flows and hence the desired adjustment (see Fig. 3).
  • a number of radial apertures 261 and 262, respectively, are provided in the valve body 2 in a symmetric manner in relation to the centre plane PI (see also Fig. 4).
  • Said apertures provide communication between an outer annular chamber 163 and 164, respectively, which is provided in the outer valve seat portion 104 and an inner annular chamber 161 and 160, respectively, provided in the valve seat portion 103.
  • Said inner chambers 160 and 161, respectively, communicate directly with the apertures 124 and 153, respectively, leading to respective pressure chamber 115 and 116, respectively, to which the respective hydraulic conduit 430 and 520, respectively, is connected.
  • a valve body is shown, which is provided with an additional set of radial apertures 263 and 264, respectively, which are symmetrically arranged in relation to said plane PI, and which are provided in the lower annular chamber 162 and the upper annular chamber 165, respectively.
  • Said lower and upper annular chambers, respectively, communicate directly with the lower 119 and the upper 119B, respectively, outlets leading to a tank (see also Fig. 3).
  • Channels and apertures are arranged in the same way in connection to the outlet to the tank 119 as in connection with the channels communicating with the pressurized opening 107, so that a mirror symmetry in principle exists around a plane P 1. Further, there is shown (see also Fig. 5) that there are arranged a plurality of inlets 107 for hydraulic liquid.
  • valve body 2 there are arranged one (or several) electro magnets 42 A and 42B, respectively, for the adjustment of the valve body 2. Due to the limited movement requirement of the valve body said adjustment/movement of the valve body 2 can advantageously be performed in a magnetic way.
  • the valve body 201 is magnetic us such, and therefore the electro magnets 42 A, 42B on each sides of the valve body 2 may be utilized to control the positioning of the valve body 2.
  • a valve device functions as follows. Pressure exists through the inlets 107 and thus pressurizes the annular chamber 151 being in communication with the central apertures 252 of the valve body 2. When the positioning according to Fig. 2 is reached, no flow of hydraulic oil in any direction takes place, as all flow paths out of the annular chamber 151 and 260, respectively, are sealed, when the edges are overlapping somewhat. When the upper electro magnet 42B is provided with current, the magnetic field will move the valve body 2 in an upward direction of the figure.
  • openings will be created along the entire edge lines between the annular edge portions 271A, 271B and 272A, 272B, respectively, so that oil may flow between the annular slots provided between the edge portions 104 A, 27 IB and 103 A, 271 A, respectively, from the central annular chamber 151 and 260, respectively, up into the upper annular chambers 161 and 163, respectively.
  • the pressurized oil may then freely flow into the upper chamber 116 through the radial apertures 124 and then through the conduit 430 pressurize the return chamber 411 to the upper piston 400.
  • the movement of the valve body 2 may be reversed by means of the lower magnetic device 42A, and an inverted pressurization and drainage, respectively, may take place so that the pistons 400, 500 instead perform a working stroke.
  • the unbroken, interacting edge lines, e.g. 104C and 272A imply that an extremely small movement of the valve body 2 causes a large opening, i.e. that a large annular slot is formed so that large flows may be achieved.
  • the outer diameter D of the valve body is 100 mm, which at a movement of the valve body by only 1 mm gives a, in relation to the movement, very large through-flow opening. (The total area will be about 600 ram (» D x ⁇ x 2), as the edge portion gets all around.)
  • valve body 2 all the time is in the counter-balanced state, in the radial direction, as the radially exposed surfaces of the valve body in each chosen point are subject to a counter-directed radial force, which is equally great on the opposite side of the valve body 2.
  • This is achieved thanks to the annular recesses which- are provided in a symmetrical manner around the valve body and to the openings in the valve body, which makes communication between said annular spaces possible.
  • an impact machine is shown as an example, which machine is generally designated 31, and which is especially suitable to be provided together with a hydraulic device according to Fig. 1. Its main components consist of an upper impact unit 32; a lower impact unit 33; a central unit 34; an upper stand 36 consisting of a pair of upper rods 38 constituting a pair of piston rods; and a lower stand 37 consisting of a pair of lower rods 39 also constituting a pair of piston rods.
  • a foundation has been designated 35.
  • the upper impact unit 32 comprises a yoke 310 on the piston rods 38 and may be raised and lowered by means of a pair of upper, hydraulic lifting cylinder 312 being connected to the foundation 35, wherein the hydraulic chamber of lifting cylinders are filled with and emptied of hydraulic fluid through the hydraulic conduits extending through the piston rods 38 and the yoke 310 from and to a pressure source and a tank, respectively.
  • the yoke 310 supports an upper, hydraulic impact cylinder 410 connected to the yoke, which cylinder contains an upper ram in the form of an impact piston 400 (see Fig. 1).
  • An upper impact body is designated 315. Said body is movable in an upper impact body cylinder 316.
  • An upper punch 317 is replaceably connected to the impact body 315.
  • the upper impact body cylinder 316 is fixedly connected to the upper impact cylinder 313.
  • the lower impact unit 33 comprises a lower yoke 320 suspending in the rods 39 consisting of a pair of piston rods, which may be raised and lowered by a pair of lower, hydraulic lifting cylinders 322, which are also connected to the foundation 35, and which are filled with and emptied of hydraulic fluid through the hydraulic conduits through the piston rods 39 and the yoke 320 from and to a pressure source and a tank, respectively.
  • the yoke 320 supports a lower hydraulic impact cylinder 510 connected to the yoke, which cylinder contains a lower ram in the form of an impact piston 500 (see Fig. 1).
  • a lower impact body is designated 325. Said body is movable in a lower impact body cylinder 326.
  • the central unit 34 comprises a table 330, which may be movable in the horizontal plane but which in principle is fixed in the vertical direction, but means may be provided to allow a certain flexibility in the vertical direction.
  • the means for movements in the horizontal plane and for damping/resilience in the vertical direction • are only symbolically shown in Fig. 6 and are designated 331.
  • the table 330 contains and supports a number of identically similar, functional units 332.
  • the main parts of the functional unit 332 shown in Fig. 1 comprise a lower, tubular punch 327; a die 334; a lower punch holder 336, which is slidably movable in a punch holder controller 337; and a mandrel 335.
  • the described equipment functions as follows.
  • the working material 90 may constitute of a ring of metal, of polymer or of a composite material, which may include a ceram or any other mouldable material, but in this example it is presumed that the working material is a metal powder, possibly a composition of metal and ceramic powder.
  • the upper yoke 310 is lowered by means of the upper lifting cylinders 312 and the piston rods 38 conveying tine upper impact body cylinder 316 and its impact body 315 so far that the upper, tubular punch 317 is brought down to contact with the metal powder 90 in the moulding cavity and begins to compress the powder until the pressure reaches a certain predetermined value. The movement is stopped and the position is maintained.
  • the yoke 324 now begins to move upwardly by means of the lifting cylinders 322, whereby the lower punch is pressed upwardly against the powder 90. The movement continues until the pressure reaches a certain predetermined value. Said pressure is then also via the powder 90 transmitted to the upper impact unit. The powder 90 is hence pre-compressed and centered in the moulding cavity in the die 334.
  • the impact machine is now ready to consolidate the powder in a single, simultaneous stroke by the two rams 400 and 500 to form the desired article. Thanks to the device according to Fig. 1, it will be possible to perform two completely synchronized strokes for forming the powder 90. If a valve device according to Fig. 2 to 5 is used, extremely heavy forces/great accelerations are created.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

La présente invention concerne un dispositif hydraulique de synchronisation de deux pistons hydrauliques interactifs, de préférence au moins deux pistons exerçant un contre-choc destinés au moulage à une énergie cinétique élevée, comprenant au moins un premier piston hydraulique (400) ainsi qu'au moins un second piston hydraulique (500), respectivement, au moins un premier cylindre hydraulique (410) et au moins un second cylindre hydraulique (510), respectivement, une partie de pression/partie de choc (501 et 401 respectivement) agencée sur chaque piston hydraulique, une surface de retour (402 et 502 respectivement), et une surface de travail (403 et 503 respectivement), une chambre de retour (411 et 511 respectivement) ainsi qu'une chambre de travail (412 et 512 respectivement) prévues dans chaque cylindre, un conduit hydraulique (420, 430, 520, 530) connecté à chaque chambre (411, 412., 511, 512) ainsi qu'au moins un dispositif à soupape (1) destiné à réguler l'écoulement d'huile vers au moins un desdits conduits pour synchroniser les mouvements des pistons hydrauliques (400, 500).
PCT/SE2001/001941 2000-09-20 2001-09-12 Agencement hydraulique WO2002025119A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001288154A AU2001288154A1 (en) 2000-09-20 2001-09-12 Hydraulic arrangement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0003343-1 2000-09-20
SE0003343A SE517223C2 (sv) 2000-09-20 2000-09-20 Hydraulanordning för synkronisering av åtminstone två samverkande hydraulkolvar

Publications (1)

Publication Number Publication Date
WO2002025119A1 true WO2002025119A1 (fr) 2002-03-28

Family

ID=20281078

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2001/001941 WO2002025119A1 (fr) 2000-09-20 2001-09-12 Agencement hydraulique

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AU (1) AU2001288154A1 (fr)
SE (1) SE517223C2 (fr)
WO (1) WO2002025119A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102384122A (zh) * 2011-10-27 2012-03-21 江苏润泰胶业有限公司 多气缸同步运行装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3769881A (en) * 1970-06-17 1973-11-06 K Aoki Hydraulic device
EP0231735A1 (fr) * 1985-12-30 1987-08-12 HOERBIGER HYDRAULIK GmbH Dispositif de synchronisation pour l'entraînement hydraulique à multiples cylindres
WO1995011190A1 (fr) * 1993-10-22 1995-04-27 Ravaglioli S.P.A. Dispositif de levage electro-hydraulique pour vehicules a moteur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3769881A (en) * 1970-06-17 1973-11-06 K Aoki Hydraulic device
EP0231735A1 (fr) * 1985-12-30 1987-08-12 HOERBIGER HYDRAULIK GmbH Dispositif de synchronisation pour l'entraînement hydraulique à multiples cylindres
WO1995011190A1 (fr) * 1993-10-22 1995-04-27 Ravaglioli S.P.A. Dispositif de levage electro-hydraulique pour vehicules a moteur

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102384122A (zh) * 2011-10-27 2012-03-21 江苏润泰胶业有限公司 多气缸同步运行装置

Also Published As

Publication number Publication date
SE517223C2 (sv) 2002-05-14
AU2001288154A1 (en) 2002-04-02
SE0003343L (sv) 2002-03-21
SE0003343D0 (sv) 2000-09-20

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