EP0368078B1 - Rutschkupplung zwischen dem Spulenkern einer Wickelspule eines Bürogerätes o. dgl. und einem zu diesem konzentrisch angeordneten Antriebs- oder Getrieberad. - Google Patents

Rutschkupplung zwischen dem Spulenkern einer Wickelspule eines Bürogerätes o. dgl. und einem zu diesem konzentrisch angeordneten Antriebs- oder Getrieberad. Download PDF

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Publication number
EP0368078B1
EP0368078B1 EP89119807A EP89119807A EP0368078B1 EP 0368078 B1 EP0368078 B1 EP 0368078B1 EP 89119807 A EP89119807 A EP 89119807A EP 89119807 A EP89119807 A EP 89119807A EP 0368078 B1 EP0368078 B1 EP 0368078B1
Authority
EP
European Patent Office
Prior art keywords
teeth
sliding clutch
clutch according
spool
core
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.)
Expired - Lifetime
Application number
EP89119807A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0368078A3 (en
EP0368078A2 (de
Inventor
Christoph Dipl.-Ing. Manusch
Hans-Jürgen Dipl.-Ing. Harp
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.)
Henkel Pritt Produktions GmbH
Original Assignee
Pelikan GmbH
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 Pelikan GmbH filed Critical Pelikan GmbH
Priority to AT89119807T priority Critical patent/ATE84014T1/de
Publication of EP0368078A2 publication Critical patent/EP0368078A2/de
Publication of EP0368078A3 publication Critical patent/EP0368078A3/de
Application granted granted Critical
Publication of EP0368078B1 publication Critical patent/EP0368078B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H75/00—Storing webs, tapes, or filamentary material, e.g. on reels
    • B65H75/02—Cores, formers, supports, or holders for coiled, wound, or folded material, e.g. reels, spindles, bobbins, cop tubes, cans, mandrels or chucks
    • B65H75/34—Cores, formers, supports, or holders for coiled, wound, or folded material, e.g. reels, spindles, bobbins, cop tubes, cans, mandrels or chucks specially adapted or mounted for storing and repeatedly paying-out and re-storing lengths of material provided for particular purposes, e.g. anchored hoses, power cables
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H37/00—Article or web delivery apparatus incorporating devices for performing specified auxiliary operations
    • B65H37/002—Web delivery apparatus, the web serving as support for articles, material or another web
    • B65H37/005—Hand-held apparatus
    • B65H37/007—Applicators for applying coatings, e.g. correction, colour or adhesive coatings

Definitions

  • the invention relates to a slip clutch between the core of a winding spool of an office device or the like. And a concentrically arranged to this drive or gear wheel, on its axis of rotation, evenly distributed around this, radially projecting and radially deflectable elastic pawls of the same Form are attached, with their free ends are in locking engagement with the coil core distributed over the inner circumference of the locking receptacles.
  • a donor spool e.g. a coated tape is pulled off, which has to be rewound uncoated on a take-up reel in the device after the release of its coating (e.g. an adhesive film, a cover-up film or the like)
  • its coating e.g. an adhesive film, a cover-up film or the like
  • coaxial slip clutches are therefore mostly used for the corresponding coil core.
  • a common form for such slip clutches is that the drive or gear wheel has a centrally projecting axle section which projects through a central opening of a central axle bolt attached to the associated coil in such a way that at its end it projects somewhat axially from this opening.
  • a metal clip is attached, the two side legs of which overlap from the outside the axle bolt of the coil and resiliently press against its outer surface.
  • This metal clamp which is rigidly connected in the direction of rotation to the drive or gear wheel, creates a frictional connection between the resilient legs and the axle pin of the coil, which acts as a slip clutch when a relative speed difference between the coil and the drive or gear wheel occurs.
  • slip clutches are relatively complex to install, which is particularly true for automatic assembly, which must also be seen as their main disadvantage.
  • they are expensive, since the use of metal clips as spring elements is generally necessary.
  • a film for example an adhesive film
  • the film layer is also removed from the tape at the end of the application (ie separated from the film layer still remaining on the tape) can be, without undesirably moving the spools, this would require such slip clutches that the preload of the metal clip would have to be chosen so strong that the running tape unwinding would then be very difficult.
  • Another known solution also has similar disadvantages, in which a "spring belt” transmission is used between the two coils, the spring belt of which slips when the speed of the coils is not the same. Although slight angular deviations can be compensated for here, the disadvantages resulting from the pure frictional engagement are still present and the assembly is complicated.
  • a coaxially effective slip clutch in which a clutch hood, which is provided on its inside diameter with circumferential corrugation, engages with the ends of the coupling wheel projecting radially outward, thin elastic angle pawls.
  • the coil is attached to this coupling hood with the coil core, with drivers formed on the coupling hood engaging in suitable shaped grooves on the inside of the coil core.
  • the disadvantages associated with a purely frictionally operating slip clutch are avoided in this known slip clutch, but it is still complex to assemble, which applies in particular to the special attachment of the elastic, radial pawls, particularly in the case of automatic assembly.
  • the known slip clutch is also expensive in terms of materials because of the majority of the individual parts used and thus overall in use. It is also unable to compensate for a slight angular misalignment between the axes of the coil and the drive wheel.
  • the object of the invention is to further develop a slip clutch of the type mentioned at the outset so that it is easier and quicker to assemble, can be produced with less effort, is cheaper overall and is particularly suitable for compensating for an angular offset between the axes of rotation of the coil and drive or gear wheel.
  • a slip clutch of the type mentioned in that the elastic pawls in the form of axially extending, radially obliquely outward from the drive or gear wheel projecting into the coil interior enclosed by the coil core, at their ends with at least one each radially outwardly directed locking teeth provided spring tongues are formed, the locking teeth are in engagement with a corresponding internal toothing on the coil core, the spring tongues being formed in one piece either with the drive or gear wheel or with a support plate coaxially fastened thereon.
  • the axially directed, radially outwardly expanding spring tongues work directly on an internal toothing on the coil core without the interposition of a clutch hood or the like, which results in a significant material saving compared to the generic solution.
  • the design of the locking devices by locking teeth on the one hand and an internal toothing on the coil core on the other hand ensures precisely definable engagement conditions in the locking area, whereby not only does a securely effective, precisely interpretable locking effect occur, but also very special locking effects can be achieved if desired.
  • the inventive design of the spring tongues and the resulting engagement situation on the internal toothing of the coil core also gives the possibility of compensating for an angular misalignment (whether intentionally or not) between the axes of rotation of the coil core and the drive or gear wheel without the desired slip clutch effect would be affected, which in any case at least simplifies assembly.
  • the slip clutch according to the invention in the case of a one-piece design of the spring tongues or pawls with the drive or. Gear wheel any need for separate attachment The same, the inventive design of this one-piece component is easy to manufacture.
  • the elastic tongues or pawls are formed in one piece with a support disk, which in turn is attached concentrically to the drive or gear wheel, the individual attachment of each tongue or pawl is no longer necessary, but only the attachment of one concentrically to the drive - or gear wheel to be attached, which does not pose any problems even with automatic assembly. Since the elastic tongues engage with their locking teeth directly in the internal toothing on the coil core of the coils to be plugged on, there is no need for any intermediate link and thus the material, production and assembly effort required for this.
  • Attaching the spool with its internal toothing to the spring tongues is only an axial push-on operation, which can be carried out easily and quickly, especially in the case of automatic assembly, so that the overall assembly of the slip clutch according to the invention can be carried out surprisingly easily and therefore particularly quickly, the entire material and manufacturing outlay is low and overall a particularly inexpensive construction is achieved.
  • the use of locking teeth specially designed at the ends of the spring tongues and a corresponding internal toothing does not cause any problems in terms of production technology, but it does guarantee precisely defined engagement conditions when engaging, which allow a precise design of the clutch to the desired release torque of the slip clutch, preclude randomness and, moreover, also achieve it special slip clutch effects, which will be discussed below.
  • the locking teeth and the teeth of the internal toothing can be designed in any shape suitable for a locking engagement.
  • the latching teeth and the teeth of the internal toothing are particularly preferably shaped such that they have a symmetrical tooth cross section, as a result of which a latching coupling effect can be achieved in both directions of rotation.
  • the symmetrical design of the teeth is preferably triangular in cross section, the tooth flanks of each tooth advantageously enclosing an angle of approximately 120 °.
  • An advantageous further embodiment of the slip clutch according to the invention also consists in that the teeth of the internal toothing of the coil core have a larger, preferably three times larger tooth height than the locking teeth of the elastic tongues, whereby a significant reduction in the wall thickness of the coil core can be achieved, which leads to a further, leads to noticeable material savings there.
  • the teeth of the internal toothing of the coil core and the latching teeth can also be advantageous in the latching coupling according to the invention to design the teeth of the internal toothing of the coil core and the latching teeth to be non-symmetrical, in order to obtain different opening moments for the latching-releasing torque in both directions of rotation.
  • a preferred asymmetrical design of the teeth is such.
  • the teeth of the internal toothing of the coil core as well as the locking teeth each have a radially extending side flank, while the other side flank is inclined to this, preferably at an angle of 60 °.
  • the desired slip clutch effect is achieved only in one direction of rotation, while in the other direction of rotation, when the radially extending side flanks of the two rows of teeth abut one another, there is in principle a blocking (without a slip effect).
  • the ratchet teeth can immediately spring out without it - as with a symmetrical tooth cross section - under the Tension of the carrier tape for an accelerated sliding down of the external toothing on the inclined side flank of the tooth adjoining the tooth tip of the ratchet tooth (in addition under the effect of the radially outward restoring force of the ratchet tooth) and thus an undesirable, sudden band relaxation occurs.
  • the pitch of the internal toothing is furthermore preferably less than half the width of the locking teeth supporting end portion of a spring tongue selected, whereby (seen in the circumferential direction) a one-sided rebound of a single tongue can be avoided because at least two teeth of the internal toothing are always in engagement with the locking teeth of the spring tongue.
  • teeth instead of a triangular configuration of the teeth, however, these can also be formed with a symmetrical cross section in the form of a circular section, the internal toothing having a correspondingly complementary shape, which can be particularly advantageous in certain applications.
  • the coil core with the internal toothing and the spring tongues with the locking teeth are made of plastic, which not only results in easy manufacture of the individual parts, but also results in favorable frictional conditions in the area of the locking engagement (plastic / plastic).
  • the spring tongues are arranged concentrically around the axis of rotation of the drive or gear wheel, with their sections arranged between the locking teeth and the drive or gear wheel preferably lying with their radial outer surfaces on the lateral surface of a truncated cone.
  • the spring tongues in this area are provided with a cross-section which tapers radially in the direction away from the drive or gear wheel, as a result of which overall a favorable rebound behavior with a stable overall arrangement can be achieved.
  • the spring tongues are particularly preferably provided with a thickened cross section at their end region carrying the latching teeth.
  • the teeth of the internal toothing are preferably arranged over substantially the entire axial width of the coil interior of the coil core, with, more preferably, the locking teeth at the end region of the coil toothing lying inside the coil core being in engagement therewith, as a result of which the force transmission effected at the latching point axially in the Close to the bearing point of the coil on the housing side can.
  • the distance between two spring tongues is smaller than the pitch of the internal toothing, thereby ensuring that between each spring tongue there is no more than one unloaded tooth of the internal toothing.
  • the pitch of the internal teeth should preferably be three times as large as the pitch of the locking teeth on the spring tongues, as a result of which very good results can be achieved.
  • FIG. 1 shows the section through the housing of an office hand dispenser formed from two housing halves 1, 2, with which an adhesive film applied to a carrying tape can be transferred to a substrate.
  • the film-coated carrying tape is located on a dispenser spool mounted in the housing in the form of a tape supply 4 wound on a spool core 3 (see FIGS. 1 and 2), from which it is drawn to one side (as shown in dash-dot lines in FIG. 2 and by the arrow) shown) is subtracted for use.
  • a winding spool (not shown in the figures) is arranged inside the housing 1, 2, onto which the film-coated carrier tape led out of the housing is wound again in the housing after the adhesive film has been released.
  • the coil core 3 of the dispenser coil is rotatably supported on a bearing collar 6, which is attached to one of its axial ends (facing the housing side wall) and rotatably supports the coil core 3 and which is attached to one of the side walls of the housing half 2 projecting collar 13 is formed in the interior of the housing.
  • a centrally arranged, hollow center shaft 10 protrudes from the gear wheel 7, which extends through the entire open width of the entire housing formed from the housing halves 1, 2 and at its two axial ends in each case on a short bearing pin projecting from the housing half 1 or 2 in question 12 or 11 rotates.
  • the outer surface of the gear wheel 7 facing the housing half 1 is supported axially against a thrust collar 14 which is concentrically circular around the bearing journal 12.
  • Each spring tongue 15 extends axially in the direction of the axis of rotation of the gear 7, but not parallel to it, starting from its point of mouth on the gear 7, rising obliquely radially outwards.
  • the outer surfaces of all spring tongues 15 thus lie on a truncated cone-shaped envelope surface.
  • the spring tongues 15 are each provided with at least one latching tooth 16 which projects radially outward, two latching teeth 16 being provided per spring tongue 15 in the embodiment shown in FIGS. 1 and 2, as shown in FIG. 2 is removable. These radial locking teeth 16 are in engagement with corresponding counter teeth of an internal toothing 17 which is formed on the inner circumference of the coil core 3.
  • the axial extent of the spring tongues 15 is so large that they only engage in the internal toothing 17 of the coil core 3 at a small axial distance from the front end of the bearing collar 6 projecting from the opposite housing half 2.
  • the power transmission between the teeth 16 and 17 is moved axially into a region which is very close to the bearing point of the coil core 3 on the housing side, as a result of which the tilting moments on the housing-side bearing which occur as a result of the axial spacing of the latching engagement point from this bearing point and are caused by the tooth-supporting forces the dispenser coil or its coil core 3 can be kept very low.
  • the locking teeth 16 and the counter teeth of the internal toothing 17 of the coil core 3 are each provided with a symmetrical cross section in the exemplary embodiment according to FIG. 2, FIG. 3 showing a greatly enlarged detail section from FIG. 2 for better illustration of the mutual tooth engagement and the tooth shapes.
  • both the locking teeth 16 on the spring tongues 15 and the teeth of the internal toothing 17 are triangular in cross section, the side flanks of the teeth enclosing an angle ⁇ (see FIG. 4) between them, which is 120 ° in the exemplary embodiment shown.
  • angle ⁇ see FIG. 4
  • the symmetrical tooth shapes shown give the possibility of a slipping clutch effect in both directions of rotation, as shown by the arrow indicated on both sides in FIG. 3.
  • the gear 7 meshes (directly or optionally with the interposition of a further intermediate gear) with a gear wheel, not shown in the figures, attached to the axis of rotation of the take-up spool for driving the take-up spool.
  • the gear ratio is chosen so that even with full tape supply still present on the dispenser spool, the speed of the dispenser spool is always greater than the speed of the gear wheel 7 specified via the take-up spool, so that its speed when using the device is always somewhat smaller than that by Pulling off the carrier tape is forced unwinding speed of the spool core 3, the occurring speed difference being compensated for by the described slip clutch.
  • the pitch t of the locking teeth 16 is the same size as the pitch T of the internal teeth 17, so that there are always two adjacent teeth of the internal toothing 17 with two adjacent, on a spring tongue 15 attached locking teeth 16 are engaged.
  • the tooth height H2 of the teeth of the internal toothing 17 is three times as large as the tooth height H1 of the locking teeth 16, which can achieve a significant and significant reduction in the circumferential load-bearing wall thickness of the coil core 3 (and thus a noticeable material saving) with good function.
  • a space of a width A is provided which is significantly smaller than the distance T between two adjacent teeth of the external toothing 17, which means that between two spring tongues 15 which follow one another in the circumferential direction, only one tooth of the external toothing 17 is always present Locking engagement or support on a spring tongue is.
  • a particularly large number of latching engagements on the teeth of the internal toothing 17 of the coil core 3 is achieved over the entire circumference, as a result of which the individual load that occurs per tooth engagement can be kept particularly low.
  • the locking effect is canceled, which it enables the tooth of the internal toothing 17 to slide down with its second flank along the other flank of the latching tooth 16, while at the same time the spring tongue 15 springs back radially outward in the direction of the arrow shown in FIG. 6 (and due to its pressure the sliding of the Counter tooth accelerated).
  • the internal toothing 17 can move freely in the drive direction relative to the spring tongues 15 until its side flank, which is in the drive direction, comes into contact again with the facing side flank of the following locking tooth.
  • each of the teeth of the internal toothing 17 as well as the locking teeth 16 has a side flank S1 which is purely radial (or only inclined by a small angle to the radial) ) is arranged, while the second side flank S2 of the tooth which is triangular in cross section is set at an angle ⁇ which is 60 ° in the example shown.
  • each spring tongue 15 is chosen to be significantly larger than the distance T (see FIG. 3) between two teeth of the external toothing 17, preferably larger than twice the distance T, so that always two teeth of the internal toothing 17 are in active engagement with each spring tongue 15 and a one-sided rebound of a spring tongue 15 is not possible.

Landscapes

  • Mechanical Operated Clutches (AREA)
  • Common Mechanisms (AREA)
  • Storage Of Web-Like Or Filamentary Materials (AREA)
  • Pulleys (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
EP89119807A 1988-11-05 1989-10-25 Rutschkupplung zwischen dem Spulenkern einer Wickelspule eines Bürogerätes o. dgl. und einem zu diesem konzentrisch angeordneten Antriebs- oder Getrieberad. Expired - Lifetime EP0368078B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89119807T ATE84014T1 (de) 1988-11-05 1989-10-25 Rutschkupplung zwischen dem spulenkern einer wickelspule eines buerogeraetes o. dgl. und einem zu diesem konzentrisch angeordneten antriebsoder getrieberad.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8813861U 1988-11-05
DE8813861U DE8813861U1 (ko) 1988-11-05 1988-11-05

Publications (3)

Publication Number Publication Date
EP0368078A2 EP0368078A2 (de) 1990-05-16
EP0368078A3 EP0368078A3 (en) 1990-05-30
EP0368078B1 true EP0368078B1 (de) 1992-12-30

Family

ID=6829574

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89119807A Expired - Lifetime EP0368078B1 (de) 1988-11-05 1989-10-25 Rutschkupplung zwischen dem Spulenkern einer Wickelspule eines Bürogerätes o. dgl. und einem zu diesem konzentrisch angeordneten Antriebs- oder Getrieberad.

Country Status (8)

Country Link
US (1) US5150851A (ko)
EP (1) EP0368078B1 (ko)
JP (1) JPH0631132B2 (ko)
KR (1) KR940001581B1 (ko)
AT (1) ATE84014T1 (ko)
DE (2) DE8813861U1 (ko)
ES (1) ES2037368T3 (ko)
GR (1) GR3006893T3 (ko)

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DE8813861U1 (ko) * 1988-11-05 1988-12-22 Pelikan Ag, 3000 Hannover, De
DE3902553C2 (de) * 1989-01-28 1993-12-23 Henkel Kgaa Handgerät zum Übertragen eines Filmes von einer Trägerfolie auf ein Substrat
DE3902552C1 (ko) * 1989-01-28 1990-04-26 Henkel Kgaa, 4000 Duesseldorf, De
HUT58474A (en) * 1989-06-27 1992-03-30 Richter Gedeon Vegyeszet Herbicidal compositions, as well as process for applying them and for producing the active ingredients
JP2532967Y2 (ja) * 1991-05-09 1997-04-16 ゼネラル株式会社 塗布膜転写具
JP2639606B2 (ja) * 1991-08-30 1997-08-13 シードゴム工業株式会社 塗膜転写具
US5316613A (en) * 1991-09-06 1994-05-31 Minnesota Mining And Manufacturing Company Definite length transfer adhesive dispenser
US5310445A (en) * 1992-10-15 1994-05-10 The Gillette Company Tape dispenser
JP2540232Y2 (ja) * 1992-12-28 1997-07-02 東洋ケミカル株式会社 両面粘着転写テープの自動転写器
GB2275042B (en) 1993-02-10 1995-10-25 Gillette Co Correction tape dispenser
JP3221207B2 (ja) * 1994-02-23 2001-10-22 アイシン精機株式会社 ヘツドレスト装置
DE19606626C2 (de) * 1996-02-22 1998-05-20 Pritt Produktionsgesellschaft Reibungsbremse für einen Dispenser zur drehmomentbegrenzenden Kraftübertragung zwischen einem Spulenkern einer Spule zum Auf- oder Abwickeln eines Bandes und einer Drehaufnahme
JP3296265B2 (ja) * 1997-09-12 2002-06-24 株式会社シード 塗膜転写具のクラッチ機構および塗膜転写具
US6085612A (en) * 1998-08-05 2000-07-11 Lord Corporation Elastomer detent assembly
DE19936445B4 (de) 1999-08-03 2004-03-04 SOCIéTé BIC Handgerät zum Übertragen eines Filmes von einem Trägerband auf ein Substrat
CN1258410C (zh) * 2001-09-28 2006-06-07 美克司株式会社 钢筋捆扎机和用于该机器的卷盘
US7147179B2 (en) * 2001-09-28 2006-12-12 Max Kabushiki Kaisha Reinforcement binding machine and reel used for the machine
DE60214330T2 (de) * 2002-01-16 2007-10-04 3L-Ludvigsen A/S Vorrichtung zum Ausgeben von zweiseitig klebenden Klebeband
JP2005199631A (ja) * 2004-01-19 2005-07-28 Kokuyo Co Ltd 転写具
CN100484856C (zh) * 2004-11-22 2009-05-06 覃通衡 卷膜等分分页轮
US7438457B2 (en) * 2005-11-14 2008-10-21 Asyst Technologies, Llc Input shaft for a lamp adjuster
EP1806309A1 (en) * 2006-01-04 2007-07-11 Société BIC Tape dispenser with protector
CN101376063B (zh) * 2007-08-31 2011-03-23 鸿富锦精密工业（深圳）有限公司 关节
US8397784B2 (en) 2010-08-31 2013-03-19 Sanford, L.P. Correction tape dispenser with variable clutch mechanism
US8746313B2 (en) 2010-12-29 2014-06-10 Sanford, L.P. Correction tape re-tensioning mechanism and correction tape dispenser comprising same
US8578999B2 (en) 2010-12-29 2013-11-12 Sanford, L.P. Variable clutch mechanism and correction tape dispenser with variable clutch mechanism
US8746316B2 (en) 2011-12-30 2014-06-10 Sanford, L.P. Variable clutch mechanism and correction tape dispenser with variable clutch mechanism
KR101170046B1 (ko) * 2012-06-07 2012-07-31 임지훈 예초기용 안전판 충격흡수장치
WO2018009722A1 (en) * 2016-07-06 2018-01-11 Michael Bellon Action figure

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Also Published As

Publication number Publication date
DE58903170D1 (de) 1993-02-11
ATE84014T1 (de) 1993-01-15
KR940001581B1 (ko) 1994-02-25
EP0368078A3 (en) 1990-05-30
GR3006893T3 (ko) 1993-06-30
KR900007620A (ko) 1990-06-01
JPH02243482A (ja) 1990-09-27
JPH0631132B2 (ja) 1994-04-27
US5150851A (en) 1992-09-29
EP0368078A2 (de) 1990-05-16
DE8813861U1 (ko) 1988-12-22
ES2037368T3 (es) 1993-06-16

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