WO2005046977A1 - Appareil de broyage - Google Patents

Appareil de broyage Download PDF

Info

Publication number
WO2005046977A1
WO2005046977A1 PCT/IB2004/052365 IB2004052365W WO2005046977A1 WO 2005046977 A1 WO2005046977 A1 WO 2005046977A1 IB 2004052365 W IB2004052365 W IB 2004052365W WO 2005046977 A1 WO2005046977 A1 WO 2005046977A1
Authority
WO
WIPO (PCT)
Prior art keywords
rack
formations
pinion
teeth
crushing apparatus
Prior art date
Application number
PCT/IB2004/052365
Other languages
English (en)
Inventor
Peter B Dugmore
Anthony E Bull
Stanford W G Reynolds
Original Assignee
Peter B Dugmore
Anthony E Bull
Stanford W G Reynolds
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 Peter B Dugmore, Anthony E Bull, Stanford W G Reynolds filed Critical Peter B Dugmore
Publication of WO2005046977A1 publication Critical patent/WO2005046977A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/32—Presses specially adapted for particular purposes for consolidating scrap metal or for compacting used cars
    • B30B9/321—Presses specially adapted for particular purposes for consolidating scrap metal or for compacting used cars for consolidating empty containers, e.g. cans
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B9/00—Presses specially adapted for particular purposes
    • B30B9/30—Presses specially adapted for particular purposes for baling; Compression boxes therefor
    • B30B9/306—Mechanically-driven presses
    • B30B9/3067—Mechanically-driven presses by rack-and-pinion means
    • 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
    • F16H—GEARING
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
    • F16H19/043—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack for converting reciprocating movement in a continuous rotary movement or vice versa, e.g. by opposite racks engaging intermittently for a part of the stroke

Definitions

  • THIS INVENTION relates to a crushing apparatus, with particular reference to a can crushing apparatus.
  • fulcrum-based or lever-actuated can crushing devices are potentially hazardous, in that the moving linkages tend to provide a number of potential digit crushing zones, especially in the case of young children.
  • Manually operable crushing mechanisms also either tend to be over-engineered, on the one hand, or substantially under-engineered on the other in order to minimize the cost of materials.
  • Most manual devices require the compaction mechanism to be reset between each compaction stroke. They are moreover normally characterized by a lack of any ready manner of distinguishing between or separating aluminium and steel or tin-plated cans.
  • a crushing apparatus comprising: a framework having a first end wall defining a first fixed crushing surface; a compression ram mounted for reciprocal motion within the framework and defining a first movable crushing surface; a rotary-to-linear crawl mechanism including at least one toothed rack formation and a complementally toothed pinion formation carried on the rack formation; and drive means for crawling the mechanism in a first linear direction so as to crush an object placed between the first movable and fixed surfaces.
  • the framework includes a second opposed end wall defining a second fixed crushing surface
  • the compression ram defines a second movable crushing surface opposite the first movable crushing surface, with the toothed rack formation extending between the first and second end walls, whereby the drive means is arranged to crawl the pinion formation along the rack formation in a second opposed linear direction to crush an object placed between the second movable and fixed surfaces.
  • continued reciprocating motion of the compression ram is arranged alternatively to crush objects placed successively between the first fixed and movable crushing surfaces and the second fixed and movable crushing surfaces respectively.
  • the drive means may comprise an electrical or similar motor. Typically, it may comprise a manually operable crank arm and handle, or the like.
  • the toothed rack formation comprises a plurality of rack plates in an adjacently stacked arrangement, each rack plate carrying a substantially identical row of teeth; and the complementally toothed pinion formation comprises a matching number of pinion gears in a co-operating adjacently stacked arrangement.
  • rows of teeth on adjacent rack plates and co-operating pinion gears are offset by a matching degree.
  • the degree of offset may be one half pitch.
  • the toothed rack and pinion formations may comprise a common rack or pinion base member respectively, on which are cut one or more mutually offset and adjacent sets of teeth.
  • controlled gear slippage means may be effected by providing a special profile of the intermeshing gear teeth, whereby negligible clearance between the respective addenda and dedenda of the mating teeth of the respective pinion and rack formations is provided.
  • Adjacent sets of teeth may also or alternatively be provided with complementary rolling formations to further reduce wear on the gear train.
  • the rolling formations may comprise side- or spacer- plates running respectively contiguous to or interposed between adjacent rack plates, the side- or spacer- plates being designed to guide complemental rollers arranged to be mounted for rolling movement beside, or within gaps defined between, adjacent, complemental pinion gears.
  • the roller diameter may conveniently correspond to the pitch circle diameter of the pinion gears and rack plates.
  • At least one idler shaft carrying two or more idler pinion formations and at least one drive shaft carrying two or more drive pinion formations for driving the idler pinion formations may typically be journalled within the compression ram, with the framework advantageously defined by two pairs of spaced apart rack formations joining the first and second end walls, each pair being coplanar with a drive pinion formation and an idler pinion formation.
  • the ram may include a magnetic circuit for selectively attracting ferromagnetic cans
  • the crushing apparatus may comprise at least one outer opening adjacent the first end wall for discharging non-ferromagnetic cans and at least one central opening for discharging ferromagnetic cans.
  • the magnetic circuit includes a central magnet, a pair of pole pieces on the opposed first and second moving faces of the ram, and a toggle mechanism for moving the magnet between the first and second pole pieces for selectively attracting cans to and releasing cans from the first and second moving faces of the ram.
  • a crawl mechanism assembly comprising: a mechanism containment formation; a rotary-to-linear crawl mechanism; and drive means for crawling the mechanism linearly within the containment formation.
  • the containment formation may advantageously comprise a framework.
  • the mechanism will comprise at least one toothed rack formation and a * complementally toothed pinion formation carried on the rack formation, the pinion formation defining an axis of rotation.
  • Each of the rack and pinion formations may comprise one or more adjacent sets of teeth, each set of teeth being mutually offset from an adjacent set of teeth in a plane perpendicular to the axis of rotation, whereby the mutually offset sets of teeth on the rack and pinion formations respectively are arranged to intermesh to prevent sideways displacement of the teeth relative to one another.
  • the crawl mechanism includes a pair of parallel spaced apart rack formations and a corresponding pair of spaced apart pinion formations arranged to travel along the rack formations, with the mutually offset interengaging rows of teeth on both the rack formations and the pinion formations serving to ensure that the rack formations are maintained in a parallel configuration at their moving points of contact with the pinion formations.
  • the crawl mechanism assembly will drive a compression ram, a skip or similar carrier or container formation or conveyance, or the like.
  • each of the rack formations of the crushing apparatus is formed from a pair of rack plates of identical length which are fine blanked from a single strip of sheet metal (advantageously a relatively thin gauge mild steel) in such manner that the profiles of the teeth of a first rack plate form the matching profiles of the tooth spaces between the teeth of a second rack plate.
  • the framework thus formed is then treated against corrosion, preferably by tin- dipping.
  • tin acts as a solder flux which in its molten state penetrates even the smallest gaps defined between the rack plates, effectively solder-bonding them together as an integral rack formation as the tin cools; and secondly because of its superior resistance to the corrosive effects of residual cold drink beverages which could be spilled when a beverage can is crushed;
  • a housing for the crushing apparatus is formed out of a number of nominally planar, interlocking components, preferably injection moulded out of a polymer such as glass-filled nylon.
  • the drive shaft assembly is then formed by affixing two pairs of drive pinion gears in spaced apart arrangement on the drive shaft, with the adjacent teeth on each pair of gears being mutually offset by half a pitch.
  • the gears are affixed to the shaft using high current silver soldering;
  • the drive shaft assembly is then treated against corrosion, preferably by tin dipping, before being introduced into the framework through the gap defined by the two opposing pairs of rack formation, with the drive pinion gears intermeshing, in the manner previously described, with the upwardly projecting teeth of the lower pair of rack formations; in the event that the drive shaft assembly includes a manual crank handle, the drive shaft assembly is introduced into the framework at a precisely determined point along the rack formation, and at a pre-determined angle of the crank arm relative to the longitudinal axis of the framework.
  • the crank handle will lie in co- planar orientation to the longitudinal axis of the framework as an aid to effective packaging; the diameter of the holes in the centre of the idler pinion gears is smaller than the outside diameter of the idler shaft.
  • the four idler pinion gears are introduced as offset adjacent pairs into the framework, in a manner such that the teeth at the bottom of the idler gears intermesh with the teeth at the top of the corresponding drive gears, and the teeth at the top of the idler gears intermesh with the corresponding downwardly depending teeth of the upper rack formations.
  • the idler shaft is then introduced between the centres of the opposing pairs of idler pinion gears, and a screw is passed through the centre holes of the gears and then tightened into a pre-threaded hole in each end of the idler shaft.
  • the upper pair of rack formations are therefore spaced and held precisely apart by the idler shaft assembly, the lower pair of rack formations are similarly spaced and held precisely apart by the drive shaft assembly, and each of the vertically opposed pairs of rack formation are spaced apart by the drive shaft and idler shaft assemblies acting perpendicularly in concert with one another; • mating halves of the compression ram, or tup, are then journalled and fixed around the drive and idler shafts in the spaces defined between opposing pairs of pinion gears; cradle members for holding an empty beverage can in the crushing apparatus prior to being crushed are screwed into the framework; and finally inwardly projecting moulded studs on the panels comprising the housing of the apparatus are passed through complemental fixing apertures in the framework and then welded thermally or electronically into
  • Figure 1 shows a partly exploded perspective view of a first embodiment of a crushing apparatus of the invention in the particular application of a can crushing apparatus;
  • Figure 2 shows a top plan view of the can crushing apparatus of Figure 1;
  • Figure 3 shows a side view of the can crushing apparatus of Figures 1 and 2;
  • Figure 4 shows a cross-sectional view of a compression ram along the lines 4-4 of Figure 2;
  • Figure 5 shows a cross-sectional side view of a first embodiment of a ram along the lines 5-5 of Figure 3;
  • Figure 6 shows a cross-sectional side view of a second embodiment of a ram;
  • Figure 7 shows a detailed side view of part of the crawl mechanism of the invention
  • Figure 8 shows a perspective view of a second embodiment of a can crushing apparatus of the invention without its housing
  • Figure 9 shows a top plan view of the can crushing apparatus of Figure 8;
  • Figure 10 shows a side view of the can crushing apparatus of Figures 8 and 9;
  • Figure 11 shows a detailed side view of part of the crawl mechanism of the can crushing apparatus of Figures 8 to 10 illustrating a protective finger shield
  • Figure 12 shows a block diagram schematic view of a method of manufacturing and assembling the can crushing apparatus of Figures 8 to 11
  • Figures 13 A and B show respectively a plan view of the cutting profiles for the rack plates, and the die cut rack plates, referred to in Step 1 of the method of Figure 12
  • Figure 14 shows a perspective view of the framework cage produced according to Step 2 of the method of Figure 12
  • Figure 15 shows an exploded perspective view of the components forming the housing of the can crushing apparatus of Figure 8, moulded according to Step.4 of the method of Figure 12
  • Figure 16 shows the drive shaft assembly formed in accordance with Step 6 of the method of Figure 12
  • Figure 17 shows a detailed perspective view of the assembled crawl mechanism introduced into the framework cage according to Step 10 of the method of Figure 12
  • Figure 18 shows a perspective view of the can crushing apparatus of Figure 8 prior to
  • a crushing apparatus 10 of the invention comprises a can crushing apparatus having a framework 11 in the form of first and second rectangular opposed end plates 12 and 14 spaced apart by four rack formations 16, 18, 20 and 22 which are welded to the end plates 12 and 14 so as to provide a parallelopipedal framework.
  • the end plates 12 and 14 are formed with apertured flanges 24 for mounting the can crushing apparatus to a suitable fixture such as a wall, or for receiving mounting brackets such that the apparatus may be mounted to a pole, a vehicle, a shopping trolley or the like.
  • the end plate 12 defines a first fixed crushing surface 26 and the end plate 14 defines a second fixed crushing surface 28.
  • a housing indicated in chain outline at 29 covers the framework.
  • a compression ram 30 is mounted for reciprocal motion within the framework 11 , and is formed with a first moving crushing surface 32 and a second moving crushing surface 34.
  • a drive shaft 38 extends through the ram, and first and second spaced apart pinion formations 40 and 42 are carried on opposite ends of the shaft 38, with the pinion formation 40 intermeshing with the teeth 45 in the rack formation 22 and the pinion formation 42 intermeshing with the teeth 44 in the rack formation 20.
  • An idler shaft 48 also extends through the ram 30, and a pair of idler pinion formations 50 and 52 are carried on opposite ends of the idler shaft.
  • the idler pinion formations 50 and 52 intermesh with the teeth of the respective drive pinion formations 40 and 42, and also intermesh with the teeth 54 and 56 on the respective rack formations 16 and 18.
  • a drive means 61 is provided by a crank arm 58 extending from the drive shaft 38 and terminating in a handle 60.
  • the rack formations 16 to 22 and the drive and idler pinion formations 40, 42, 50 and 52 in combination define a crawl mechanism 57. It can clearly be seen that rotation of the drive pinion formations 40 and 42 via the crank arm 58 will cause the intermeshing drive and idler pinion formations to travel to and fro along the toothed rack formations.
  • a centre cradle 62 and outer cradles 64 and 66 define a pair of central openings 68 and 70 and a pair of outer openings 72 and 74 in the base of the can crusher.
  • a can 76 is placed on the cradles 62 and 64, and the lever arm 58 is rotated clockwise so as to cause the crawl mechanism to move to the right, with the can being crushed between the first fixed crushing surface 26 and the first moving crushing surface 32.
  • the crushed can 76 merely drops straight through the opening 72. If however, the can has a ferromagnetic component, then, as is clear from Figures 4 and 5, the crushed can 76 will be attracted to the surface 32 of the ram 30 by a pole piece 82 which forms a magnetic circuit in conjunction with a permanent magnet 84 located within the ram. The fer- romagnetic can 76 will be conveyed to a point in which it overlies the gap 70. As the ram traverses past a centre zone overlying the cradle 62, the magnetic hold on the can 76 is temporarily released and the can is allowed to fall through the central aperture 70.
  • the compressed cans fall through chutes beneath the cradles, which feed containers, with the non-magnetic cans being collected via outer chutes 85 A and the cans having a ferromagnetic content being collected via a central chute 85B which is fed from the central openings 68 and 70.
  • the magnetic circuit assembly comprises the pole piece 82, the permanent magnet 84 and a pole piece 86.
  • the permanent magnet 84 is a disc-shaped magnet which is held within a non-magnetic ring 88 which forms a cradle 90 in conjunction with a pair of laterally extending arms 92 each terminating in a pair of teeth 94.
  • the teeth 94 intermesh with complemental teeth 96 which extend from flipper or toggle arms 98.
  • the toggle arms 98 pivot on stub axles 100 which locate within complemental channels 101 defined within the body of the ram.
  • the opposite ends of the toggle arms are formed with semi-circular indents 102 which are positioned to interact with corresponding protrusions 104 extending inwardly from the centre of the rack formations 16 and 18.
  • the protrusions 104 locate within the indents 102 and cause the flipper arms to rotate in the direction of arrows 106 so as to move the cradle 90 from the Figure 5 position to a position in which the permanent magnet 84 is separated from the pole piece 82 and toggles over to the pole piece 86, with which it forms a magnetic circuit.
  • this then serves to ensure that the can 76 is released as it passes over the centre opening 70.
  • FIG. 6 an alternative version of the magnetic cradle assembly 90A is shown comprising a central rectangular permanent magnet 84A which is switched to and fro via the flipper arms 98A to define a magnetic circuit in conjunction with pole piece pairs 82 A and 86 A.
  • the rack formation 18 comprises a first outer rack plate 110 having a first row of teeth 112 having a trapezoidal profile and a second inner rack plate 114 formed with a second row of trapezoidal teeth 116 which are offset from the first row of teeth 112 by a distance 'd' which corresponds to one half of the pitch of a tooth.
  • the pinion formation 50 is formed from first and second pinion plates 118 and 120 which are similarly offset by one half of a tooth pitch.
  • the teeth are self-aligning, and sideways movement of the teeth is prevented in that the inner surfaces of all of the intermeshing plates are in contact with one another at the point of intermeshing.
  • the ram and pinion formations serve as a moving tie bar when travelling reciprocally along the rack fo ⁇ nations 16 and 18 and 20 and 22, so as to hold the rack formations in parallel spaced relationship where they interengage the pinion formations.
  • the gear teeth also have a profile which is different to that of a conventional gear train.
  • a conventional gear train utilizing substantially identical complemental teeth with minimum gear slippage, the gear train will tend to wear and become sloppy.
  • a modicum of slippage is introduced on the addenda and dedenda surfaces as the true motion transfer actually occurs tangentially to the pitch circle diameter of the gear members and not on either the addenda or the dedenda.
  • gears can be stamped out of relatively thin sheet material in a relatively simple but cost effective manner.
  • Figures 8 to 11 illustrate a simpler and more compact version of the can crusher of Figures 1 to 7. Where functions or characteristics of the invention in Figures 8 to 11 are essentially the same as those previously described in Figures 1 to 7, for convenience the same numerals are used, distinguished only in the case of Figures 8 to 11 by the use of the suffix ' .1'.
  • the can crusher 10.1 illustrated in Figures 8 to 19 differs from that described in Figure 1 in four material respects.
  • the overall length of the crusher 10.1 is reduced by 40 per cent, without in any way compromising its operating efficacy.
  • a different method of forming and assembling the housing 29.1 considerably simplifies the moulding of the component parts of said housing and their assembly to the framework 11.1 of the can crusher.
  • digit protection means in the form of a finger shield 126 are provided to obviate the possibility of digits being trapped between the teeth of the pinion formations 50.1 and 52.1, and the teeth of the intermeshing rack formations 18.1 and 20.1 respectively.
  • framework 11 of Figures 1 and 2 is affixed to the substrate or mounting bracket on which it is to be mounted by means of apertured flanges 24, the framework 11.1 of Figures 8 and 9 is affixed to the selected mounting substrate 132 or mounting bracket through four mounting apertures 128 in rack formations 16.1 and 22.1.
  • Apertured mounting spacer bushes 130 act as stand-offs to keep framework 11.1 suf- ficiently clear of substrate 132 to accommodate housing back plate 166 of Figure 15 and also allow sufficient free play for stub axle 134 of drive shaft 38.1 to reciprocate as compression ram 30.1 moves linearly within the framework 11.1.
  • Access apertures 136 through rack formations 18.1 and 20.1 are arranged to sit immediately behind housing mounting access apertures 172 in front plate 168 of housing 29.1 in Figure 15, in such manner that a suitable driver can be used to drive a wall fixing, screw or the like through mounting apertures 128 in order to affix the framework 11.1 to the mounting substrate 132.
  • Step 1 at block 142 of method 140 rack formation 16.1 (or, equally, 18.1, 20.1, 22.1) of Figures 13A and B is formed from a pair of rack plates 16.1 A and 16. IB of identical length which are fine blanked from a single strip of thin gauge mild steel 174.
  • rack plates 16.1 A and 16. IB adjacently back-to-back with one another as shown in Figure 13B, a rack formation 16.1 is defined having two adjacent and identical sets of teeth 56.1, each set of teeth being offset from the other by half a pitch;
  • Step 2 at block 144 rack formations 16.1, 18.1, 20.1 and 22.1, formed in accordance with Step 1, are then welded in opposing pairs to first and second rectangular opposed end plates 12.1 and 14.1 spaced apart by the rack formations so as to provide the parallelopipedal cage 176 illustrated in Figure 14, with the teeth (54.1 and 45.1) and (56.1 and 44.1) of each pair of rack formations (16.1 and 22.1) and (18.1 and 20.1), respectively, inwardly opposing one another;
  • Step 3 at block 146 the cage 176 formed per Step 2 is then tin-dipped, thereby both treating the cage against corrosion, and tin-soldering the individual rack plates making up the rack formations 16.1, 18.1, 20.1 and 22.1, together.
  • Step 4 at block 148 a housing 29.1 as illustrated in Figure 15 for the can crusher is formed out of a number of nominally planar interlocking plates 166, 168 and 170, injection moulded out of glass-filled nylon;
  • Step 5 at block 150 four idler pinion gears and four drive pinion gears per can crusher, as used respectively in idler pinion formations 50.1 and 52.1, and in drive pinion formations 40.1 and 42.1, are pressed out of a relatively thin gauge mild steel plate, and the gears are then case-hardened;
  • Step 6 at block 152 the drive shaft assembly 39 illustrated in Figure 16 as part of the crank mechanism 178 is then formed by affixing two pairs of drive pinion gears 40.1 and 42.1 in spaced apart arrangement on the drive shaft 38.1, with the adjacent teeth on each pair of gears being mutually offset by half a pitch.
  • the gears are affixed to the shaft using high current silver soldering;
  • Step 7 at block 154 the drive shaft assembly 39 and crank mechanism 178 are then treated against corrosion by tin dipping, before being introduced into the cage 176 through the gap defined by the vertically opposed pairs of rack formation (18.1 and 20.1) and (16.1 and 22.1);
  • Step 8 at block 156 the drive shaft assembly 39 is introduced, as shown in Figure 17 into cage 176 at a pre-determined point A along rack formation 20.1, and at a predetermined angle B of crank arm 58.1, with the drive pinion gears intermeshing with the upwardly projecting teeth 44.1 and 45.1 of rack formations 20.1 and 22.1 respectively.
  • the precise positioning of the drive shaft assembly 39 ensures that when it is at the extreme of its travel relative to the first end plate 12.1 of the cage 176, the crank handle 58.1 will lie in co-planar orientation to the longitudinal axis of the cage as an aid to effective packaging;
  • Step 9 at block 158 after tin plating, the four idler pinion gears are introduced as offset adjacent idler pinion formations 50.1 and 52.1 into the cage 176, in a manner such that the teeth at the bottom of the idler pinion formations 50.1 and 52.1 intermesh respectively with the teeth at the top of the corresponding drive gear formations 40.1 and 42.1, and the teeth at the top of the idler pinion formations 50.1 and 52.1 intermesh with the corresponding downwardly depending teeth 54.1 and 56.1 of the upper rack formations 16.1 and 18.1 respectively.
  • the diameter of the holes in the centre of the idler pinion formations 50.1 and 52.1 is smaller than the outside diameter of the idler shaft 48.1.
  • idler shaft 48.1 is then introduced between the centres of the opposing pairs of idler pinion formations 50.1 and 52.1, as illustrated in Figure 17, and screws 180 are passed through the centre holes of the idler pinion formations and then tightened into a pre- threaded hole in each end of idler shaft 48.1.
  • the upper pair of rack formations 16.1 and 18.1 are therefore spaced and held precisely apart by the idler shaft assembly, the lower pair of rack formations 20.1 and 22.1 are similarly spaced and held precisely apart by the drive shaft assembly 39, and each of the vertically opposed pairs of rack formation (16.1 and 22.1) and (18.1 and 20.1) are spaced apart by the drive shaft and idler shaft assemblies acting perpendicularly in concert with one another;
  • step 11 at block 162 mating halves of the compression ram, or tup, 30.1 are then journalled and fixed around the drive and idler shafts in the spaces defined between opposing pairs of pinion formations as illustrated in Figure 18;
  • Step 12 at block 164 cradle members 62.1 for holding an empty can in the crusher 10.1 prior to being crushed are attached to the framework 11.1 by means of screws (not illustrated) driven through apertures 182 in rack formations 20.1 and 22.1 into screw housings 184 formed in cradle members 62.1; and
  • Step 13 at block 165 inwardly projecting moulded studs 186 on housing back and front plates 166 and 168, respectively, are passed through complemental fixing apertures 188 in rack formations 16.1 and 18.1, and studs 187 on housing end plates 170, are passed through complemental fixing apertures 188 in framework end plates 12.1 and 14.1, and then welded thermally or electronically into countersunk plastic rivet heads 190, as illustrated in Figure 19 thereby securely affixing the housing plates 166, 168 and 170 to the framework 11.1.
  • Each of the moulded studs 186 and 187 are provided with a spacer boss 192 to ensure that the housing plates stand off from the framework 11.1 by a precise and pre-determined amount when the housing 29.1 is assembled onto the framework 11.1.
  • Removable plugs 194 as illustrated in Figure 15 are provided so that a suitable driver (not illustrated) may be inserted into housing mounting access apertures 172 in housing front plate 168 in order to fix can crusher 10.1 to a suitable mounting substrate, after which the plugs 194 are replaced into apertures 172 for cosmetic appeal.
  • Handle shaft 59.1 is passed through slot 196 in front housing plate 168 before plate 168 is affixed to framework 11.1, whereafter handle 60.1 is screwed onto handle shaft 59.1.
  • the crawl mechanism assembly offers a number of functional and commercial advantages over known conventional crawl mechanisms. The most important of these is the arrangement of offset, essentially adjacent, sets of intermeshing teeth carried on the rack formations, pinion formations, or both. Used in combination with one or more drive shaft and idler shaft assemblies, this arrangement allows the crawl mechanism assembly to dispense with conventional guide means, effectively to provide a moving tie bar in order to maintain spaced apart parallel configuration of rack formations, and to provide a very high level of assurance that the crawl mechanism will not 'de-rail' off the rack formations along which it travels.
  • the special design of the gear teeth so as to offer a planned modicum of slippage, and thereby largely avoid wear on the gear train as it rolls, is a further advantage of the invention, as is the method of constituting rack and pinion formations out of respectively a plurality of rack plates and pinion gears. This allows relatively thinner and softer metal plate to be used, which simplifies pressing and significantly reduces cost.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Crushing And Pulverization Processes (AREA)

Abstract

L'invention concerne un appareil de broyage (10.1) comportant un pilon de compression (30.1) définissant une surface de broyage mobile et monté pour permettre un mouvement linéaire alternatif à l'intérieur d'un bâti (11.1) possédant au moins une paroi terminale (14.1) définissant une surface de broyage fixe (28.1). Ce bâti (11.1) est défini par deux paires de parties conformées espacées formant crémaillère (16.1/22.1 et 18.1/20.1) unissant les première et deuxième parois terminales (12.1,14.1), chaque paire étant coplanaire avec une partie conformée formant pignon d'entraînement (42.1) et avec une partie conformée formant pignon fou (52.1) montées respectivement sur des ensembles arbre d'entraînement et arbre intermédiaire. Chaque partie conformée formant crémaillère et chaque partie conformée formant pignon porte deux jeux de denture adjacents, chaque jeu étant décalé d'un demi pas par rapport à son voisin. Les ensembles arbre d'entraînement et arbre intermédiaire font office de tirant de raccordement mobile de manière à maintenir parallèles et espacées les parties conformées formant crémaillère (16.1/22.1 et 18.1/20.1) lorsqu'elles s'engrènent dans les parties conformées formant pignon.
PCT/IB2004/052365 2003-11-12 2004-11-10 Appareil de broyage WO2005046977A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA2003/8794 2003-11-12
ZA200308794 2003-11-12

Publications (1)

Publication Number Publication Date
WO2005046977A1 true WO2005046977A1 (fr) 2005-05-26

Family

ID=34592855

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2004/052365 WO2005046977A1 (fr) 2003-11-12 2004-11-10 Appareil de broyage

Country Status (1)

Country Link
WO (1) WO2005046977A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009056674A1 (fr) * 2007-10-29 2009-05-07 Ari Kinnunen Dispositif de compactage de boîtes de conserve/de bouteilles ou d'objets similaires
CN103727200A (zh) * 2014-01-10 2014-04-16 姚平 一种机械运动磁力转换装置
WO2014208305A1 (fr) * 2013-06-24 2014-12-31 ニッタ株式会社 Crémaillère et procédé de fabrication de crémaillère
WO2015198171A1 (fr) * 2014-06-27 2015-12-30 Gsg International S.P.A. Poignée pour portes ou fenêtres
US10232380B2 (en) * 2015-01-16 2019-03-19 Flsmidth A/S Extraction mechanism for comminution device

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US741718A (en) * 1903-06-23 1903-10-20 Amearicus C Roberts Baling-press.
US4240341A (en) * 1978-12-06 1980-12-23 Robert Whipple Can crusher
US4414891A (en) * 1981-07-06 1983-11-15 Kitzman Donald G Crushing apparatus
JPS5923151A (ja) * 1982-07-30 1984-02-06 Tomiya Eng Kk 歯車による直線運動機構
CH656832A5 (en) * 1982-08-19 1986-07-31 Eugen Willi Briquette-forming apparatus in particular for paper refuse
WO1990000509A1 (fr) * 1988-07-08 1990-01-25 Mytronic Ab Dispositif de positionnement rapide de chariots lourds
EP0416260A1 (fr) * 1989-08-31 1991-03-13 Sante Cattarossi Dispositif pour écraser des boîtes
JPH0796399A (ja) * 1993-09-28 1995-04-11 Toshio Okamura 空き缶処理用手動式小型プレス
US5448946A (en) * 1994-08-08 1995-09-12 Laux; William R. Bottle compacting apparatus
WO1996029494A1 (fr) * 1995-03-21 1996-09-26 Feherdi Janos Mecanisme d'entrainement
EP1308267A2 (fr) * 2001-10-30 2003-05-07 Chang-Geun Park Procédé et dispositif pour écraser et trier des boítes

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US741718A (en) * 1903-06-23 1903-10-20 Amearicus C Roberts Baling-press.
US4240341A (en) * 1978-12-06 1980-12-23 Robert Whipple Can crusher
US4414891A (en) * 1981-07-06 1983-11-15 Kitzman Donald G Crushing apparatus
JPS5923151A (ja) * 1982-07-30 1984-02-06 Tomiya Eng Kk 歯車による直線運動機構
CH656832A5 (en) * 1982-08-19 1986-07-31 Eugen Willi Briquette-forming apparatus in particular for paper refuse
WO1990000509A1 (fr) * 1988-07-08 1990-01-25 Mytronic Ab Dispositif de positionnement rapide de chariots lourds
EP0416260A1 (fr) * 1989-08-31 1991-03-13 Sante Cattarossi Dispositif pour écraser des boîtes
JPH0796399A (ja) * 1993-09-28 1995-04-11 Toshio Okamura 空き缶処理用手動式小型プレス
US5448946A (en) * 1994-08-08 1995-09-12 Laux; William R. Bottle compacting apparatus
WO1996029494A1 (fr) * 1995-03-21 1996-09-26 Feherdi Janos Mecanisme d'entrainement
EP1308267A2 (fr) * 2001-10-30 2003-05-07 Chang-Geun Park Procédé et dispositif pour écraser et trier des boítes

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 008, no. 116 (M - 299) 30 May 1984 (1984-05-30) *
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 07 31 August 1995 (1995-08-31) *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009056674A1 (fr) * 2007-10-29 2009-05-07 Ari Kinnunen Dispositif de compactage de boîtes de conserve/de bouteilles ou d'objets similaires
KR20160024843A (ko) * 2013-06-24 2016-03-07 니타 가부시키가이샤 랙 및 랙의 제조 방법
WO2014208305A1 (fr) * 2013-06-24 2014-12-31 ニッタ株式会社 Crémaillère et procédé de fabrication de crémaillère
JP2015004422A (ja) * 2013-06-24 2015-01-08 ニッタ株式会社 ラックおよびラックの製造方法
CN105102860A (zh) * 2013-06-24 2015-11-25 霓达株式会社 齿条及齿条的制造方法
EP3015742A1 (fr) * 2013-06-24 2016-05-04 Nitta Corporation Crémaillère et procédé de fabrication de crémaillère
EP3015742A4 (fr) * 2013-06-24 2017-04-26 Nitta Corporation Crémaillère et procédé de fabrication de crémaillère
KR101884053B1 (ko) * 2013-06-24 2018-07-31 니타 가부시키가이샤 랙 및 랙의 제조 방법
CN105102860B (zh) * 2013-06-24 2019-03-19 霓达株式会社 齿条及齿条的制造方法
CN103727200A (zh) * 2014-01-10 2014-04-16 姚平 一种机械运动磁力转换装置
WO2015198171A1 (fr) * 2014-06-27 2015-12-30 Gsg International S.P.A. Poignée pour portes ou fenêtres
CN106574473A (zh) * 2014-06-27 2017-04-19 Gsg国际股份有限公司 门或窗的把手
US10232380B2 (en) * 2015-01-16 2019-03-19 Flsmidth A/S Extraction mechanism for comminution device

Similar Documents

Publication Publication Date Title
US5762116A (en) System for filling bottles with pills
KR102330515B1 (ko) 컨베이어용 다방향 롤러 조립체
US6290095B1 (en) Chip component take-in apparatus
EP0070195B1 (fr) Dispositif de retournement d'objets
WO2005046977A1 (fr) Appareil de broyage
US6652146B2 (en) Linear motion guide device having two offset ball rows
US3923148A (en) Conveying system
JP2816951B2 (ja) 粉末収容袋の材料固化解消装置
CN111922164A (zh) 一种打印冲压瓶盖的设备
JP2003070432A (ja) 米飯成形装置
JP2921758B1 (ja) 回転プレス装置
WO1995010453A1 (fr) Appareil pour couper et tasser de la pate
JP3410251B2 (ja) 空缶圧潰装置
CN218258805U (zh) 用于灌装的压料装置
JPH11170095A (ja) 使用済み容器の潰し機
EP0917277A1 (fr) Entrainement motorisé
JP3370609B2 (ja) 電子部品供給装置
CN113753543B (zh) 一种带式输送机用翻转组件
JPH037420Y2 (fr)
EP3352149B1 (fr) Machine avec un support de broche pour les marchandises
JPH054712A (ja) 充填機のガイド装置
JP3978115B2 (ja) 自動販売機の商品搬送装置及び自動販売機
JPH02191093A (ja) 自動販売機の商品搬送装置
US20200171770A1 (en) Automated pallet press
JPH023794Y2 (fr)

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase