EP0746661B1

EP0746661B1 - Vertical storage conveyor with improved load support and drive system

Info

Publication number: EP0746661B1
Application number: EP95910878A
Authority: EP
Inventors: Robert D. Lichti
Original assignee: Wei Sheng Development Co Ltd
Current assignee: Wei Sheng Development Co Ltd
Priority date: 1994-02-25
Filing date: 1995-01-24
Publication date: 1999-04-07
Anticipated expiration: 2015-01-24
Also published as: ATE178683T1; AU1867895A; CN1104545C; EG20491A; BR9506917A; NZ281758A; DE69508930T2; TW397105U; DK0746661T3; TW346140U; DE69508930D1; EP0746661A1; AU691584B2; CA2184109C; IL112481A; IL112481A0; WO1995023266A1; HK1001134A1; CA2184109A1; KR100216958B1

Abstract

A vertical conveyor is disclosed having a frame with a first and second vertical frame section spaced apart but supportingly connected to each other. Load supports having first and second ends are conveyed around a looped path. Each load support is movably mounted at the first and second ends to first and second frame sections. A pickup chain assembly has a pickup drive chain, an upper drive sprocket driven by the motor wherein a substantial amount of the load exerted by the supports against the pickup chain assembly is imported against the upper drive sprocket. An idler sprocket is aligned below the drive sprocket and has a smaller diameter than the drive sprocket. The pickup drive chains include a plurality of pickups pivotally mounted thereto which engage transverse axles mounted at the end of compression links of a compression chain assembly. The load supports are mounted on the compression chain assembly. A motor simultaneously drives the first and second pickup chain assemblies which in turn drive the compression chains and move the supports up and down.

Description

The invention relates to a vertical conveyer with the features cited in the preamble of claim 1.

A vertical conveyor of this type is described in US-3,547,281. It teaches to insert the through pin through a hole of said pick-up arm so that the through pin projects at both sides. The projecting ends of the through pin are respectively connected to one strand of the pick-up drive chain. The pick-up arm is rotatable with respect to the pick-up drive chain so that it can be adjusted for engaging and driving the compression chain. The engagement with the compression chain has to be accurate enough for correct operation of the vertical conveyor.

Other vertical conveyors are described in US-3,424,321 and 3,656,608.

It is the object of the present invention to provide an improved vertical conveyor of the above-mentioned type with an improved handling and maintenance work, said conveyor providing at least the same balance, stability and force for raising the load supports in operation.

According to the present invention, this object is attained by a vertical conveyor with the features defined in claim 1.

This construction allows to disassemble each pick-up arm separately from the unit without disturbing the orientation of the pick-up and compression chains. If a defect with one of the pick-up arms or in connection with the compression chain occurs, the respective pick-up arm can be removed from the through pin by e.g. splitting the pick-up arm in the upper head portion and the lower tail portion. If desired, the through pin can remain in connection with the strands of the chain during the repair.

Advantageous features and embodiments of the invention are cited in the independent claims.

In one subsidiary aspect of the invention, first and second drive chain assemblies may be present and each comprises a pickup drive chain which drives a compression chain supporting the load supports, and an upper drive sprocket of the pickup drive chain driven by a motor wherein a substantial amount of the load exerted by the supports against the pickup drive chain is imparted against the upper drive sprocket. An idler sprocket is aligned below the drive sprocket and has a smaller diameter than the drive sprocket. Thus, the slack produced in the pickup drive chain is minimized such as occurs during reversing motion of the conveyor.

In one subsidiary aspect of the invention, a plurality of pickup arms may be present which are pivotally connected to the pickup drive chain such that the pickup arms engage and drive the compression chain so as to move the load supports. The pickups are pivotally mounted offset on the pickup chain to aid in engagement of the pickups with the compression chain. The compression chain includes an endless roller chain comprised of interconnecting, elongate compression links and transverse axles mounted at each end of the compression links such that the pickup arms engage the axles for pushing the compression links upward. The offset mounting of the pickups enables receiving notches on the pickups to engage the axles as the chain moves in its lower portion of the loop.

In one subsidiary aspect of the invention, the load supports may include load support mounting arms, which are pivotally mounted to the compression links. A mounting member extends in the support spacing. The motor is mounted to the mounting member. A connecting member supportingly connects the first and second frame sections. The motor mounting member is suspended from the connecting member substantially centrally between the frame members.

In still another subsidiary aspect of the invention, the pickup chain may comprise two spaced roller chains. Each through-pin connects the roller chains. The pickups are pivotally connected to the roller chain between the pickups. The pickup chain also includes a link, and a link pin interconnecting the link. The through-pins are offset from the link pins. The pickups comprise an upper head portion and a smaller lower bifurcated tail portion. The upper head portion includes opposing receiving notches for engaging the through-pins of the compression chain.

In one subsidiary aspect of the invention, as a pan traverses through the top transfer guide, the guide moves upward and then returns to its original height. In addition, as the compression chain links shorten over the life of the conveyor, the reference starting point for the top transfer guide moves slightly downward.

As the pan traverses through the bottom transfer guide, a vibration develops due to a lack of dampening of the guide motion which moves downward from a reference point and returns. The present invention provides for a vertical floating motion with the possibility of a dampening effect.

In still another subsidiary aspect of the invention, a positive locking device prevents movement of the compression chain while the rotational movement of the pan is at rest. The locking device is capable of transferring any load imbalance to the frame structure.

In accordance with the present invention, a vertical conveyor has a frame with a first vertical frame section and a second vertical frame section spaced apart from, but supportingly connected thereto. A looped compression chain is mounted respectively to each of the first and second frame sections. A plurality of load supports have first and second ends, with each load support being capable of holding a load to be conveyed around in a looped path. A support mechanism interconnects the compression chain and respective first and second ends of the load supports so that the compression chains support the load supports such that as one support is conveyed upwardly, another load support is conveyed downwardly. The load supports pass through a predetermined, spaced apart, horizontal distance, which defines a support spacing.

First and second pick-up drive chain assemblies are mounted respectively to each of the first and second frame sections. A plurality of pick-up arms are pivotally connected to each pick-up drive chain assembly, and the pick-up arms engage and drive the compression chain.

A motor is mounted within the spacing defined by the load supports. A first drive shaft connects the motor to the first pick-up drive chain assembly and a second drive shaft connects the motor to the second pick-up drive chain assembly. The drive shafts simultaneously drive the first and second drive chain assemblies so that the pick-up arms engage and drive the compression chain and move the load supports.

In one subsidiary aspect of the present invention, the pick-ups are pivotally mounted offset on the pick-up drive chain assembly to aid in engagement of the pick-ups with the compression chain. Each pick-up drive chain assembly comprises two spaced roller chains and a through-pin interconnecting the roller chains. The pick-up arms are pivotally connected to each through-pin. The pick-up drive chain assembly includes a link and a link-pin interconnecting the links. The through-pins are offset from the link-pins. The pick-up arms comprises an upper head portion and a smaller, lower bifurcated tail portion. The compression chain includes axles, and the upper head portion includes two receiving notches for receiving axles positioned on the compression chain.

The mounting member preferably mounts the motor substantially centrally between the frame sections. The motor may be an electrical motor having first and second motor shaft ends, located at respective sides of the motor, and respectively connected to the first and second drive shafts. The motor may be mounted at a vertical height less than one half the vertical height of the vertical frame sections.

In another subsidiary aspect of the present invention, each compression chain also includes an endless roller chain comprising interconnecting, elongate compression links and transverse axles mounted at each end of the compression links. Each load support also includes load support mounting arms at first and second ends of the load supports. The mounting arms are pivotally connected to the compression links so that the load supports are supported by the compression chain. Pick-up arms are pivotally connected to each pick-up drive chain assembly, such that the pick-up arms engage the axles while pushing the compression links upward.

BRIEF DESCRIPTION OF THE DRAWINGS

The foregoing advantages of the present invention will be appreciated more fully from the following description, with reference to the accompanying drawings, in which:

Figure 1 is a front and elevational view of a vertical conveyor according to one embodiment of the present invention.

Figure 2 is a side elevation view of the vertical conveyor shown in Figure 1.

Figure 3 is an enlarged, front elevational view of the major weldment of the frame and depicting the pickup drive chain mechanism for the vertical conveyor.

Figure 4 is an enlarged front elevational view similar to figure 3, showing features of the endless pickup chain drive and of the secondary compression chain lock.

Figure 5 is an enlarged, front elevation view of the front upper guide plate subassembly.

Figure 6 is an enlarged side elevation view looking in the direction of arrow 6 of Figure 4.

Figure 7 is an enlarged from elevation view of the drive gear sprocket.

Figure 8 is a cross-sectional view taken along line 8-8 of Figure 7.

Figure 9 is an enlarged engineering scale front elevation view of the idler sprocket.

Figure 10 is a cross-sectional view taken along line 10-10 of Figure 9.

Figure 11 is an enlarged front elevation view of one of the pickup arm assemblies which engages with and conveys a compression link in the secondary chain.

Figure 12 is a sectional view taken along line 11-11 of Figure 12.

Figure 13 is a front elevation view of the doublestranded conveyor chain in the pickup drive chain.

Figure 14 is a sectional view of the pickup chain taken along line 14-14 of Figure 13.

Figure 15 is an enlarged side elevation view of the bottom pickup guide assembly.

Figure 16 is an enlarged plan view depicting the mounting and stabilizing structures of one end of a conveyed pan.

Figure 17 is a sectional view of the upper column section.

Figure 18 is a sectional view of the lower column section taken along line 18-18 of Figure 1.

Figure 19 is an enlarged, front elevation view of the top stabilizing transfer guide assembly.

Figure 20 is a top plan view of the conveyor shown in Figure 1.

Figure 21 is a partial rear elevation view taken along line 21-21 of Figure 20 and showing the guide channel cross-over.

Figure 22 is an enlarged, front elevation view of the bottom stabilizing transfer guide assembly.

Figure 23 is a side elevation of the bottom stabilizing transfer guide assembly shown in Figure 22.

Figure 24 is a top plan engineering scale view of the bottom stabilizing transfer guide assembly depicted in Figure 22.

Figure 25 is an enlarged, top plan view of the tower locking assembly.

Figure 26 is an enlarged, front elevation of a portion of Figure 19 to delineate the shock mechanism.

Figure 27 is an enlarged section view of the sliding guide for the top transfer guide shown in Figure 26.

Figure 28 is an enlarged section view of Figure 27 delineating the friction mechanism components of the top transfer guide.

Figure 29 is a top plan view of the mounting and stabilizing structures which support a conveyed pan.

Figure 30 is a schematic, elevational view showing the compression chain supporting the load support.

Figure 31 is a front elevational view depicting the pick-up drive chain assembly and pick-up arms engaging the compression chain.

Figure 32 is an enlarged view showing the load support mounting mechanism engaged with the compression chain.

Figure 33 is an elevation view of the motor and drive shafts of the present invention.

Figures 34 and 35 depict the inner link assembly of the compression chain, with Figure 34 being a plan view and Figure 35 being an elevation view.

Figures 36 and 37 depict the outer link assembly of the compression chain, with Figure 36 being a plan view and Figure 37 being an elevation view.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring now to Figs. 1 and 2, a vertical conveyor 10 according to a presently preferred embodiment is depicted. The conveyor 10 has a skeletal frame 12. A compression chain vertical conveyor system 14 (Figs. 1 and 30) includes a left subsystem 14a and a substantially identical right subsystem 14b. A plurality of platform cells or pans 16 are hung from the conveyor system 14 and are rotated in either direction in an endless racetrack (looped) path (Figures 1, 2 and 30).

The illustrated conveyor 10 has fourteen pans 16. Each pan 16 is designed to carry a static load of up to 2268 kg (5,000 pounds), pan thus can carry a full size manufactured automobile. In this illustrated embodiment, the conveyor 10 has an overall height of about 16 m (52 feet), an overall width of about 6 m (20 feet), and an overall length of about 7,6 m (25 feet). The conveyor 10 can be designed to have more than thirty pans 16 and have a height of about 32 m (103 feet). The zoning laws in a particular location where the conveyor is installed will sometimes dictate height requirements.

Frame 12 (Figs. 1 and 2), is a fixed support structure and is substantially transversely symmetrical about a central plane 18 as depicted in Fig. 2 and is substantially longitudinally symmetrical about a central plane 20. A top guide strut brace 52 is at the top. As shown in Figs. 2 and 20, the frame 12 includes a front vertical frame section 22 (shown in substantial elevation in Fig. 1) and a substantially identical rear vertical frame section 24 mounted on a rectangular base section 26. The base section 26 has two transverse headers: 1) a front transverse header 28 and 2) a rear transverse header 30 connected at substantially similar top cornices 32 to two longitudinal side headers (not shown). The front, rear and side headers define an annular rectangle. The base section 26 also includes four legs (three shown) located at and connected to each cornice 32.

As shown in Fig. 2, the front header 28 has a rotated "G" shaped cross-section and rests above the automobile entrance. The "G" shaped cross-section forms a stronger, lighter and more economically manufactured member which can be easily installed and removed. In addition, other conveyor equipment can be mounted inside the G-shaped header frame including operating equipment for a gate (not shown) used to block the entrance to the conveyor 10.

As shown in Fig. 2, a plurality of internal braces on each side of the vertical conveyor 10 connect the

frame sections

22 and 24 together and provide structural rigidity, equalizing the loading between the frame sections. The internal bracing includes

horizontal struts

34, 54, 56, 58 (Fig. 2), each of which is rigidly mounted at respective ends to frame

sections

22 and 24. Lateral stability is provided by diagonal bracing 60, 62 and 64. The bracing for the top transfer guide 102 Figs. 1, 19 and 20 is shown in section 50 and includes a top guide strut brace 52, two top guide spacing struts 51 and 57, and four top guide braces 53, 55, 59 and 61 bolted together to form an "X" configuration.

As shown in Fig. 1, the frame section 22 has substantially the form of an A-frame. The frame section 22 has a base formed by header 28 and

legs

38 and 40, and has an upper section formed by

diagonal columns

66 and 68. The

diagonal columns

66 and 68 are bolted at their lower ends to respective cornices 32 of the A-frame base, and are bolted at their upper ends to each other and to a transverse midpoint of front column 70.

A substantially similar rear column 70 (Fig. 2) is provided for the frame section 24. The column 70 includes a lower section 72 and an upper section 74 that are spliced together with bolts at a vertical mid-portion joint 76 (described below). The height of the mid-portion joint 76 above the foundation 11 depends upon the total number of conveyor pans and the overall height of conveyor 10. The lower column section 72 includes a solid one-piece weldment.

The columns 70 and 70' form a fixed tower structure and provide a conveyor housing and a track 77 for a secondary conveyor assembly that includes a rolling compression chain 78 (Figs. 16 and 17).

Further non-essential details of the compression chain 78 are described below. Other details of the compression chain 78 and of columns 70 and 70' can be obtained by referring to United States Patent Nos. 3,424,321, 3,547,281, and 3,656,608 to Lichti.

Each column 70 and 70' serves as part of a main frame extending upwardly from the front header 28 (or the rear header for rear frame section 24) through a joint adjacent the top of conveyor 10 where it supports the upper end of endless compression chain 78 located at the point where chain 78 crosses over from one side to the other.

Each platform pan 16 has a slightly, upwardly curved, rectangularly configured bottom plate 80. The bottom plate 80 is supported at each corner by a vertical pan hanger or post 83. Those posts 83 are located on the same side of the bottom plate 80 and connected at the tops thereof to a horizontal, V-shaped top pan header 84 (Fig. 16). A horizontal, tubular top strut 85 connects the apices of each header 84 and, with two braces 86, are welded thereto.

Referring to Figure 16, each platform pan 16 is mounted and stabilized during its travel around conveyor 10 through a mounting assembly 87. A stub shaft 88 connects the mounting assembly 87 to the pan 16. The stub shaft 88 extends outwardly from the other side of the apex of each header 84 and is welded thereto. A bearing housing 89 is mounted on the stub shaft 83. The apex of a "v" shaped link hanger 90 (Figure 32) is pivotally mounted to the bearing housing 89. The link hanger 90 has two mounting coplanar arms (arm 92 shown in Fig. 16, 30 and 32), which are pivotally mounted at their respective free ends to a compression link of the endless compression chain 78. As shown in greater detail in Figure 32, a bracket arm 78a extends from the compression chain 78. The bracket arm 78g slides within a respective arm 92 and is held thereto by a clevis pin 93 and cotter pin 93a.

Thus, a pan 16 is cantilever mounted at each end to the corresponding conveyor subsystem 14a and 14b by a link hanger 90.

As shown in Figs. 1, 16 and 32, the apex of a V-shaped stabilizer 96 is also mounted to the stub shaft 88. The stabilizer 96 pivotally mounts guide shoes 98. The stabilizer 98 stabilizes the pan 16 as it is conveyed around the top and bottom of the conveyor 10. Mounted to the top and bottom of front and

rear conveyor housing

70 and 72 are a top guide 102 and a bottom guide 104 which contain crossing channels 100 and 102 (see also Fig. 21). Guide shoes 98 of each pan 16 are received in the

channels

100 and 101 as a pan 16 is conveyed.

In general, the vertical conveyor 10 includes a motor means 120, a pickup drive chain assembly 122 rotated by the motor, and a compression drive chain assembly 124, driven by the pickup drive assembly 122. The compression chain assembly 124 includes a compression chain 78 that carries pans 16.

In the present invention and as shown in greater detail of Figure 33, the motor means includes a motor 130 which is a double ended, reversible, three phase 460 AC volt input, 500 volt DC output, regenerative electric motor. The motor is connected to the primary drive chain assembly 122 or each

frame section

22 and 24 through drive subassemblies 146 and 148 (Fig. 2). Each

drive subassembly

146 and 148 comprises a commercially available universal joint 150 which connects a drive shaft 152 to motor 130. A second, distal universal joint 154 is connected to the distal end of the drive shaft 152. Connected to the other end of the distal universal joint, through a keyed fitting (not shown) is a conventional, hydraulically actuated electrically operated friction brake 156, which is connected and mounted to a speed reduction gearing 158 with a splice fitting (not shown). The housing containing the reduction gearing 158 is mounted at the other end to the corresponding

vertical frame section

22 or 24. The reduction gearing 158 is operatively connected to and drives the pickup drive chain assembly 122. A hydraulic controller, indicated generally at 159a, actuates the brake 156. The controller 159a includes a motor 159b for driving a pump 159c for pumping hydraulic fluid from the reservoir 159d. An accumulator 159e, pressure switch 159f and valve 159g are also included.

Referring now to Figs. 1 through 6, each pickup drive chain assembly 122 is mounted on a solid, one piece weldment 160 which includes a lower frame section 72 of the frame portion 22. More particularly, the pickup drive chain assembly 122 is mounted inside an interior cavity 162 of the weldment 160.

The pickup drive chain assembly 122 (Figs. 3, 13 and 31) includes an upper toothed drive sprocket subassembly 166 (Fig. 8), a lower toothed idler sprocket subassembly 168 (Fig. 10), a dual drive chain subassembly 170 (Fig. 14) and five pickups arms (pickups) 172 (Fig. 12) attached to the drive chain subassembly 170 with a through-pin 194 (Fig. 14) and rotated in a racetrack path. In the illustrated embodiment, there are only five pickups 172. For explanation and clarity, one of the pickups 172 is shown in phantom (Fig. 3) in an advanced position at the top of drive chain subassembly 170. In Figure 4 the bottom-most pickup 172 has been omitted.

An upper toothed drive sprocket subassembly 166 is an integral, one-piece, molded element (Figs. 7 and 8) and includes an outside drive sprocket 176, a substantially similar inside drive sprocket 178, and an interconnecting, hollow tube 179. A solid shaft 180 (Fig. 6) is keyed to and mounted inside the tube 179 and terminates on its inner end in a splice (not shown), which in turn is mounted to and driven by reduction gearing 158. The outer end of the shaft 180 is mounted in a bearing 183 (Fig. 6), which in turn is rigidly mounted to the weldment 160. Each

drive sprocket

176 and 178 has a mean diameter of about 23 inches, a total of 18 standard teeth 181, and two sets of two reduced diameter teeth 181' located 180 degrees apart. The teeth 181' terminate inside the mean diameter circle 177. The radial size of the teeth is smaller so as to provide clearance for the diameter of the through-pin 194.

The lower toothed idler sprocket subassembly 168 is shown in Figs. 4, 6, 9, 10, and 15 and includes an outside idler sprocket 184, a substantially similar inside idler sprocket (not shown), and coaxial, spaced apart shaft 188 for respectively mounting inside and outside idler sprockets. The 186 spacing between the adjacent ends of shafts 188 is selected so that pickups 172 can pass therebetween. Idler sprocket 184 has a diameter of about 0,31 m (12 1/4 inches) and a total of nine teeth 185 and two teeth 185'. The teeth 185' terminate inside the mean diameter circle 187 and the pitch between them is deeper so as to provide clearance for the larger diameter of the through-pin 194.

The pickup drive chain subassembly 122 (Figs. 13 and 14) is comprised of a first roller chain 190 and a second roller chain 192 each with five interconnected, matched strands. The center lines of the roller chains 190 and 192 are spaced apart about 0,22 m (8 1/2 inches) and the two chains are interconnected with five through-pins 194. Each of the five strands of each chain 190 and 192 is about 0,87 m (34 1/4 inches) long and terminates in a master link 195 which connects to the adjacent strand and which mounts through-pin 194. In this particular embodiment, each chain 190 and 192 has an average tensile strength of 68039 kg (150,000 pounds) per strand. The center axis line of the through-pins 194 is offset from a center line drawn from chain link-pins 197 (Fig. 13).

As shown in Figs. 3, 4, 11, 13 and 14 a pickup 172 is pivotally mounted at the bottom section thereof on each heat-treated through-pin 194.

The pickups 172 of the present invention have a split body. Each pickup 172 includes an upper head portion 196 and a smaller, lower bifurcated tail portion 198 that is mounted to upper head portion with bolts and nuts (not shown). In a preferred embodiment, pickup 172 is almost 0,66 m (26 inches) long and a little over 0,36 m (14 inches) wide at the top and tapers down to 17,78 cm (7 inches) wide at the bottom of head portion 196 with a 25,4 cm (10 inch) radius curve. Each pickup 172 is journalled onto the through-pin 194 and is held centered thereon with snap rings 199 on either side. A notch 200 (Fig. 12) on each side of the centerline of pickup 172 in the upper head portion 196 engages with and picks up a connecting pin assembly, shown at 210 (Fig 3), in compression chain 78 (Fig. 16).

The mating ends of the head portion 196 and tail portion are provided with mating half-circular cutouts. The cutout in the head portion 196 has a nominal radius of 3,8 cm (1.5 inches) so it can receive a semi-circular bearing insert 201 having integral end flanges. The cutout in the tail portion 198 has a nominal radius of 3,2 cm (1.25 inches), which matches with the inner surface of insert 201. A sleeve 202 has a thickened central portion with a central circular slot therein for engaging the head portion. The sleeve 202 has a reduced shoulder to support ball bearings 203 at each end. Each ball bearing supports 203 a metal wheel 204, which has been heat treated to a surface hardness of Rc 44/47. The wheels 203 have an outer diameter of 11,75 cm (4.625 inches) in a preferred embodiment and engage and ride on a bottom guard 205 (see Fig. 4), which helps orient the pickup 172.

Located near the top of head portion 196 (Fig. 12) is a hole having a radius of 4,45 cm (1 3/4 inches) for mounting a upper shaft 206. Mounted onto each end of shaft 206 (Fig. 11) are ball bearings 207 which in turn mount a top, inner flanged wheel 208, which has an base outer diameter of 11,4 cm (4.5 inches) and a flange outer diameter of 13,3 cm (5.25 inches) in a preferred embodiment. Wheel 208 engages and is guided by a plurality of track guides 209 (Fig. 4) and 352 (Fig. 4). Mounted between upper wheel 208 and lower wheel 204 on either side of pickup 172 is a somewhat triangular safety lug 211 (Fig. 12) which restricts the back fall of the pickup traversing the top guide 350 (Fig. 4).

As shown in Figs. 3, 16 and 34 through 37, the compression chain 78 includes a plurality of outer compression links 212 and a plurality of inner compression links 214, which are similar to and fit inside outer compression links 212. The inner and outer compression links are pivotally interconnected by connecting pin assemblies 210. Also mounted to the inner link 214 are two angled connecting lugs 228, only one of which is depicted in Fig. 16, for connecting link hanger arms 91 and 92 of the pan 16.

As shown in Fig. 3, the bearing roller 238 is engaged in one of the notches 200 of the pickups 172 as the engaging pickup 172 lifts or pushes it and the associated compression link upwards. Thus the weight of the whole load on the side of the upwardly rotated conveyor 10 is realized through bearing roller 238. The compression chain also includes two roller 292, 294 which fit within the formed channels 77 so that the compression chain forms a roller chain with reduced friction as it moves in a looped manner.

The guide and channel subassemblies for the compression chain assembly 124 (Fig. 2) are integral components with the other elements of the conveyor 10. For the upper frame section 74 (Figs. 1 and 17), the outwardmost components have spaced apart left hand guide rails 252 and right hand guide rails 254 (Fig. 17). The guide rails 252 include an inner guide channel 256 and an outer guide channel 258 spaced apart to the plate 260. The guide rails 254 are formed of an inner guide channel 262 and an outer channel 264 spaced apart to a plate 266. Each guide channel also serves as a vertical structural component and has a bevelled U-shaped channel that is welded to the upper frame section 74. The compression chain rollers 292, 294 (Fig. 16) have a similar size, shape and bevel to the slope of the guide channels. The upper and lower ends of

channels

252 and 254 are flared inwardly to permit the compression links 214 to "bend over" the top of frame sections 74 (Fig. 1) and 74a (Fig. 2).

The guide and channel subassemblies for the lower tower section are parts of the weldment 160 (shown in Figs. 3, 4, 6 and 18). As shown in Fig. 18, the weldment 160 is formed of a welded metal sheet base plate 270 having

side plates

272 and 274 welded to each end to form a somewhat rectangular box. In the middle section of

side plates

272 and 274 are

slots

276 and 278 to accommodate pickups 172 entering the channel area and engaging connecting pin 210 of compression chain 78. The weldment, 160, as shown in Fig. 18, also contains suitable mounting plates, such as mounting plate 280, for mounting the pickup dive chain assembly 122.

Directly welded to side plate 272 is a guide rail 282. A guide rail 284 is welded to side plate 274. The guide rail 282 has an inner guide channel 286 (Fig. 18) and an outer guide channel 288 spaced apart and connected to side plate 274 by welding. Similarly, the guide rail 284 has an inner guide channel 290 and an outer channel 290 mounted spaced apart and connected to side plate 274 by welding. Each

guide channel

286, 288, 290 and 292 also serves as vertical structural component and is a bevelled U-shaped channel that is connected to weldment 160. Also, each U-shaped channel has the same size and shape as

channels

256, 258, 262 and 264.

The weldment 160 (Figs. 3, 4 and 6) has three pickup guides - the bottom guide 205, side guide 209, and a top guide 302. The bottom guide 205 is also shown in Fig. 15 and has a mounting plate 304 rigidly attached at the bottom to a square mounting tube 306. Two substantially identical spaced guides 308 and 309 (not shown) are rigidly mounted at their respective bottoms to the mounting tube 306. Each guide 308 and 309 is comprised of a U-shaped guide plate 310 (Fig. 4) with removably mounted tip portions 312 bolted thereto and supporting side gusset plates 314. A flat polyurethane guide bar 316 is mounted perpendicularly along the inner edge of guide plate 310 (Fig. 4). The pivot pin 320 also catches the tail portion of the pickup 172 as the pickup 172 is rotated in either direction to it. This holds the bottom of the pickup 172 stationary, and permits the top portion, connected to chains 190 and 192, to be rotated with respect to the bottom in the proper direction.

The side guides 209 have an outer guide plate 326 which extends out of the paper (Fig. 3) and an inner guide plate 328 which is bolted to the primary drive mounting plate 272 and 274 (Fig. 18).

The top guide 302 (Fig. 3) has a front upper guide plate 340 rigidly mounted on the weldment 160 and a lower guide plate 342 spaced below the upper guide plate 340. A similarly shaped rear upper guide (not shown) is spaced 6,4 cm (2½ inches) behind the front guide. Together the front and rear guides form a captive path 352 for the upper wheel 208 of a pickup 196 to traverse the top of the drive. A plurality of U-shaped jointing plates 344 are perpendicular to the plates 340 and 342 and welded at its respective feet to plates 340 and 342. As seen in Fig. 5, the upper guide plate 340 has a lower concave curvilinear surface 346 with a circular upper mid-portion cutout 348 which is symmetrical about the centerline. The curvilinear surface 346 has a preferred lower circular segment with a 12,1 cm (4.75 inch) radius and an upper circular segment with a 1 m (39.75 inch) radius. The cutout 348 has a 5,7 cm (2.25 inch) radius. The bottom length of upper guide plate is 69,9 cm (27.5 inches). The lower guide plate 346 has a pentagon shape with an upper convex curvilinear surface 350 that is symmetrical about the centerline. Each half of surface 350 has a circular segment to produce a guide path 352 (Fig. 4).

As upper wheel 208 of pickup 172 enters either end of guide path 352, it will cause pickup 172 to rotate slightly in the direction of motion. When pickup upper wheel 288 enters cutout 348, the top of pickup 172 is prevented from rotating and the pickup tail will then rotate in the direction through the center of the drive. In this way, pickup 172 is rotated into preferred orientation to exit the top guide path.

Referring now to Figures 26, 27 and 28, details of the dampening action imparted to the apparatus is described together with an improved locking device.

As a pan 16 (Fig. 1) traverses the top of the conveyor 10, the shoes 98 (Fig. 1) are engaged in the tracks 100 and 101 (Fig. 21) of the top transfer guide 102 (Fig. 1) and lift the transfer guide upward at the apex of the travel and then returns as the shoes pass from the apex of travel. The top transfer guide 102 (Fig. 19) is comprised of the sliding guide support 107 and transfer guide 108. The center tube 109 of the sliding guide 107 is bolted 111 to the fixed tower 22. In Fig. 26 the vertical weight of the transfer is counter balanced by the four shock absorbers 113 which also provide a dampening motion for the guide movement. Inside the center tube 109 is a ground tube 114 (Fig. 27) that provides a vertical guide for the sliding guide 107. At the bottom end of the round tube 114 is round bar that engages a friction bar 115 and is restrained by a captive bar 116.

Bellville washers

117 provide friction between a friction plate 118 and the captive bar 116. The friction connection is then established between the fixed tower 22 and the sliding guide 107 and still allow a downward movement of the transfer guide as the compression chain shortens during the life of the conveyor.

The bottom transfer guide 130 floats down and up as a pan 16 (Fig. 1) traverses the bottom of the conveyor 10 (Fig. 1). The vertical weight of the bottom transfer guide 130 is transferred through the two shock absorbers 131 (Fig. 22) and two die springs 132 (Fig. 22) to the header 28. The shock absorbers 131 provide the dampening of the vertical motion of the bottom transfer guide 130. The upward motion of the guide 130 is restricted by die spring 133 and is mounted such that it comes in contact with the under side of header 28 (Fig. 1) during excessive upward movements. This series of die springs and shock absorbers keep the bottom transfer guide at a prescribed reference point and still allow vertical motion with a dampening effect.

When a pan 16 (Fig. 1) is at the bottom of the conveyor 10 the lock link system 140 (Fig. 4 and 25) is in its extended position. The height of the lock link bar 141 (Fig. 4) is such that the top of the bar 141 is 1/8 (0.125) of an inch below a bearing roller 238 (Fig. 3) of a compression link. Normally a service brake 156 (Fig. 2) provides the holding power to resist any unbalanced load. If one or both of these brakes 156 fail then the compression chain 78 could move in the direction of the unbalanced load. The lock link bars 141 are extended and retracted by the cam motion of the actuator 143 (Fig. 25). In Fig. 25 the lock link bars 141 are shown extended to engage the compression chain. When the bar 141 is rotated clockwise 180 degrees, the lock link bar will retract and allow the compression chain 78 to move.

Claims

A vertical conveyor comprising:

a frame (12) having a first vertical frame section (22) and a second vertical frame section (24) spaced apart, but supportingly connected thereto,

a plurality of load supports (16), each support (16) having a first and second end capable of holding a load to be conveyed around in a looped path, each support (16) being movably mounted at the first and second ends respectively to the first and second frame section (12, 22) such that as one support (16) is being conveyed upwardly, while another support (16) is being conveyed downwardly so that the supports (16) pass one another at a predetermined spaced apart horizontal distance which defines the support spacing,

first and second conveying means (122, 124) mounted respectively to said first and second frame sections (22, 24) for respectively conveying a first and second end of said supports (16), said first and second conveying means (122, 124) each comprising a looped compression chain (78) supporting said supports,

a pick-up of drive chain (170) comprising at least two strands (190, 191) and through pins (194) interconnecting the matched strands,

a plurality of pick-up arms (172) pivotally connected to said through pins (194) such that said pick-up arms (172) engage and drive said compression chain (78), and

motor means (120) for simultaneously driving said first and second pick-up drive chains (190, 191) so that said pick-up arms (172) engage and drive said compression chain (78) so as to move said load supports (16),

characterised in that

said pick-up arms (172) comprise a two-piece journal construction having an upper head portion (196) and lower tail portion (198), each portion having cut outs at mating ends to form an opening through which a respective through pin (194) is received, said upper head portion (196) and lower tail portion (198) being removably mated to each other so as to enable ready disassembly of the pick-up arms (172) from the pick-up drive chain (170).
The vertical conveyor according to claim 1 wherein said first and second conveying means (122, 124) comprises a compression chain assembly (124) which supports said load supports (16), and a plurality of pickup arms (172) pivotally connected to said pickup drive chain (122) such that said pickup arms (172) engage and drive said compression chain (124) so as to move said load supports (16).
The vertical conveyor according to claim 2 wherein said pickups (172) are pivotally mounted offset on said pickup drive chain (122) to aid in engagement of said pickups (172) with said compression chain (124).
The vertical conveyor according to claim 2 or 3 wherein said compression chain assembly includes an endless roller chain comprised of interconnecting, elongate compression links (214, 212) and transverse axles (210) mounted at each end of said compression links (212, 214) such that said pickup arms (172) engage said axles (210) for pushing said compression links (212, 214) upward.
The vertical conveyor according to claim 4 wherein said load supports (16) include load support mounting arms, and means pivotally mounting said load support mounting arms to said compression links (212, 214).
The vertical conveyor according to claim 1 including a mounting member extending in said support spacing, wherein said motor means (120) is mounted to said mounting member, and including a connecting member supportingly connecting said first and second frame sections (122, 124), and wherein said motor mounting member is suspended from said one connecting member substantially centrally between said frame members (22, 24).
The conveyor according to one of the claims 1 to 6 wherein the pickup drive chain (170) comprises two spaced roller chains (190, 191), each through-pin (194) interconnecting said roller chains, wherein said pickups (172) are pivotally connected to said roller chains between said pickups (172).
The conveyor according to one of the claims 1 to 7 wherein said pickup drive chain (170) includes a link, and a link pin (172) interconnecting said links, and wherein said through-pins (194) are offset from said link pins (197).
The conveyor according to one of the claims 1 to 8 wherein said pickups comprise the upper head portion and the smaller, lower bifurcated tail portion.
The conveyor according to one of the claims 1 to 9 wherein the upper head portion (196) includes two receiving notches (200) for receiving therein respective through-pins on said compression chain (124).