parts of sandicator crusher

cone crusher parts

cone crusher parts

The cast steel spider cap has been designed to serve as a feed distribution plate for coarse materials. It is recessed on the 22, 30, 36 and 48-in. crushers. For fine materials, the wobble plate feeder a more effective means of distributing the feed is recommended.

The annealed cast steel top shell and spider are made in one piece. The spider is of the three arm type, equipped with a self-aligning, Scor-Proof plastic ball and socket bearing in crusher sizes 22 to 48-in., and with an hourglass type bearing in sizes above 48-in. The lubricant is sealed in with a garter type oil seal. Bearings can be lubricated from outside the topshell on the 51, 60 and 84-in. crushers through oil holes in spider caps of the four smaller sizes.

The mainshaft is of high grade forged steel, annealed for stress relief. It is tapered to gauge for head center fit. The bottom of the shaft is fitted with a polished bronze step bearing. The journal for the spider bearing is formed by a sleeve shrunk on the shaft on the 51, 60 and 84-in. crushers. Short, heavy mainshaft design results in long life.

The step bearing consists of a bronze mainshaft step, a bronze piston wearing plate, and an alloy steel washer between the two. The washer is drilled for oil cooling and lubrication. Both the mainshaft step and the piston wearing plate are made of high lead bronze, selected to give the best bearing surface. The washer and plate are pinned in place, and the bearing surfaces are grooved to permit distribution of the lubricating oil.

The Mantalloy head mantle of this cone crusher is a replaceable wearing surface. It is made of alloyed manganese steel, and is held in place with a self-tightening head nut. On the 51-in. Hydrocone crushers and larger, the bottom portion of the mantle is ground to gauge to fit the head center, and the top portion is zinced. For crushers smaller than 51-in., the entire inner surface of the mantle is ground to gauge and no zincing is required.

The Mantalloy concave ring, or the stationary crushing surface, is available in three standard types, coarse, intermediate and fine. Helices, cast into the bottom of the concave ring, engage similar helices on the top of a cast steel concave support ring. The support ring is held by a key to the top shell to facilitate assembly, after which it is supported on the bottom shell. The helical surfaces make the concave ring self-tightening; no zincing is required.

The dust seal is a plastic ring suspended in a housing from the head center and encircling the dust collar. It is designed to accommodate the vertical adjustment and the gyrating and rotating motion of the head. All wearing parts are replaceable. The crusher is fitted with a connection for introducing low pressure air inside the seal for additional dust protection.

The eccentric is made of high carbon cast steel and fitted with a bronze inner wearing sleeve. The eccentric turns in a bronze bottom shell bushing. Both sleeve and bushing are replaceable. The eccentric throw can be changed in the field by installing a different sleeve.

The alloy steel pinion is mounted on a turned shaft. The cast steel pinionshaft housing is bolted to the machined opening in the bottom shell. It is equipped with anti-friction bearings sealed inside and out, and has separate pool lubrication in all sizes except the 36 and 48-inch machines. The 36 and 48-inch Hydrocone crushers have sleeve type counter-shaft bearings which are lubricated by the external oiling system.

The annealed cast steel bottom shell is of the three arm, open discharge type, bored to gauge for the top shell and eccentric bushing. It is bored and faced for the bottom plate, pinionshaft bearing and dust collar.

The external oil conditioning system furnished with Hydrocone crushers consists of a large oil storage tank on which are mounted a condenser type cooler, pressure type filter, motor, and a pump which pumps the lubricant to the crusher automatically. These units both cool and filter the oil. The accumulator and tank for the Automatic Reset are mounted separately from the oil storage tank.

All oil conditioning systems are equipped with oil flow and temperature safety switches which are adjusted to open the motor circuit and stop the crusher if the temperature becomes too high or if there is not a sufficient flow of oil. Flexible hose connects the lubricating unit to the crushers, greatly reducing the number of pipe fittings required and simplifying the installation.

Oil for the tank is pumped through the filter and cooler to the step bearing and up the inner eccentric bearing. It flows down the outer eccentric bearing, lubricates the gear and pinion, then returns to the tank. Tank capacities vary from 30 gallons for the 22-in. Hydrocone crusher to 240 gallons for the 84-in. machine.

23. Feed Plate 24. Screw 25. Torch Ring 26. Locking Bolt 27. Dust Shell 28. Clamp Ring 29. Adjustment Ring 30. Mainshaft Pin 31. Pin 32. Socket Liner 33. Socket 34. Eccentric 35. Eccentric Bushing 36. Counterweight 37. Counterweight Guard 38. Gear 39. Thrust Bearing 40. Countershaft Box 41. Countershaft Box Guard 42. Oil Finger Cover 43. Oil Finger 44. Countershaft Bushing 45. Countershaft 46. Pinion

CRUSHING CHAMBER may be any one of three standard types (Fine, Intermediate and Coarse) designed to assure a cubical, well-graded product. Shape of mantle and concave ring, and the range of adjustment available, results in maximum life and minimum scrap when replacing parts. Special crushing chambers also available.

BEVEL PINION AND GEAR are of the spiral design in the larger sizes provide greater tooth contact and smooth, trouble-free operation under most severe conditions. Bevel spur and pinion gears are used on smaller size Hydrocone crushers.

INNER CRUSHING CONE or mantle is one-piece Mantalloy casting held in place by a self-locking head nut. Complete contact of the ground inner surface with steel head center eliminates need for zincing in all but the larger sizes.

OUTER CRUSHING RING or concave ring is one-piece Mantalloy casting. Necessity of zincing or clamping concave ring in place is eliminated by ground-to-fit finish on outer surface and the use of an effective self-locking device.

3-PIECE STEP BEARING accommodates gyrating motion of main shaft and transmits crushing pressure to hydraulic piston. Designed to withstand bearing pressures much greater than those encountered in actual service.

While it is one of the major parts in the machine, there are few essential differences between the adjustment ring in the 10 ft. crusher and in the smaller machines, except as to size. Material of the ring which weighs 70,000 pounds is cast steel. Rigidity of the adjustment ring cross-section is essential. In this case, increased section thickness, with ordinary carbon steels, results in a reduction in deflection.

This part, which is screwed into the adjustment ring, is the means of setting of the machine. Adjustment is performed by rotating the bowl relative to the adjustment ring. In the 10 ft. machine provision has been made to adjust the setting during crushing. This increases the availability of the crusher substantially. Past practice had been to stop feed to the crusher during adjustment.

During crushing the position of the bowl and adjustment ring is maintained on the slant flank of the threads by means of the crushing force. The slant flank helps in centering the two elements. The clamp ring acts somewhat like a locking device to take up clearances. Ideally, the clamping cylinders do not have to have any greater capacity than is necessary to overcome the weight of the bowl. Practically, the clamp ring capacity is many times higher to withstand tramp passage.

To adjust the setting of the machine, hydraulic rams are used to rotate or counter-rotate the bowl in the adjustment ring. The seal between the adjustment cap and hopper is a simple, continuous, tightly fitting flap which allows free, relative rotation but prevents intrusion of dust into the thread area. The lower end of the thread connection between bowl and adjustment ring is also sealed. The hopper assembly, which is actually a part of the bowl assembly, including the hopper, hopper liner and cap closure, comprises the section in which the feed is introduced. It includes a dead bed, reducing wear and shock from the fall of the feed from the feeder above.

The adjustment rams are pressurized hydraulically and provide a setting adjustment. For normal adjustment of setting due to wear, installation and removal of the bowl is made through a swivel sheave and a cable turn applied around the adjustment cap. The bowl is then rotated by use of the maintenance crane.

The crushing head, similar in section to that of the 7 ft. machine, had three-dimensional photoelastic studies made using the technique of freezing stresses into a loaded plastic model, sectioning the model and examining the slices under polarized light. As a result of these techniques, stresses have been reduced. The core of the head consists of six massive ribs to support the crushing forces on the surface of the head. The head is cast steel.

The main shaft is of turbine rotor steel of high quality and refinement, the chemistry of which is low carbon to reduce the possibility of heat checking. It includes chrome nickel additions for deep hardening, notch toughness and resistance to fatigue. The shaft extension is provided to reduce the relative strain between the head and shaft and thereby reduce fretting in the fit, which has a heavy press. The shaft diameter is 50 percent greater than the 7 ft. crusher shaft. As a result, the shaft operates at lower values of bending stress and deflection. Reduced deflection produces distinct benefits in bearing behavior because of uniformity of oil film under load. Reduced stresses assure longer life and resistance to overloads.

The head-shaft assembly is supported by the socket and socket liner which is, in essence, a spherical thrust bearing. The function is to carry the vertical component of the crushing force while allowing the head to oscillate around the theoretical center of rotation.

The socket of carbon steel is of dowelled design. The forces between the head and the socket are normal to the spherical surface of the head and pass through the theoretical center. The line of action of these forces is such that practically pure compression is applied to the socket and liner, reducing deflection and stress to a minimum and promoting good bearing performance.

The force distribution throughout the crusher is based on a vector diagram of the cavity forces during crushing and the reactions at various associated loading points in the crusher. The vector diagram establishes their relative magnitude, direction and points of application. The actual magnitude of these forces is established by the crushing force necessary to lift the adjustment ring off the frame seat. This condition represents the maximum allowable force for normal crushing.

A baffle ring attached to the head is sub-merged around its entire periphery in a water trough resting on the socket. Dust tends to settle into the trough and must be continuously removed to prevent caking. For this reason, water is continuously fed through specially designed nozzles which scour the trough. Overflow water is carried off by internal piping and passages. The seal chamber is vented to atmosphere to prevent siphoning which may cause oil contamination of the water or vice versa.

The gears are straight tooth bevel gears and are designed to AGMA standards using a computerized program which, upon input of the basic information, such as DP, diameters, gear ratio, material properties, tooth type, provides a complete printout of the rated power on the basis of tooth strength and surface durability of the gear. The factor of safety on the gear is in excess of three on the strength basis and in excess of two on the durability basis.

expected or typical

expected or typical "life span" of wear parts of jaw crusher - crushing, screening & conveying - metallurgist & mineral processing engineer

Is there any standards or guidelines to determine the expected or typical "life span" of all wearlife of parts of jaw crusher, cone crushers or VSI crushing plant. Any help on what wear & tear can do to liners and other crusher parts is highly appreciate.

Hi, this is highly dependant on density of materials being crushed, maintenance schedules, and of course quality of wear parts being used to name but a few of the contributory factors so in my opinion it is VERY difficult to standardise life span on any crushing plant.

The standard can only be determined through the material being crushed, as the abrasive nature will be the main variable in determining wear. For example basalt is generally very low wear, granite is very high.

Historical data is very much available for various materials and there various "A typical" wear rate hours in specific regions of countries which can be used as a guideline. Ask people doing that job what wear rate they are in fact experiencing on the product you want knowledge on.

Silica content in aggregates is a huge factor. The higher the content - the more abrasive the material. Crushing wet material (for example when keeping the dust levels lower) also contributes to higher wear situations. Without mentioning the obvious factors such as tonnage or throughput as mentioned in previous comments from others, different wear alloys - manganese versus chrome/moly/manganese, different grades of hard-facing or other hardened steels all contribute. One of the factors people often forget is actual operator habits. The same crusher can wear at different rates depending on % feed into the crusher as well as rotation or operating speed set by the operator.

Many great comments offered to which I completely agree. Feed characteristics I believe is your number one factor. Abrasiveness and hardness are important factors but so are the amount of fines allowed to enter the crusher. This will also effect wear part life. The other factor is of course water. If you are using dust suppression it can have a big effect on wear life. Other factors mentioned like crusher speed and your reduction ratios all have an impact on wear life. The key to wear life is to get the best bang for your buck. If you can optimize your crusher to its best production efficiency you can then justify wear cost as your cost per ton goes down the more efficient you get. You cant change your materials natural characteristics but you can buy wear parts with the correct composition best suited for your specific application.

I agree to all of the comments that the main factor that effects the life span of the crusher liners is the abrasiveness and hardness of stone and addition to this choke feeding to the crusher can helps a lots to prolonged the life of the liners especially to the cone crusher and the VSI.

It is highly KEY that when folks are suggesting wear life it is a bit of a mugs game. You must compare the wear rates of "that specific material" in that specific quarry or very close to that operation to get HIstorical actual wear rates vs "theoretical wear rates".

That is an excellent point that youmake concerning feed consistency as this applies to all types of crushers. We tend to forget sometimes that with all the variables mentioned they simply dont mean much unless we start with the beginning which is the feed consistency. Anytime you have less then consistent feed rate to your crusher your wear parts life will be dramatically reduced regardless of your choices of wear parts. Its like I had mentioned earlier your crushers efficiency will determined wear part life. In order to achieve feed consistency you need to begin with sized material so that you can reach maximum consistency and by doing so achieve true attrition crushing. In other words let your rock become a wear part.

In order to choose the correct wear parts you should educate yourself on what your material is made up of. Knowing what your material characteristics are will help you to make the best decisions as to what type of wear parts to purchase. The best way to learn what your material is made of is to have your material tested. Some tests would include;

We have had good success in gathering data relating to the CSS over the last year at one minesite. This has provided data for trending mantle life. http://www.crushervision.comworking in a manganese casting foundry,which supply the Metso and Sandvik parts.

At the same time in Russia they have alsoconsideredaggregate shape. Quarry may have a lot of aggregate for very good price but clients (mainly - road contractors, interested in volcanic rock material) refuse to buy it due to poor shape. Some cone crushers (for example, from your brother company - Telsmith) can produce very good product, most crushers - not. The plant owner had to pay extra to get better shape - either additional passing through VSI, or bigger recirculation to get optimal feed in crushing chamber. First variant gives additional cost, second - less lifetime of wear parts per ton of product.

Long time ago I was involved in EBRD (European Bank of Reconstruction and Development) investment project in Belarus. It was about refurbishing road from Poland border to Russian border. Project was sophisticated with comprehensive feasibility study. It should be three crushing plants as well.

I don't remember expert names (or company names) involved in the study. But I remember a few figures they operated with. For limestone aggregate cost of wear/spare parts was 3-7% of new plant cost per 2000 hours, for medium abrasive granite - 5-10%, for high abrasive material - 7-15%. If material is harder than standard - plus one percent for low abrasive rock, two - for medium and three for high. For equipment older than 6000 hours spare/wear parts cost got 1-3% higher for every 2000 hours. Experts made choice of this figures mainly depends on equipment specs and their knowledge.

I remember it was stressed that these figures are more or less valid for crushing plants made by first class European manufactures according to European specifications. It was 1995-1996 and I don't now if these figures are still valid because nowdays it looks like everything made outside of China should be considered as infringing goods :)). I mean that prices and specs which are much more important may differ.

You can keep all the log books in the world but if you use low quality manganese and chrome alloys from cut rate foundries, you are only wasting your time and throwing your companies money in the GARBAGE! Look for suppliers that aren't necessarily the cheapest but that aren't slamming you over the head either. AND, LAST BUT NOT LEAST, be cautious of the OEM! All too often they source materials out from whomever has the best price or parts in stock. You may think because you are buying direct from the OEM that you are getting the BEST product, NOT ALWAYS TRUE!

Here's my personal thought, if your rock is hard Do not use impact crushers or VSI use cone and jaws I realize what foundries have good days and bad. The problem I have with most sales guys, in the industry is they sell the wrong machine into the wrong application. Make sure the mag is right for the app, if your buying direct keep the foundry responsible for the mag.

Best would to record what is happening in your crushers have it all documented and drawn out. From there you can start redesigning your mantels, bowl liners, jaws, blow bars and start playing with you material specs to improve your lifetime on them.

There is no standard but big companies have software to estimate life time. Shortly higher manganese increase life time but to increase manganese you need to increase carbon which make liner brittle.And I must disagree about VSI thing.

The rate of consumption of wear parts is as stated by several others driven by material being crushed, wear part quality and by site crushing practices. As a manufacture of crushing equipment we have some typical guidelines and we can test for part consumption in VSI crushers. But experience tells me that in most cases the utilization of wear parts is heavily dependent on proper feeding of the equipment. Under feeding or gap feeding causes issues that are portrayed by utilizing a small portion of the available wear material in a part such as a jaw plate or a cone liner.

The main wearing mechanism in crushercavity is abrasive wearing. Fatigue wear isalso present as wear part are subjected tomultiple compression or impact loads.Abrasive wear (or abrasion)Crushers typically compress the feed material between the fixed and movable wearparts. Besides the breakage of the feedmaterial, this is also wearing material awayfrom the wear part. Wearing micromechanisms are:

During the crushing cycle, gouging orhigh stress abrasion is present depending onthe particle size of feed material. Betweenthe crushing cycles when particles of feedmaterial are sliding against wear parts, lowstress abrasion is present.

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primary gyratory parts | gyratory crusher parts | cms cepcor

primary gyratory parts | gyratory crusher parts | cms cepcor

The CMS Cepcor product range of precision machined replacement parts to suit primary gyratory crushers includes complete mainshaft assemblies, mainshafts, cores, spider assemblies, spider bushings, spider seals, top shell assemblies, bottom shell assemblies, eccentric bushings, shell bushings, mainshaft nuts, spider rim liners, spider shields, dust seal rings, retainers, step washers, piston wear plates, pinion shafts, shell bolts and many more.We are the genuine alternative to the original equipment manufacturer.

CMS Cepcor premium manganese is a solution annealed, water quenched, austenitic manganese steel that has been developed from the original Hadfields manganese steel specifications, although our variation can provide unequalled toughness with good resistance to abrasion, which improves as the steelwork hardens in operation.

gyratory crushers

gyratory crushers

The belowimage shows a sectional view of a typical gyratory crusher. This type of machine is, by virtue of chronological priority, known as the standard gyratory crusher. Although it incorporates many refinements in design, it is fundamentally the same crusher that first bore the name of gyratory; its crushing chamber is very much the same shape; the motion is identically the same, and the method of transmitting power from belt to crushing head is similar. It is an interesting fact that the same similarity in essential features of design exists in the case of the standard, or Blake type, jaw crusher, which is something in the way of a tribute to the inspiration and mechanical ability of the men who originated these machines.

Essentially, the gyratory crusher consists of a heavy cast-iron, or steel, frame which includes in its lower part an actuating mechanism (eccentric and driving gears), and in its upper part a cone-shaped crushing chamber, lined with wear-resisting plates (concaves). Spanning the crushing chamber across its top is a steady-rest (spider), containing a machined journal which fixes the position of the upper end of the main shaft. The active crushing member consists of the main shaft and its crushing head, or head center and mantle. This assembly is suspended in the spider journal by means of a heavy nut which, in all but the very large machines, is arranged for a certain amount of vertical adjustment of the shaft and head. At its lower end the main shaft passes through the babbitted eccentric journal, which offsets the lower end of the shaft with respect to the centerline of the crusher. Thus, when the eccentric is rotated by its gear train, the lower end of the main shaft is caused to gyrate (oscillate in a small circular path), and the crushing head, likewise, gyrates within the crushing chamber, progressively approaching, and receding from, each element of the cone-shaped inner surface.

The action of the gyratory crusher, and of the other member of the reciprocating pressure family, the jaw crusher, is fundamentally a simple one, but as will be seen a great deal of thought and some very progressive engineering has been expended upon the design of crushing chambers to increase capacities and to permit the use of closer discharge settings for secondary and fine-reduction crushing (various crusher types).

Referring to the table, always available from the manufacturer, it will be noted that standard gyratory crushers are manufactured in commercial sizes ranging from 8 to 60 receiving openings. Capacities are listed, for minimum and maximum open-side discharge settings, in short tons per hour, and the horsepower requirements for soft and hard materials are listed for each size. The capacities, and the minimum settings, are based upon the use of standard (straight-face) concaves.

Primary gyratory crushers are designated by two numbers. These are the size of the feed opening (in inches) and the diameter of the mantle at its base (in inches). A 60~x~89 crusher would have an opening dimension of 60 inches (152 cm) and a diameter across the base of the mantle of 89 inches (226 cm).

To stand up under the extremely rugged work of reducing hard and tough rock and ore, and in doing so to maintain reasonably true alignment of its running component, the crushermust necessarily be of massive and rigid proportions, rigidity being of equal importance to ultimate strength. Regardless of the tensile strength of the metal used in the main frame, top shell, and spider, these parts must be made with walls and ribs thick enough to provide this rigidity. Therefore it is practicable to use close-grained cast iron, and special high-test mixtures of cast iron, for these parts, if the machine is intended for crushing soft or medium materials. When very hard and tough materials are to be crushed, the machine is usually strengthened by substituting cast steel in one or more of its parts.

Wearing parts in the gyratory crusher may be either chilled cast iron or manganese steel, depending on the character of the material to be crushed and the particular class of service for which the machine is intended. Standard crushers, in the small and medium sizes, are customarily fitted with chilled-iron head and concaves for crushing soft and medium limestone and materials of similar hardness and abrasiveness, because its relatively low first cost and excellent wearing qualities make it the most economical material to use when the service is not too severe. Manganese steel, which combines extreme toughness with unsurpassed wear-resistance, is the universal choice for crushing hard, tough rock regardless of the class of service or type of crusher. Even though the rock be quite soft and non-abrasive, it is general practice to use manganese steel concaves in the larger sizes of primary crushers because of the shocks attendant upon handling large and heavy pieces of rock.

The primary rockbreaker most commonly used in large plants is the gyratory crusher, of which a typical section is shown in Fig. 5.It consists essentially of a gyrating crushing head (521) working inside a crushing bowl (522) which is fixed to the frame (501).

Thecrushing head is carried on a short solid main shaft (515) suspended from the spider (502) by a nut (513) ; the nut fits into the seating of a sleeve (514) which fixes its position in relation to the spider and, therefore, to the frame (501). The lower part of the main shaft fits into a sleeve (530) set in an eccentric (527), to which is keyed the bevel driving gear (528) ; the bevel pinion (533) is similarly fastened to the countershaft (535) and engages with the bevel gear. The whole of this driving assembly is protected from grit and dust by means of a dust seal (524), (525), and (526).

The countershaft carries the driving pulley, and as it revolves it causes the eccentric to rotate ; as it rotates the main shaft gyrates and with it the crushing head ; the top of the shaft at the point of suspension has practically no movement. Although the motion of the head is gyratory, the main shaft is free to rotate in the eccentric and it actually revolves slowly in relation to the bowl, thus equalizing the wear on the mantle (519) which lines the head and on the concave liners (522 and 523) which comprise the bowl. Both mantle and bowl liners are usually made of manganese steel. The suspension nut (513) is adjustable and enables the crushing head and main shaft to be raised in relation to the bowl to compensate for wear. The size of the product is determined by the distance between the bottom edges of the crushing head and the bowl, in the position when they are farthest apart.

The crushing action is much the same in principle as that of a jaw crusher, the lumps of ore being pinched and broken between the crushing head and the bowl instead of between two jaws. The main point ofdifference between the two types is that the gyratory crusher does effective work during the whole of the travel of the head, whereas the other only crushes during the forward stroke. The gyratory crusher is thereforethe more efficient machine, provided that the bowl can be kept full, a condition which is, as a rule, easy to maintain because it is quite safe to bury the head in a pile of ore.

Tables 7 and 8 give particulars of different sizes of gyratory crushers. As in the previous paragraph, the capacity figures are based on material weighing 100 lb. per cubic foot and should be increased in direct proportion for heavier ores.

Primary and secondary gyratory crushers, including the cone crusher, can be directly connected to slow speed motors if desired, but the standard method of drive is still by belt and pulley. Jaw crushers must be belt-driven.

An efficient substitute for the flat belt in all cases is the Texrope drive, which consists of a number of V-shaped endless rubber belts running on special grooved pulleys. The grip of these belts is so great that the distance between the pulley centres can be reduced to about 30% of that required for a flat belt. This results not only in a saving of space but also in greater safety, since the drive is easier to protect and there is no danger of an accident such as might occur if a long belt were to pull through its fasteners. Moreover, the short drive makes it possible for any stretch to be taken up by moving the motor back on its rails without the necessity of cutting and rejoining the belts. The flexibility and ease of maintenance of the Tex-rope drive makes it very suitable for crushing machines.

LOW OPERATING COSTS Vertical adjustment compensates for wear on crushing surfaces (also maintains product uniformity). Oiling system provides proper lubrication throughout, including spider. Effective dust seal prevents dust infiltration to moving parts. Long life bearings, easy to replace.

Strength, of course, makes an all-important contribution to the rugged heavy duty service and day-in, day-out dependability demanded of a crusher. However, strength does not necessarily mean excessive weight. The metals and alloys used in construction and the distribution of weight are actually the determining factors in the strength of a gyratory crusher.

MAINSHAFT ASSEMBLY mainshaft forged steel; annealed quenched and tempered. Tapered to gauge for head center fit. Head center of cast steel. Head mantle of manganese steel. Mainshaft sleeve shrunk on mainshaft to provide renewable wearing surface on spider bearing.

Gyratory crusher advanced design includes the placing of circumferential ribs around the top and bottom shells. These integrally cast reinforcing rings prevent distortion provide the rigidity necessary to maintain true alignment of running parts.

Hollow box construction of the cast steel spider affords maximum strength with the least amount of feed interference. Arms are cast integrally with the heavy outer rim. Crushing stresses are transmitted to the rim, which is taper-fitted to the top shell. Because spider and top shell are interlocked, they reinforce each other to provide maximum stability and rigidity.

The bottom shell is the foundation of the crusher. It must be strong enough not only to support the weight of the crusher, but to withstand extreme crushing stresses (most stresses terminate here) strong enough to protect vital mechanism the eccentric, gears and countershaft assembly housed in the bottom shell. In the Gyratory crusher, bottom discharge design makes possible a compact, squat structure of simplified design and comparatively high strength. Supplementing the strength of the bottom shell are the previously described circumferential ribs. Crushing stresses are transmitted directly to these reinforcing members through three radial arms.

Because the mainshaft does the actual crushing, it must literally possess crushing strength. In the Gyratory crusher, the eccentric is located directly below the crushing head. This design permits the use of a short, rigid mainshaft a mainshaft that will withstand the strain of severe service.

Flexibility is the keynote of the Gyratory crusher efficiency and economy. While your particular installation is designed to best meet your specific and immediate requirements, built-in flexibility permits adaptation to changing operating conditions anytime in the future.

A Gyratory crusher not only affords a maximum capacity-to-size ratio, but provides the variable factors which facilitate increasing or decreasing capacity as the need arises. Flexibility in a Gyratory crusher also permits compensation for wear and assures product uniformity.

In the Gyratory crusher, the use of spiral bevel gears instead of spur gears makes possible the broad range of speeds conducive to meeting varying capacity demands. Because the Gyratory crusher is equipped with an external oiling system, speed may be reduced as much as desired or required. Adequate lubrication is supplied at even the lowest speeds, because the flow of oil is not relative to the crushers operating speed as is the case with an internal system.

With a primary gyratory crusher running at a given countershaft speed, capacity is increased as eccentricity is increased. At a given eccentricity, greater capacity results from higher countershaft speeds. Conversely, reducing either the speed or eccentricity reduces capacity.

Another high capacity characteristic of the Gyratory crusher is a large diameter crushing head. Because the area of discharge opening is directly proportionate to head diameter, high capacities result.

VARIABLE INITIAL SETTINGS The contour of the crushing chamber at the bottom is designed to afford various initial settings without changing the angle of the nip. This is accomplished by installing lower tier concaves of the shape and thickness for the desired setting and capacity.

HOW SIZES ARE DESIGNATED The numerical size designation of Gyratory crushers represents the feed opening and the maximum diameter of the crushing head. For example, a 60-109 Gyratory crusher has a 60-inch receiving opening and an 109-inch maximum diameter crushing head.

ELIMINATES DIAPHRAGM In a gyratory crusher with aside discharge, sticky materials may pack on the diaphragm and eventually cause considerable damage. Thestraight down discharge of the Gyratory crusher is a design simplification that eliminates the diaphragm and itsmaintenance problems.

CONTRIBUTES TO BALANCED CIRCUIT The adaptabilityof a primary crusher to a large extent dictates the plantflowsheet the initial and overall operating costs of subsequent equipment. With a Gyratory primary crusher,these costs are kept at a minimum because the entirecrushing circuit remains in balance. The concrete foundation may be modified for use as a surge bin. This storagecapacity permits controlling the flow of material throughthe plant. Secondary and tertiary crushers, vibrating screens, etc. may be installed in size ranges and types tomeet the requirements of a constant tonnage. For thosefew installations where a side discharge is essential, a discharge spout can be furnished. Another factor in maintaining a balanced circuit is the vertical adjustment(pages 12 and 13) which permits retaining the initial discharge setting by compensating for wear on mantle andconcaves. Related equipment need not be readjusted because of variations of feed size from the primary crusher.

In the Gyratory crusher, the original discharge setting may be maintained for the life of a single set of alloy crushing surfaces with only one resetting of concaves. Raising the mainshaft compensates for wear onconcaves and mantle. This simplified vertical adjustment cuts resetting time facilitates holding product size.

The threaded mainshaft is held in and supported from the spider hub. (See illustration at lower left.) A vertical adjustment range of from 6 inches to approximately 11 inches is possible, depending upon the size of the machine. The original discharge setting can be maintained until the combined wear of mantle and concaves is about one-third of the vertical adjustment.

A cast steel, split adjusting nut with a collar issupported on a two-piece thrust bearing in the spider hub. The nut is threaded for the mainshaft. The outside of the nut is tapered, with the large diameter at the top. The weight of the head and shaft draws the nut down in its tapered seat in the collar to form a self-clamping nut. Desired setting is achieved by positioning split nut in the proper location on the threaded portion of the mainshaft.

The Gyratory crusher is also available with a Hydroset mechanism a hydraulic method of vertical adjustment. With the Hydroset mechanism, compensation for wear and product size control is a one- man, one-minute operation. The Hydroset mechanism consists of a motor-driven gear pump operated by push button.

The accompanying drawings show the simplicity of Hydroset design. The mainshaft assembly is supported on a hydraulic jack. When oil is pumped into the jack, the mainshaft is raised compensating for mantle and concave wear or providing a closer setting. When oil is removed from jack, the mainshaft is lowered and a coarser setting results.

Since the mainshaft assembly is supported on a hydraulic jack, its position with respect to the concaves, and therefore the crusher setting, is controlledby the amount of oil in the hydraulic cylinder.

Oil pressure is maintained in the hydraulic cylinder below the mainshaft by a highly effective chevron packing. The oil supply of the Hydroset mechanism functions independently of the crushers lubrication system.

If a Gyratory crusher equipped with Hydroset mechanism stops under load, the mainshaft may be lowered to facilitate clearing of the crushing chamber by merely pumping oil out of the cylinder. Only under extreme conditions is it necessary to dig out. When the cause of the stoppage is remedied, the oil is pumped back into the cylinder quickly, returning the mainshaft assembly to its initial position.

STEP BEARING consists of bronze mainshaft step, bronze piston wearing plate, and an alloy steel washer between the two. Washer is drilled for oil cooling lubrication. Bearing surfaces are grooved to permit oil distribution.

Utilizing pool lubrication, a gun-type fitting in the spider arm makes it easy to oil the spider bearing. A garter-type oil seal in the bottom of the bearing retains oil. Being flexible, the seal compensates for movement of crusher mainshaft.

The countershaft assembly is an anti-friction, pool-lubricated unit. Both ends of the bearing housing are sealed by garter-type spring oil seals which: (1) keep dust from anti-friction bearings; (2) separate pinion- shaft bearing lubricant from oil lubricating the eccentric and gears.

Getting the most out of a crusher in performance and capacity depends largely upon positive lubrication. And positive lubrication means more than just adequate oil lubrication. It also entails conditioning oil for maximum lubricating efficiency.

The Gyratory crusher is equipped with an externally located, fully automatic lubricating system. Positive and constant lubrication is maintained at all speeds even at the slowest speed. If desired, oil may be circulated through bearings of Gyratory crusher during shutdown periods.

A gear pump circulates oil from storage tank, through crusher and back. Each time oil is pumped to the crusher, it passes through the filter and cooler. The cleaned, cool oil lubricates the step bearing (in Hydroset mechanism only), the eccentric wearing plate and the inner eccentric bearing. At the top of the bearing, most of the oil flows through ports in the eccentric to the outer eccentric bearing. Theoil then flows down the outer eccentric bearing and lubricates the gear and pinion before it is returned to storage. The overflow oil which may have become contaminated is returned immediately to the oil conditioning tank. It does not contact any other wearing parts within the crusher.

The oil conditioning system may be modified to meet your particular applications. In cold climates immersion heaters are installed in the storage tank to preheat oil. This arrangement permits circulating warm oil through the crusher during shutdown periods. A thermostatic control turns heater on and off. Only in a crusher specifically designed for external oiling is it possible to circulate warm oil when the crusher is stopped.

An added measure of safety is providedby the oil conditioning system. Foreignmaterial is removed by pumping warm oilthrough a mechanical filter. After oil isfiltered, it flows through a condenser-type cooler before it is returned to the crusher.

An oil flow switch provides automatic protection against possible damage caused by oil system failure. This switch stops the crusher immediately if oil flow is insufficient for proper lubrication. Interlocks between pump motor and crusher prevent starting crusher before oil circulation begins.

In addition to its other advantages, the externally located oil conditioning system is easy to service. The unit consists of (A) an oil storage tank, (B) a motor-driven gear pump, (C) a pressure- type filter, and (D) a condenser-type cooler.

In the gyratory crusher, expensive castings are protected by replaceable parts. Rim and arm liners protect the spider from wear. Bottom shell liners and shields provide protection below the crushing chamber. An alloy steel shaft sleeve protects the mainshaft in the spider bearing. The eccentric sleeve and bushing are easily replaced when worn.

Because all parts are readily accessible and removable, down time is kept to a minimum. For example, the countershaft assembly is removed as a unit and can be taken to your machine shop for convenient servicing. Eccentric bearings are bronze bushings. Because bronze is used, the need for babbitt mandrels and melting facilities is eliminated.

Sealing out dirt and dust and their equipment-destroying abrasive action results in obvious maintenance economies. The type of dust seal used in the gyratory crusher is the most reliable and effective device ever developed for preventing excessive wear caused by dirt and dust.

In the gyratory crusher, a synthetic, self-lubricating, light-weight ring is used as a dust seal. The ring is enclosed between a dust collar bolted to the bottom shell and a recess in the bottom of the head center. Regardless of the eccentric throw and vertical positioning, the ring maintains its contact with the outer periphery of the dust collar. Because of its light weight and self-lubricating characteristics, wear on this ring is negligible.

Provisions have been made on the gyratory crusher for the introduction of low pressure air to the dust seal chamber. This internal pressure, which can be obtained through the use of a small low pressure blower, creates an outward flow of air through the dust seal. This prevents an inward flow of abrasive dirt and dust. The combination of a highly effective sealing ring and the utilization of internal air pressure protects the eccentric and gears from destructive infiltration even under the most severe conditions. When required, this additional protection is supplied at a nominal additional cost.

All of the operating advantages all of the engineering and construction features described in this bulletin are found in both the primary and secondary gyratory crushers. Of course, certain modifications have been made to efficiently accomplish the tough, rugged job of secondary crushing. For instance, the secondary gyratory crusher has been engineered to accommodate the greater horsepower requirement of secondary crushing. Increased strength and durability have been built into all components.

In the past, primary crushers had to be set extremely close in order to provide an acceptable feed for secondary crushers. As a result, primary crushers were penalized by reduced capacity and excessive maintenance. The secondary gyratory crusher was engineered to solve this problem.

Anticipating product size variations, Allis-Chalmers has designed the secondary crusher with a large feed opening one large enough to accept oversized materials. This design feature is particularly advantageous when the secondary gyratory crusher follows a primary crusher that has no vertical adjustment for wear.

A large diameter crushing head along with tailored-to-your-operation design results in big capacity. An acute angle in the crushing chamber and a long parallel zone facilitate precision setting assure a cubical, well graded product distributes even the normal wear throughout the crushing chamber.

1. Spider cap 2. Spider 3. Hour glass bushing 4. Spider bearing oil seal 5. Spider bearing oil seal retainer 6. Spider bearing oil seal retainer screws 7. Spider joint bolts 8. Spider joint bolt nuts 9. Spider joint bolt lock nuts 10. Spider arm shield 11. Spider arm shield bolts 12. Spider arm shield bolt nuts 13. Center spider rim liners (not shown) 14. End spider rim liners 15. Rim liner bolts 16. Rim liner bolt nuts 17. Spider bearing spherical support ring 18. Spider bearing spherical support ring seat 19. Spider lubricating hose bushing 20. Spider lubricating hose 21. Spider lubricating hose bracket 22. Spider lubricating hose grease fitting 23. Spider lubricating hose bracket bolts 24. Spider joint studs (not shown) 26. Mainshaft thrust ring 27. Mainshaft thrust ring bolts 31. Top shell 32. Concave support ring 33. Upper concaves 34. Upper middle concaves 36. Lower middle concaves 37. Lower concaves 43. Bottom shell 44. Bottom shell joint bolts 45. Bottom shell joint bolt nuts 46. Bottom shell joint bolt lock nuts 47. Bottom shell bushing 48. Bottom shell bushing key 49. Bottom shell bushing clamp plate 50. Bottom shell bushing clamp plate bolts 51. Bottom shell front arm liners 52. Bottom shell rear arm liners 53. Bottom shell side liners 54. Bottom shell hub liners 55. Dust collar 56. Dust collar cap screws 57. Dust collar gasket 63. Bottom plate 64. Bottom plate studs 65. Bottom plate stud nuts 66. Bottom plate stud lock nuts 67. Bottom plate dowel pin 68. Bottom plate drain plug 69. Bottom plate gasket 95. Eccentric 96. Eccentric sleeve 97. Eccentric sleeve key 98. Bevel gear 99. Bevel gear key 100. Bevel gear key cap screws 101. Eccentric wearing plate 107. Mainshaft 108. Head center 109. Mantle lower section 110. Mantle upper section 111. Head nut 112. Dowel pin (for keying head nut to mantle) 113. Mainshaft sleeve 114. Adjusting nut 115. Adjusting nut collar 116. Enclosed ring type dust seal sealing ring 117. Enclosed ring type dust seal retaining ring 118. Enclosed ring type dust seal bolts 119. Adjusting nut tie bar 120. Adjusting nut tie bar bolts 121. Adjusting nut key 124. Pinion bearing housing 125. Pinion bearing housing gasket 126. Pinion bearing housing studs 127. Pinion bearing housing stud nuts 128. Pinion bearing housing stud lock nuts 129. Pinion bearing housing dowel pin 130. Pinion bearing housing oil drain plug 131. Pinion bearing housing oil level plug (not shown) 132. Pinion bearing housing oil filler plug 133. Pinionshaft 134. Drive sheave and bushing 135. Drive sheave key 136. Pinion shaft lock nut spacer 137. Pinion shaft lock nut spacer lockwasher 138. Pinion shaft lock nut spacer lockwasher gasket 139. Pinion bearing seal plate 140. Pinion bearing oil seal 141. Pinion bearing seal plate gaskets 142. Pinion bearing seal plate bolts 143. Pinionshaft outer bearing 144. Pinionshaft inner bearing 145. Pinionshaft bearing spacing collar 146. Pinionshaft bearing spacing collar gasket 147. Pinion 148. Pinion key 149. Pinion retainer plate 150. Pinion retainer plate bolts

In the dimension charts above, the first number in each size classification designates the size of the receiving opening in inches. The second number is the largest diameter of the mantle in inches. Primary crushers having the same mantle diameter use the same size bottom shell, gears, eccentrics and countershaft assemblies.

Secondary crushers use the same size bottom shells as certain size primary crushers, but different size top shells, mainshaft and spider assemblies. The 30-70 secondary gyratory crusher uses the bottom shell of the 42-65 primary crusher; the 24-60 secondary uses the 30-55 primary bottom shell.

Capacities given here are based on field data under average quarry conditions when crushing dry friable material equivalent to limestone. Because conditions of stone and methods of operation vary, capacities given are approximate only.

Where no capacity data is given the crusher is under development.Figures under Maximum Horsepower are correct only for throw and pinion Rpm given above. When speed is reduced, Maximum Horsepower must also be reduced proportionately.

This graph is based on customary practice and is principally a guide. Size of crusher may vary considerably with different materials, depending upon stratification, blockiness, quarry methods and size of quarry trucks. Pieces that cannot be handled by crusher without bridging should be broken in the quarry.

The screen analysis of the product from any crusher will vary widely, depending upon the character of the material, quarry conditions, and the amount of fines or product size in the initial feed at the time

the sample is taken. These factors should be taken into consideration when estimating the screen analysis of the crusher product. Product gradation curves based on many actual screen analyses have been prepared which can be used for estimating.

The crusher discharge opening on the open side will govern the product gradation from a crusher if corrected to take into consideration quarry or mine conditions, particularly as to the amount of fines in the crusher feed. The tabulation at the left is basedon an average of many screen analyses and gives the approximate percentage of product equal to the open side setting of the crusher. Its actual use when the feed conditions are definitely known should be corrected to take care of these conditions, particularly insofar as fines or product size in the feed are concerned. The curves on these pages have been prepared giving the approximate screen analysis of the crusher product and should be used in conjunction with Table I

Table I shows 90% of product should pass a 6-inch square opening flat testing sieve. Using the 90% vertical line on Table II, follow it up to the horizontal line of 6 inches. Follow the nearest curve to the intersection, and using this curve you will get the following approximate screen analysis.

Until recently, there has been no way of accurately determining the power required for agiven crushing operation. With little or no factualoperating data correlated into useful form, it wasdifficult even for the most experienced operators toarrive at a correct size crusher or a proper size crusher motor to do a given job.

The correlation of all this factual material, from extensive field operating data and laboratory data covering wide varieties of material, ranges of reduction sizes, and types of equipment, made it possible to establish a consistent common factor known asthe Work Index for accurately determining the power required for crushing.

In the Work Index method, frequently referred to as the Bond method, the Work Index is actually the total work input in kwhr per short ton required to reduce a given material from theoretically infinite particle size to 80% passing 100 microns or approximately 67% passing 200 mesh. Knowing the Work Index, you need only apply the given equation to determine power input required. The calculated power input enables you to select the proper crusher.

In order to simplify the selection of a crusher by the Work Index method, the following form has been developed. References below the form explain the various parts of the calculation, and, immediately below, a complete example is worked out.

REFERENCE I Average Impact. As noted, the Work Index is determined from the average impact value and the specific gravity of the material being crushed. The impact value and Work Index can be determined in the Processing Machinery Laboratory, or these values can be determined from a comparable operation in the field. Acomplete listing of Work Indexes of materials which have been tested in the laboratory.

REFERENCE II Feed Size. In the case of a primary crusher this may be somewhat difficult to obtain. Experience indicates, however, that in most cases 80% of the feed size will pass a square opening equal to from half to two-thirds of the crusher receiving opening.

A crushed stone producer desires a primary crusher to handle the product from a 3-yard shovel at an average rate of 350 tph. The rated capacity of the crusher must, of course, be greater than this because of inevitable quarrying and crushing delays. A crusher setting of 5 in. on the open side is desired because of following equipment and the requirements for stone.

MATERIAL: Limestone WORK INDEX 10.7 CRUSHER: 42-65 Primary gyratory Open Side Setting: 5; Eccentric Throw: 1 Recommended Operating Speed; 400 Rpm (Approximately 80% of Maximum Speed) Capacity at Recommended Speed: 438 Short Ton/Hour Maximum Horsepower Allowable at Selected Throw and Speed: 213 Horsepower. FEED SIZE: (F) 80% Passes 28 (66% of Feed Opening) F 711,000 Microns F = 842 PRODUCT SIZE: (P) 80% Passes 4, P = 108,000 Microns P = 328 F P = 514 HORSEPOWER/SHORT TON = 10.7 x 13.4 x 514/842 x 328 = .267 .267 Horsepower/Short Ton x438 Short Tons/Hour Capacity = 117Horsepower Required RECOMMENDED MOTOR SIZE: 150 Horsepower Motor.

Tabulated data presented has been compiled from tests made in the Allis-Chalmers Research Laboratory. This data is a cross section of impact and compressive strength tests made on hundreds of different rock samples for customers in the U.S. and abroad.

Ten or more representative pieces of broken stone, each of which passes a square opening three inches on a side and will not pass a two-inch square, are selected and broken individually between two 30-lb pendulum hammers. The hammers are raised by an equal amount and released simultaneously. This is repeated with successively greater angles of fall until the specimen breaks. Its impact strength is the average foot-pounds of energy represented by the breaking fall divided by the thickness in inches. The average impact strength is the average foot-pounds per inch required to break the ten or more pieces, and the maximum is the foot-pounds per inch required to break the hardest piece, the highest value obtained.

The compressive strengths of many materials have been measured in the Laboratory by cutting samples into one-inch cubes which are then broken under slow compression in a Southwark compression tester. This indicates the compressive strength in pounds per square inch.

The correlation between the compressive strengthand the impact crushing strength is inconsistent, and experiencehas shown that theimpact strength is abetter criterion of theactual resistance tocrushing. The impactdevice more nearly approaches actual crusher operation, both invelocity of impact andin the fact that broken stone is used intesting.

The average impactcrushing strength isan indication of theenergy required forcrushing, while themaximum compression values indicate the danger of crusher breakage and the type of construction necessary. Crusher capacities do not vary greatly with the impact strength. There is a capacity increase of less than 10% from the hardest to the softest stone, where packing is not a factor.

what is a jaw crusher | advantages, types, parts and specifications | quarrying & aggregates

what is a jaw crusher | advantages, types, parts and specifications | quarrying & aggregates

The series of jaw crushers produced by Rayco are widely used in mining and aggregate crushing industries. They are specially developed for crushing the hardest ores and rocks, and are mainly used as primary crushers.

When working, the motor drives the belt and pulley to move the movable jaw up and down through the eccentric shaft. When the movable jaw rises, the angle between the toggle plate and the movable jaw becomes larger, thereby pushing the movable jaw plate closer to the fixed jaw plate, and the material passes through the two jaws. The squeezing and rolling between the plates realize multiple crushing.

When the movable jaw descends, the angle between the toggle plate and the movable jaw becomes smaller. The movable jaw plate leaves the fixed jaw plate under the action of the pull rod and the spring, and the crushed material passes through the discharge port in the lower jaw cavity freely under the action of gravity Unload.

When crushing high hardness and strong corrosive materials, C6X can accomplish the task very well. Its equipment structure, manufacturing technology and material selection determine the high strength of its body. Not only can it be used for coarse crushing of the hardest rocks and ore, but also can be continuously produced in the most demanding production environment on the ground and underground to ensure the maximum production efficiency of customers.

jaw crusher parts & jaw crusher spares | cms cepcor

jaw crusher parts & jaw crusher spares | cms cepcor

CMS Cepcor aftermarket jaw crusher replacement parts and wear parts are used by crusher operators worldwide and are often specified by many of the worlds most prestigious mining, quarrying, demolition and recycling operators together with several of the major original equipment manufacturers.

The CMS Cepcor product range of mechanical spare parts for jaw crushers is unrivalled. CMS Cepcor stock precision-machined UK manufactured eccentric shafts, labyrinths, spacers and end covers for most popular jaw crushers.

CMS Cepcor also stock toggle assembly components for single and double toggle crushers, including toggle beams, grooveblocks, wedgeblocks, toggle seats, toggle grooves, toggle pins and pitmans together with all the ancillary components.

CMS Cepcor has heavily invested in new technology in order to set the standard for aftermarket quality assurance, reverse engineering and metallurgy resulting in continual and rapid growth of our product range especially for those parts normally only associated with the OEMs.

CMS Cepcor has successfully supplied replacement jawstocks, flywheels, mainframes and pitmans for jaw crushers amongst other major components, where the original equipment manufacturer has deemed these components obsolete.

cone crusher parts | cone crusher spare parts | cms cepcor

cone crusher parts | cone crusher spare parts | cms cepcor

CMS Cepcor is the aftermarket cone crusher experts and the range of replacement cone crusher parts held in stock is unrivalled. CMS Cepcor replacement parts are specified by mining and quarrying operators worldwide.

The CMS Cepcor product range of mechanical spare parts for cone crushers is unrivalled. CMS Cepcor stocks precision-machined UK manufactured mainshafts, head centres, socket liners and eccentric bushings for popular cone crushers.

CMS Cepcor has heavily invested in new technology in order to set the standard for aftermarket quality assurance, reverse engineering and metallurgy, resulting in continual and rapid growth of our product range, especially for those parts normally only associated with the original equipment manufacturers (OEM).

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