DE3326626A1 - Conical crusher - Google Patents

Abstract

Conical crusher with sliding bearings between the outer surface of the eccentric device and the inner surface of a skirt extending downwards from the crusher head, and also roller bearings between the eccentric device and the middle shaft housing. Lubricating oil throughflow paths run through the middle shaft housing and radially outwards to an oil groove which completely surrounds the inner surface of the eccentric device and directs the lubricating oil into an oil space between the inner surface of the eccentric device and the outer face of the middle shaft housing and from the oil space into the roller bearing. A radial oil channel runs from the oil groove through the eccentric device to the surfaces of the sliding bearings and the opposing inner surface of the skirt, for the lubrication of both cooperating surfaces. The main thrust bearing has pillars with a smooth surface, which cooperates with a spherical sector having radial and self-intersecting circular lubricating oil grooves. The lubricating oil received from all the bearings flows directly through each of the bearings, without first flowing through another bearing. A counterweight is provided for the flywheel of the eccentric device. At least parts of the flywheel cylinder wall are tapered inward and upward, in order to induce a flow of lubricating oil against these walls.

Description

8326626

Cone crusher

The invention relates to cone crushers and, more particularly, to gyratory crushers.

The crushing effect of a cone crusher is based on the gyroscopic motion a moving breaking tool versus a stationary breaking tool and the interaction between these two tools and their effect on the material to be broken. A driven eccentric works with the moving one Breaking tool over bearing surfaces together so that the movable breaking tool executes the circular motion and a relative Rotary movement between the movable breaking tool and the eccentric is obtained, which is required during the breaking operation is. Crushers of the type disclosed in U.S. Patents 3,227,381 and 3,417,932 have only sliding bearings between the Using bearing surfaces consume too much energy to overcome the frictional forces that occur with plain bearings. On the other hand, crushers such as those disclosed in U.S. Patents 3,396,916 and 3,759,453 require only rolling bearings Use between the bearing surfaces, relatively complicated arrangements to achieve an adjustment of the distance Crushing tools and to clear the gap when non-crushable material, e.g. scrap iron, falls into the crushing chamber. if these crusher clearance adjustment arrangements are made on the upper crusher tool, they often require the Use of heavy coil springs or hydraulic Cylinders arranged outside around the circumference of the upper part of the crusher. The process of adjusting the springs or hydraulic piston has often resulted in operator injury and is laborious and cumbersome Protective devices made necessary. If the crusher spacing adjustment is carried out on a type of cone crusher with a vertically adjustable lower breaking tool can be made

should, results in the required relative linear movement between Storage areas extremely complicated and expensive storage arrangements.

Thorough and continuous lubrication of the many bearings and Storage space in the cone crusher is necessary for the crusher to function effectively and properly. Until now have known arrangements for feeding lubricating oil to the crusher bearings, e.g., U.S. Patents 3,417,932 and 3,692,249 however, the disadvantage that the lubricating oil is passed through the individual bearings one after the other before it is cooled and filtered; furthermore, known arrangements very often use existing spaces as oil channels, so that the too large or straight sufficient amount of oil is accepted that flows into a particular camp or through this camp instead of that the correct amount of lubricant is provided for bearing maintenance.

A main or ball bearing arrangement is used in many cone crushers for securing the support member for the movable Breaking tool or the mounting cone used to simplify the rotary motion of the movable breaking tool. Here, too, proper lubrication of the bearing surface is important and this is usually the case with existing cone crushers not guaranteed.

An essential part of gyratory crushers is a flywheel with a counterweight that has the influence of the rotating Eccentric adjusts. In the case of cone crushers, e.g. of the type according to U.S. Patents 2,359,987 and 2,814,450, the counterweight is thereby designed that lead is poured into a recess which is provided in the available space in the casting, which also has the gear for driving the eccentric. In some cases, this leads to a counterweight which, although the Adjusts the effects of the eccentric, but can generate other undesirable forces. In addition, such a

Design of the counterweight inaccuracies and complications on. Counterweights made in the manner of US Pat. No. 1,945,791 are trained and arranged, have themselves for the required Purpose also turned out to be not particularly suitable. Much more is required for proper operation required than putting a weight of the correct size in an existing space.

The object of the invention is to provide a cone crusher of the generic type Kind to improve, in particular an improved bearing arrangement, preferably sliding bearing arrangement, for the To provide eccentrics for a cone crusher, to provide improved ball bearings for a cone crusher, and an improved lubrication system for the bearings of the cone crusher including the bearings of the eccentric and for the main thrust bearing of the cone crusher create. It is also an object of the invention to provide an improved flywheel and an improved counterweight for a cone crusher as well as a flywheel working with a counterweight. Finally, the object of the invention is a method for the manufacture of an improved counterweight for a cone crusher.

This object is achieved according to the invention with the features of Characteristic of the main claim solved. Further refinements of the invention are the subject of the dependent claims.

With the invention, new and improved cone crushers are ahead Gyroscopic type, which have an eccentric which is rotatably arranged around a stationary shaft and which faces downwards standing apron of the support cone for the movable breaking tool cooperates to the movable breaking tool a Abandon gyroscopic motion, created. A combination of plain and roller bearings is proposed to move the eccentric in To attach crusher, and to obtain an interaction with the fastening cone for the lower breaking tool. Of further is the main thrust bearing assembly, which is also used for

Support of the fastening cone for the lower breaking tool is used, provided with interacting surfaces that a perfect and complete lubrication of the bearing facilitate; furthermore, a direct and effective path for the Lubricant flow to main thrust bearing assembly for all Creation of positions for setting the crusher gap; lubricant channels and flow paths continue to be formed, which ensure proper lubrication of the plain bearing and thus lubrication of all bearings, with the lubricant after filtering and cooling reaches the camp without first flowing through other camps. Eventually one becomes with Counterbalanced working flywheel proposed which is made so that it not only the rotational effect of the Eccentric offset, but is also designed so that the rotational forces are distributed so that undesirable torques around the center of gravity of the crusher to a minimum.

Below is the invention in connection with the drawing explained using an exemplary embodiment. It shows:

Fig. 1 is a vertical sectional view of a gyratory crusher without Spoke star, with parts drawn out of the rotation for better representation,

Fig. 2 is an enlarged view of part of Fig.l ,,

Fig. 3 is a further enlargement of part of Fig. 2, showing details of the lubricant flow paths and other components of the crusher,

Fig. 4 is a sectional view taken along the line IV-IV,

Figure 5 is a top plan view of the ball sector of the main thrust bearing assembly for the cone crusher according to Fig. 1, and

6 is a partial sectional view of the flywheel assembly for the cone crusher, the mold used for casting the counterweight in use during the counterweight molding process is shown.

For reasons of simplification, the subject matter of the invention is shown in Connection with a gyratory crusher without a spoke star described; the combination of plain bearings and roller bearings for the Eccentric and the movable breaking tool, the main thrust bearing, the Sqhmiermittelystetn for the bearings and the lubricant system for the roller bearing, as well as the counterweight working However, flywheels can be used for other types of cone crushers.

In Fig. 1, a gyratory crusher without a spoke star is shown at 20, its mechanism in a lower frame arrangement 22 and an upper frame assembly 24 provided with a material feed opening 26 is provided, is housed.

A power input driving device 30 has a Drive shaft 32 for connection via a corresponding device (e.g. a drive belt, a flywheel, a gear box) with a corresponding drive energy source, e.g. an electric motor or a diesel engine, as well as a drive pinion 34 for transmitting the input energy to a ring gear 36 of an eccentric arrangement 40.

The eccentric assembly 40 (Figs. 1 and 2) is rotatable about a rigidly attached center shaft housing 50 of the lower frame assembly 22 and is attached to the inner wall 56 of a downwardly extending skirt 60 of a lower breaking tool receiving Canoes or breaker head assembly 62 connected so that a Gyroscopic motion onto the crusher head assembly 62 and a lower one or movable crusher tool or jacket 64 received by the assembly. Such a one Circular motion results in breaking of the material (not shown

represents), which is fed through the opening 26 (Fig. 1) when the material passes through a crushing chamber 70, which is between the lower tool 64 and an upper breaking tool or a concave device 72 is formed which is received by the upper frame part 24. One that works with a counterweight Flywheel assembly 74 (FIGS. 1 and 2) is also received by eccentric assembly 40.

The crusher head assembly 62 is on top of its gyratory motion positioned upper limit of a main thrust bearing assembly 80, which is received by a center shaft 82, the is arranged to be movable vertically in a bore 84 (FIG. 2). The bore 84 is formed in the center shaft housing 50. A center shaft piston 86 is arranged at the lower end of the center shaft and operates in a hydraulic cylinder 88 which is attached to the is formed lower end of the center shaft housing 50, via corresponding hydraulic fluid 89 of an accumulator arrangement 90 (Fig. 1). An anti-rotation shaft 92 (Figures 1 and 2) connects the shaft 82 to an anti-rotation assembly 94, the is disposed within the crusher head assembly 62.

A lubrication assembly 100 (Fig. 1) supplies fresh and clean lubricant 102 from a reservoir 104 to all of the lubricant surfaces a cone crusher 20, such that the lubricant for a particular bearing is not previously passed through another bearing or another storage area streamed. Corresponding channels and flow paths are provided for this, as follows to be discribed.

In particular, the center shaft housing 50 is arranged in a stationary manner in the bore 110 (FIG. 1) of a cylinder support ring 112, is the integral part of the lower housing assembly 122. A cylindrical pad 114, which is enlarged in a lower Part 116 of the bore 84 is arranged and thus forms the hydraulic cylinder 88, is through an end cap 118 and corresponding screw components 120 and nuts 122 set.

A corresponding opening 130 is formed in the end cap 118, to receive a conduit 132 (Figures 1 and 2) of the accumulator assembly 90.

The center shaft piston 86 is flush with the bottom of the center shaft 82 attached by an appropriate device, e.g. Suitably dimensioned sealing rings 138, which are disposed in a groove 140 formed at the lower end of the piston 86 are through a piston end cap 142 positioned, which in turn is fixed by screw components 144. A lower socket 150 is at the junction arranged on the lower enlarged part 116 of the bore 84 hits the reduced part.

An upper center shaft bushing 160 (Figures 2 and 3) located at the upper outer end, bore 84, is therein Position determined by a locking plate 162 and a plurality of screw members 164. The upper bush 160 and the lower bushing 150 facilitate disposition and vertical movement of center shaft 82 in the bore below the hydraulic one Effect of the accumulator arrangement 90. Two keys 165 are formed in the locking plate 162 and cooperate correspondingly shaped slots 166 at the top of the center shaft 82 together so that they prevent rotation of the center shaft 82 in the bore 84 during vertical movement is allowed.

A lubricant flow path 180 (Figures 2, 3 and 4) is from the upper limit of the center shaft 82 is drilled downwards and intersects with one extending in the radial direction Channel 182. The outer end of the channel 182 is formed so that it is in connection with a vertically extending, in the Upper sleeve 160 formed slot 184 for all positions of the center shaft 82 in the bore 84 is. One in radial Directional channel 190, which is also in connection with the slot 184, is in the wall 192 of the Mittenwellonge-

housing 50 shaped so that it can be used in conjunction with a vertical, in the wall 192 trained flow \ i / eg 194 stands and up to lower end limit is enough.

The upper end of the lubricant flow path 180 is like this designed to direct fluid through an opening 200 (Fig. 2) centered in the base 201 of the main thrust bearing assembly 80 is arranged. The upper surface of the base 201 is smooth in surface, has a plate shape, and takes a thrust bearing ball sector 202 (Figures 2 and 5), which is also provided with a centrally arranged opening 204 is. A plurality of circular lubricant channels 206 (Fig. 5) and radially running lubricant channels 208 are formed in the surface of the thrust bearing ball sector 202. the Relationship between the circular lubricant channels 206 and the radial lubricant channels 208 is such that each point is on the smooth, dish-shaped upper surface of the socket 201 (Fig. 2) a lubricant channel during each cycle of movement of the thrust bearing ball sector 202 on the base 201 is exposed. Such a movement is known per se; the special relationship of the lubricant channels here However, the type described is not known from the prior art. The preferred version for the movements of the Sphere sector 202 is that the lubricant paths are offset no more than the distance that one point on the sphere sector 202 during one cycle of rotation of the eccentric device about the center shaft 82, and a corresponding gyro cycle of the crusher head 62 moves back with respect to the central shaft 82.

The gyroscopic effect of the crusher head 62 on the center shaft and the spherical sector 202 with respect to the base 201 results from the fact that the outer surface of the eccentric device 40 so is shaped to be concentric with an axis of rotation X (Fig. 2) which is at a predetermined angle "a" opposite the vertical axis Y of the center pillar 82 is arranged. The vertical axis Y is also the axis of rotation of the inner one

Surface of the eccentric device 40 around the center column housing 50 and the center pillar 82; it is hereinafter referred to as the axis of rotation the eccentric device 40 denotes. The axis X and the axis Y intersect at a point P, which is the The center of a sphere with the radius R is used to define the configuration of the plate-shaped surface of the spherical socket 201 and the configuration of the surface of the spherical sector 202 is used. While the eccentric device 40 in the vertical direction is fixed, the central column 82 and the plate-shaped one move Surface of the base 201 between a lower position (Fig. 2) and an upper position (not shown), depending on the adjustment of the lower breaking tool 84 with respect to the upper breaking tool 72. The radius R is chosen arbitrarily for this embodiment so that it corresponds to an adjustment in the Middle between the two extreme values for the lower raking tool 64 corresponds.

Thus, the distance of movement of the spherical sector 202 with respect to the base 201 for a single cycle of rotation Eccentric device 40 (or a gyration of the crusher head 62) viewed on a vertical surface plane, which intersects the sector 202 and the base 201, through subsequent ones Equation can be set:

D = 2 (R) (tan <a) where

D 5 is the distance that a point on the spherical sector 201 on the The surface of the base 201 is covered with each gyroscopic cycle of the cone 20,

R = the length of the radius line from an imaginary point P passing through the intersection of the axis of rotation X of the outer Surface of the eccentric device 40 and the axis of rotation Y of the eccentric device 40 itself is set, and

a = the angle at which the X axis and the Y axis cut.

The width of each lubricant channel 206, 208 is like this chosen to be wide enough to take into account the fact that point P serves as a midpoint between the upper and lower extremes for the crusher head 62 is selected, but not so wide that the bearing surface of the sphere sector 202 is reduced excessively.

An additional pair of vertical lubricant channels 220 (Figures 2, 3 and 4) and 222 (Figure 4) extends from the lower extreme limit of the wall 192 of the housing 50 upwards. Radial lubricant flow paths 224 (Figures 3 and 4) and (Fig. 4) connect the vertical flow paths 220, 222 with a groove 234 (Figs. 3 and 4) formed in an interior surface 236 of the eccentric arrangement 40 is formed and completely encloses it.

A radial channel 238 extends from the groove 234 across the wall 240 of the eccentric device 40 to an outer surface 242. In particular, the radial channel 238 intersects the outer surface 242 of the eccentric device 40 at a predetermined one Place "L" with respect to point "M" (Fig. 4) of maximum load on eccentric device 40. In this particular one In this case, the point "L" rushes the point "M" (in the direction of rotation of the eccentric device under load, i.e. counterclockwise in Fig. 4) by 120 ° ahead. The point "M" of maximum load for the described embodiment in turn rushes the part the eccentric device 40 with the largest wall dimension, point "T", by about 15 ° ahead. On the other hand, the place "L" rushes to the Part of the eccentric device 40 with the smallest wall dimension, point "S", by about 45 °. However, it is important to note that the point "M" of maximum load between 15 ° and 45 ° compared to the (leading) point "T" can occur, depending

according to the degree of fine or coarse nature of the end product from the crusher 20. The arrangement of the point L for the radial channel 238 is always about 120 ° with respect to the point M.

A surface 244 (FIGS. 3 and 4) of predetermined extent is provided on the outer surface 242 of the eccentric device 40 to facilitate the accumulation of lubricant 102 in the immediate vicinity of the location L. In this particular case, surface 244 spans an arc of approximately 20 °. As shown in FIG. 3, surface 244 is bounded at the top by an edge 246 and at the bottom by an edge 248, both of which result from the formation of surface 244 on outer surface 242. As the eccentric device 40 rotates, lubricating oil 102 reaching location L is wiped over the inner wall 46 of the skirt 60 of the breaker head 62 and onto the opposite outer surface of the eccentric device, as will be discussed below.

The outer surface 242 of the eccentric device 40 provides a sliding bearing 252 (Figs. 2 and 3) in relation to the Inner wall 56 of the skirt 60 of the crusher head 62. Corresponding stock material, e.g. Babbittmetal1 254, is in corresponding thickness on the outer surface 242 including the surface 244 is provided. Babbitt metal 254 covers however does not extend the entire vertical extent of surface 242, but extends from near the top to a predetermined location 256 above a lower end 257 of the eccentric device 40. This predetermined location hangs on the height of the eccentric device 40, the equally far extending areas of the wall 56 of the skirt 60 and the outer surface 242 and crucially on the vertical distance of the outer surface 242 from the skirt 60 is lifted when the center shaft 82 and breaker head 62 are raised to their highest position. The babbitt material 254 wears out when skirt 60 and eccentric device

40 work together. When a lower edge 260 of the skirt 60 is on is raised a point higher than the lower edge 256 of the babbit metal 254, the wear of the babbit metal becomes 254 unevenly and possibly resulting in premature bearing failure.

An upper roller bearing assembly 261 (Figures 2 and 3), which is in a upper bearing groove 262 formed at the upper end of the inner surface 236 of the eccentric device 40 is seated completely the center column housing 50 and is supported by the eccentric 40 surrounded. An upper bearing retainer 264 holds the upper bearing assembly 261 in place.

A lower roller bearing assembly 270 mounted in a lower, lower end of the inner surface 236 of the eccentric 40 formed bearing groove 272 has its seat, also completely surrounds the center column housing 50 and is of the eccentric 40 surrounded. The ring gear 36 sets the lower bearing 270 in position.

The flywheel assembly 74 (Figs. 2, 3 and 4) is circumferential arranged around the circumference of the eccentric 40 and fastened therewith in a corresponding manner. The flywheel assembly 74 includes components that keep dirt and dust away from the slide bearing 252 and roller bearing assemblies 261 and 270, and is designed so that there is a correspondingly dimensioned circular ring 276 (Figure 3) with a horizontally extending shoulder 278 of the eccentric 40, e.g., by screw members 280. A lower cylinder 282 is attached to the ring 276 and extends upward from ring 276. An upper annulus 284 is rigid at the top of the cylinder 282 arranged. Two grooves 286 formed in the lower surface of the upper ring 284 mate with two annular ones Ribs 290 together which are formed on the upper end of the vertical wall 292 of the lower housing assembly 22 so that they are therewith form a labyrinth-like dust seal when they are lubricated with

medium are filled. An upper cylinder 300 is attached to the upper ring 284 and extends upwardly from that ring. A or a plurality of upper grooves 301 are formed in close proximity to the upper end of the cylinder 300, each so that that sealing rings 302 are received, which in turn under their own spring action in engagement with an inner Surface 303 of a cylindrical ring 304 extending from the crusher head assembly 62; this arrangement results a seal against dust and dirt while at the same time vertical adjustment and movement of the crusher head 62 be made possible.

An inner surface 305 (Figs. 2 and 3) of the lower cylinder 282 is machined at a suitable angle so that lubricating oil 102 falling on surface 305 by centrifugal action of the rotating flywheel 74 is influenced so that it is downwardly and by a variety of relatively large Orifices 306 flows which are formed through the circular ring 276 and around it. A shield 307 (Figs. 2 and 4) is attached to an upper surface of the upper annulus 284 to prevent splash of lubricating oil 102 upward in the vicinity of the cylinder 382 is decreased as much as possible. The shield 307 extends only part of the way around around the circumference 282 (Fig. 4) of the cylinder and widens in the radial dimension as it approaches the ends; this happens so that a clear distance between the shield 307 and the outer surface of the skirt 60 is achieved when the crusher head 82 performs its gyratory motion.

The action of the sealing ring 302 on the inner surface 303 of the ring 304 to achieve an effective seal is achieved in that the upper cylinder 300 is arranged on the upper circular ring 284 so that the axis of rotation of the upper cylinder 300 of the axis of rotation "X" (Figs. 2 and 5) of the

outer surface 242 of the eccentric 40 corresponds, while at the same time the axis of rotation of the lower cylinder 282 of the The axis of rotation Y of the eccentric 40 corresponds.

A counterweight 308 (Figs. 2 and 6) is against the inner surface of the cylinders 282, 300 with a size and location trained that the inequality forces are offset that by the rotating eccentric 40 and all gyrating parts within the cone crusher 20, e.g. Breaker head 62, are introduced. When designing the counterweight 308, it is essential to distribute the weight so that that when rotated together with the flywheel 74 any tendency to generate further imbalance forces or -force pairs reduced to a minimum with respect to the forces generated by the parts executing a rotary motion will. This is accomplished by providing a configuration for counterweight 308 that has a center of gravity and creates a line perpendicular to axis Y, as close as possible to a line similar to that on which the The center of gravity of the parts performing the rotary motion would fall. Preferably the two focal points should be on one common line that runs perpendicular to the Y-axis.

The counterweight 308 is made by casting a dense material in place during manufacture of a subassembly formed, which the lower circular ring 276, the lower cylinder 282, the upper circular ring 284 and the upper cylinder 300 with and prior to installing the shield 307 or securing the subassembly to the shoulder 278 of the cam 40 will. A plurality of L-shaped lugs 309 (Figs. 4 and 6) are around the inner surfaces of the cylinders 282,300 in them Located area where the counterweight 308 is to be cast. One leg of each lug 309 is for example fixed by welding to the corresponding inner surface,

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while the other leg of lug 309 extends laterally therefrom and is embedded in the cast dense material, to facilitate the positioning of the counterweight 308.

A mold 310 (Fig. 6) is used to facilitate the casting and molding process for the counterweight 308 to facilitate. The casting mold 310 has a base plate 311 which is connected to the ring 276 via a A plurality of screws 312 (only one shown) are attached, and a mold plate assembly 313 that attaches to the base plate 311 is secured by a plurality of screws 314 (only one shown). Mounting pins (not shown) extend extend from the mold plate assembly 318 and / or the base plate 311 and cooperate with holes (not shown) that are formed in ring 276 to facilitate positioning of mold 310 in the subassembly of FIG. in the Thereafter, end pieces of the mold plate assembly 313 are applied to inner surfaces of the cylinders 282 and 300. if The mold 310 is so positioned there will be a pocket 315 in the space above the ring 276 and between the interior surfaces the cylinder 282, 300 and an inner surface 316 of the mold plate assembly 313 are formed. The inner surface is shaped so that the counterweight 308 has an exposed lower surface 317 which is substantially parallel to the inner surface 305 of the lower cylinder 282 is arranged so that lubricating oil 102 over openings 306 of the ring 276 below Centrifugal effect of the rotating flywheel 74 can flow away. The inner surface 316 is also formed so that counterweight 308 has an exposed surface 318 substantially parallel to axis Y and one exposed interface 319 which, when the flywheel 74 is assembled with the eccentric 40 to the extent that it extends against the apron 60 that the circular movement of the apron 60 is made possible, but - similar to the shield 307 is arranged close enough to prevent oil 102 from splashing over also keeps this position as low as possible.

Before pouring the dense material into the pocket 315 suitable packing material 320 (Fig. 6), e.g., asbestos-like material, placed in each opening 360 within pocket 350, to prevent the openings 306 from being filled with the dense material. The openings 306 in the immediate vicinity the position of the counterweight 308 are opposite in position to those on the other side of the ring 276 (as shown in Fig. 4), furthermore so that they extend past a lower outer location of the counterweight 380, so that oil 102 flows under counterweight 308 and through openings 306.

When the mold 310 has received its position and appropriate As openings 306 are filled with packing material 320, a suitable impervious material, e.g., lead, is placed in the pocket 315 poured. After the lead has hardened, the mold and the packing material 320 are removed, and the flywheel 74 with it the counterweight 380 can be assembled with the eccentric 40.

The size of the mold 310 and its dispositions with respect to the subassembly is chosen so that the resulting Counterweight 380 is given the correct weight and is positioned in the manner described above.

An alternative method for creating a counterweight is shown in Fig. 4 in which an inner wall 321 is attached to the ring 276 (Figs. 3 and 7) so that it extends from there to extends above and that they are a predetermined distance inwardly from the inner walls of the lower cylinder 282 and of the upper cylinder 300 is offset. The inner wall 321 is arranged essentially concentrically with the walls 282, 300, however, it is inclined outwardly with respect to the wall 282 where it rises upwards from the ring 276. The inclination is like this is chosen so that the flow of oil 102 through opening 306 is facilitated. The inner wall 321 is from the outer surface of the wall 240 of the

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Eccentric 40 offset by a distance which is sufficient to the a gyrating apron 60 of the crusher head assembly 62 to be included in between.

The end plates 322, 324 (Fig. 7) connect the outer ends of the Inner wall 321 with the walls 282, 300, thus a pocket 326 between the walls 282, 300, 321, 322, 324 and above the ring 276 (Fig. 7) is formed, which is open on its top. Lead 328 is poured into the pocket 326 and a counterweight therein 330 forms; the amount of lead and its positioning with respect to walls 321, 322 and 324 is chosen to be that of the eccentric 40 generated rotational forces are balanced and offset. The height of the counterweight 330 is dimensioned so that that the forces generated by it when the flywheel 74 rotates uniformly with respect to the center of gravity of the Crusher 20 are distributed.

The other surfaces of the flywheel according to FIG. 7 are designed as explained above in connection with FIG.

A plurality of drainage channels 332, 334, 336, 338 (Fig. 4) extends downwardly from the upper end extension of skirt 60 through the lower outer extension and provides a return flow path for the lubricant oil 102 through the drain holes 306 of the ring 276 into the lower housing 22 of the cone crusher 20.

A drain device 342 (FIGS. 1 and 2) provides an outlet for the oil 102 from the housing interior 22 to an oil return line 344 (Fig. 1) and then to the oil container 104. The container 104 is conveniently provided with filters (not shown) and a cooling device is provided to filter and cool the oil 102.

A pump 350 is connected to the container 104 to supply oil 102 to take from it and serve oil through a check valve 352, a flow meter 354, a pipe 356, a flow divider 358 and lube oil lines 360, 362 and 364 to pump. The line 360 is via corresponding couplings Lubricant channels 220, 222 connected, while the line via a corresponding coupling with the lubricant channel 194 connected is. The pump is connected via an electrical or other drive source and has control and monitoring devices on. The flow divider 358 divides the oil flow 102 so that one third of the oil in the line 362 and one-third of the oil 102 will flow into the line 360.

Before breaking rock or the like. Material with the crusher 20 and after the crusher 20 in any other way to break Once rock is prepared, it is critical that lubricating oil 102 passes through crusher 20 to all bearings, and others, too lubricating surfaces is pumped. The pump 350 is started and the oil 102 flows out of the container 104 through the Filter 352, flow meter 354, line 356, flow divider 358, and lube lines 360 and 362 pumped. The flow paths for the oil 102 are indicated by arrows in FIG 2 and 3 indicated.

Oil 102 flowing through line 362 becomes up the vertical lubricant passage 194 (FIG. 3), the radial passage 190 outward, through the slot 184 and through the radial channel 182, the vertical flow u / eg 180 up through the Port 200 is pumped into the main thrust bearing pedestal 201 and through port 204 into the main pressure ball sector 202 so that the Space around the main thrust bearing assembly 80 is filled with oil. The oil 102 fills the lubricant channels 206, 208 of the ball sector 202 and splashes out of its circumference, so that it is in the space around the upper part of the eccentric 40 and from there through the Drainage channels 332, 334, 336 and 338 of the skirt 60 falls. in the

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Following this, the oil 102 returns through the openings 306, the drain plug 342 and the return line 344 into the container 104 back.

The oil 102 flowing through the lines 360 becomes the Flow paths 220 and 222 are pumped upward and radial channels 224, 226 are pumped outward into circular groove 234. The end the oil flowing out of the groove 234 flows through a correspondingly dimensioned space between the inner wall 236 of the eccentric 40 and the outer wall of the center shaft housing 50 to accommodate the roller bearing assemblies 261, 270 to lubricate. The oil 102 flowing through the upper bearing assembly 261 passes through the drainage channels 360, 362, 364, 366 and then through openings 306; from the lower bearing assembly 270, oil 102 flows directly through the Openings 306 to the outside.

A portion of the oil 102 is pumped through radial channel 238 to surface 244 and / or onto the surfaces of the metal 254 and the opposite inner surface 56 of the skirt 60 is wiped. This oil 102 is then over the edge of the babbitt metal 254 up and down to the edge of the plank 256 is pumped by the interaction of the eccentric 40 and the skirt 60. The used oil 102 flows in through the openings 306 outside and from there back into the container 104.

As a result, oil 102 is not pumped into a second bearing or bearing surface after it has been used for lubrication a first bearing or bearing surface has been used; this oil 102, which is from a bearing or a Storage area is taken up is relatively cool and filtered.

The lower frame assembly, the upper frame assembly, the input drive, the accumulator and other components and Mechanisms that are required to operate the cone crusher

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to let work freely are similar to comparable arrangements, Mechanisms and components designed, constructed and operated in accordance with US Pat. No. 4,168,036.

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Claims (1)

Claims 1. Cone crusher, characterized by a) a frame (22, 24), b) a center shaft housing (50) extending from the frame (22, 24) is recorded, c) a bore (84) in a central part of the Mittenvi / ellengehäuses (50), d) a center shaft (82) in the bore (84) of the Center shaft housing (50) is arranged and in the axial Movable in the direction with respect to the center shaft housing (50), but in the direction of rotation with respect to the housing (50) is stationary, e) a piston arrangement (86) which cooperates with the central shaft (82) to move it in the axial direction, f) an eccentric device (40) rotatable about the center shaft housing (50) is arranged, g) a drive device (30, 32, 34, 36) with the eccentric device (40) to drive it in a predetermined driven direction is connected, h) a breaker head assembly (62) extending from the center shaft housing (50) is received and has an apron device (60), which with the eccentric device (40) cooperates so that when the eccentric device is driven by the drive device (30, 36) the crusher head device (62) in gyration and with respect to the eccentric device eccentric device (40) and the apron device (60) is arranged, and j) a roller bearing device (261, 270) between interacting surfaces of the eccentric device (40) and the center shaft housing (50) arranged is. 2. Cone crusher according to claim 1, characterized in that the sliding bearing device (252) on an outer surface of the ■ eccentric device (40) is formed. 3. Cone crusher according to claim 2, characterized in that the sliding bearing device (252) consists of Babbitt metal (254). 4. Cone crusher according to claim 2, characterized in that the Slide bearing device (252) extends from a first position near a first outer end of the eccentric device (40) to a second position, which in a predetermined distance from a to / eiten outer end of the Eccentric device (40) is arranged at a distance. 5. Cone crusher according to claim 4, characterized in that the crusher head device (62) and the apron device (60) are arranged axially movable with respect to the eccentric device (40), and that the predetermined distance is selected is that for maximum axial movement of the skirt device (60) with respect to the eccentric device (40) in a direction in which a first outer end of the apron device (60) extends from the second outer end of the Eccentric device (40) moved away, the second position of the slide bearing device (252) between the eccentric device (40) and the apron device (60) remains. 6. Cone crusher according to claim 2, characterized in that the sliding bearing device (252) has an oil point on the outer surface (242) of the eccentric device (40), and that oil flow channels are provided that direct the lubricating oil to the oil point. 7. cone crusher according to claim 6, characterized in that the oil point at a predetermined, curved distance from one imaginary radial line is arranged, which is the point maximum eccentricity of the outer surface of the eccentric device and intersects the center of rotation of the eccentric device. 8. cone crusher according to claim 7, characterized in that the predetermined curved distance of the oil point of the imaginary radial line in the predetermined driven direction of rotation of the eccentric device leads. 9. cone crusher according to claim 8, characterized in that the predetermined curved distance of the oil point between 135 and 165 radial degrees to the imaginary radial line * 10 «cone crusher according to claim 6, characterized in that the Oil point is dimensioned around the outer surface of the eccentric device that it is about 2G degrees in arc distance overstretched. 11. Cone crusher according to claim 10, characterized in that the oil point extends in the axial direction along the outer surface of the eccentric device and in the immediate vicinity the axial outer ends of the sliding bearing device ends. 12. Cone crusher according to claim 6, characterized in that the Oil flow paths arcuate with respect to the oil point are centered. 13. Cone crusher according to claim 12, characterized in that the oil flow through a first radial channel, which is through the eccentric device (40) from the oil point on the outer surface of the eccentric device to an oil groove on the Inside of the eccentric device and first oil flow paths extending into the center shaft housing, and second oil flow paths extending through the central extend the shaft housing to the oil introduction device, wherein the first and second oil passage devices are connected to each other. 14. Cone crusher according to claim 13, characterized in that the slide bearing device (252) is arranged at a distance from the skirt device (60), and that the oil point so is dimensioned that it extends into the outer surface (242) of the Eccentric device (40) extends in such a way that when the eccentric device is in the predetermined drive direction is driven and with the apron device (60) cooperates, at this oil point collected oil on the sliding bearing device and the interacting surface the apron device is stripped. 15. Cone crusher according to claim 14, characterized in that the interaction between the eccentric device (40) and the skirt device (60) oil via the sliding bearing device (252) and the skirt device (60) towards the first and second outer ends of the eccentric device (40) promotes. 16. Cone crusher according to claim 15, characterized in that oil is circulated from a point between the eccentric device and the apron device without it being in Another storage device is directed, and that a line device is provided in which the oil in a Oil reservoir is returned without it being another Stock is supplied. 17. Cone crusher according to claim 16, characterized in that a third oil flow device is provided which extends through the apron device for oil from a Place between the eccentric device and the apron device flows at the first outer end, is directed into the oil container. 18. Cone crusher according to claim 1, characterized in that the Roller bearing device, a first roller bearing which is in the immediate vicinity of a first outer end of the eccentric device is arranged, as well as a second roller bearing, which is in the immediate vicinity of a second outer end of the Eccentric device is arranged having. 19. Cone crusher according to claim 18, characterized in that the first and second roller bearings both form the center shaft housing completely enclose and both are enclosed by the eccentric device. 20 «cone crusher according to claim 19, characterized in that the oil grooving device in the inner surface of the eccentric device is formed and connects to a fourth oil flow path established in the center shaft housing is designed to receive lubricating oil therefrom and direct this lubricating oil directly into the roller bearing device without first having the oil in another bearing device is judged. 21. Cone crusher according to claim 20, characterized in that the oil groove is further in communication with a space between the inner surface of the eccentric device and a Outer surface of the center shaft housing is in communication and which is just dimensioned so that the flow of the Lubricant oil directly from the oil groove into the first roller bearing device and directly from the oil groove into the second Roller bearing device is made possible. 22 »cone crusher according to claim 21, characterized in that ül from the first roller bearing device into lubricant channels formed by the skirt device and then into the Oil reservoir flows, and that oil flows into the oil reservoir from the second roller bearing device. 23. Cone crusher according to claim 1, characterized in that a) a thrust bearing device is arranged between the crusher head and the center shaft in order to secure the To facilitate the crusher head and a relative movement between the crusher head and the center shaft, b) that the pressure bearing device has a spherical sector with oil grooves in a predetermined surface of the same are trained, c) that the pressure bearing device further comprises a base with a smooth surface, which with the predetermined Surface of the spherical sector cooperates, and d) that the Ülnuten from each other by a predetermined distance are offset such that each point on the surface of the pedestal defines the oil grooves on each cycle of the cone crusher is exposed. 24. Cone crusher according to claim 23, characterized in that the oil grooves a plurality of circular oil grooves and one Variety of radial oil grooves intersecting with circular grooves Have oil grooves, and that the predetermined distance between the oil grooves is determined according to the equation: D = 2 (R) (tan. <A) where
D = the distance that a point on the spherical sector on the surface of the base for each gyro cycle of the Cone crusher,
R = the length of the radius line from an imaginary point P passing through the intersection of an axis of rotation X of a outer surface of the eccentric device is determined, <a = the angle at which the axis X and the axis Y each other meet. .Cone crusher according to claim 23, characterized in that the Glkanäle in the center shaft are designed so that they are at one end with the oil grooves and at the other end with the Communicate oil flow path of the center shaft housing. 26. Cone crusher according to claim 25, characterized in that the oil flow device in the center shaft housing has an oil flow path which extends from an oil inlet port ir. the center shaft housing to an oil outlet opening in an inner surface of the center shaft housing is arranged, - which defines the bore, extends, and that a sleeve device is arranged in the bore and has a longitudinal slot extending through the sleeve device, and the outlet opening from the center shaft housing with the Connects oil flow device in the center shaft. 27. Cone crusher according to claim 26, characterized in that the longitudinal slot is dimensioned and positioned so that the outlet opening and the oil flow paths are in communication with each other at all axial positions of the center shaft stand. 28. Cone crusher according to claim 1, characterized in that a) the eccentric device (40) has a flywheel arrangement (74) which, together with the eccentric device (40) is rotatable, b) a counterweight device from the flywheel device (74) is received so that it is arranged at a distance from and concentrically to the eccentric device (40), and c) the counterweight device (308) so dimensioned and is positioned to extend from a location near the first outer end of the eccentric device (40) extends to a location near the second outer end of the eccentric device (40). 29. Cone crusher according to claim 28, characterized in that the flywheel has a circular wall which the The outer surface of the eccentric device surrounds and is spaced from it that the counterweight device is formed in that a counterweight wall between the circular wall and the outer surface of the eccentric device is formed over a predetermined circular distance to define a counterweight pocket which is open along a plane which intersects the counterweight wall and the circular wall, and that the counterweight pocket with relatively dense material is filled to form a counterweight. 30. Cone crusher according to claim 29, characterized in that the dense material is lead. 31. Cone crusher according to claim 29, characterized in that the counterweight wall is substantially circular Part which is substantially concentric with the circular wall, and end parts which the circular part with the circular wall connect, has. 32. Cone crusher according to claim 31, characterized in that the counterweight wall diverges upwardly and outwardly from at least a portion of the circular wall at a predetermined angle. 33. Cone crusher according to claim 32, characterized in that the predetermined angle is chosen so that the oil flow down and away from the counterbalance device during the Rotation of the same with the eccentric device is directed. 34. Cone crusher according to claim 33, characterized in that additional parts of the circular wall are designed with the predetermined angle. 35. Cone crusher with a stationary housing and a driven one Eccentric device which is rotatably arranged around the stationary housing and cooperates with a crusher head in such a way that that when the eccentric device is driven, the crusher head has a gyratory movement and a rotational movement about the eccentric device, characterized in that the bearing arrangement for the cone crusher having: ·;' a) a slide bearing device (252) which is arranged between the eccentric device (40) and the crusher head (62) is to facilitate movement of the one relative to the other device, and b) a roller bearing device (261, 270) between the eccentric device (40) and the stationary housing (50) is arranged to facilitate rotation of the eccentric device. 36. Cone crusher according to claim 35, characterized in that the slide bearing device moves the crusher head axially as well as in the direction of rotation with respect to the Eccentric device facilitated. 37. Cone crusher according to claim 36, characterized in that the sliding bearing is formed on an outside of the eccentric device. 38.Cone crusher according to claim 37, characterized in that the sliding bearing device is made of Babbitt metal. 39. Cone crusher according to claim 37, characterized in that the slide bearing device moves from a first point in the immediate vicinity of a first outer end of the eccentric device extends to a second location a predetermined distance from a second outer end of the Eccentric device is offset. yi " 40. Cone crusher according to claim 39, characterized in that the crusher head has a skirt and the crusher head like also the skirt are arranged axially movable with respect to the eccentric device, and that the predetermined distance is chosen so that for the maximum axial movement of the skirt with respect to the eccentric device in a Direction in which a first outer end of the apron is from that second outer end of the eccentric device is moved away, the second point of the slide bearing device still lies between the eccentric device and the skirt. 41. Cone crusher according to claim 37, characterized in that the sliding bearing device has an oil point on an outer surface of the eccentric device, and that the oil flow paths are designed for the passage of lubricating oil to the oil point. 42. Cone crusher according to claim 41, characterized in that the oil point is a predetermined, curved distance from an imaginary radial line that defines the point maximum eccentricity of the outer surface of the eccentric device and the center of rotation of the eccentric device cuts. 43. Cone crusher according to claim 42, characterized in that the predetermined arc distance of the oil point of the imaginary radial line in the predetermined direction of rotation of the Eccentric device leads. 44. Cone crusher according to claim 43, characterized in that the predetermined arc distance of the oil point between 135 and 165 radial degrees from the imaginary radial line lies. 45. Cone crusher according to claim 41, characterized in that the oil point is dimensioned around the outer surface of the eccentric device that it is about 20 degrees in an arc distance overstretched. 46. Cone crusher according to claim 45, characterized in that the oil point extends in the axial direction along the outer surface of the eccentric device and in the immediate vicinity the axial outer ends of the sliding bearing device ends. 47.Cone crusher according to claim 41, characterized in "that the oil flow path is arcuately centered with respect to the oil collection point. 48.Cone crusher according to claim 47, characterized in that the oil flow path is radial, extending from the oil point the outside of the eccentric device to the oil groove on an inside of the eccentric device through the eccentric device extends, and that the first oil flow path extending in the housing extends with the second oil flow path, the through the housing to an oil inlet device extends, is connected. 49. Cone crusher according to claim 48, characterized in that the sliding bearing device is arranged offset from the skirt, and that the oil point is dimensioned so that it is extends into the outer surface of the eccentric device so that when the eccentric device is in a predetermined Direction rotates and cooperates with the skirt assembly, oil accumulated at this oil point over the Slide bearing device and the interacting surface of the apron device is wiped. 50. Cone crusher according to claim 49, characterized in that the interaction between the eccentric device and the apron device forcing oil via the sliding bearing device device and the apron device in directions against the first and to / eiten outer ends of the eccentric device leads. 51. Cone crusher according to claim 50, characterized in that oil flows through between the eccentric device and the apron device without it being over another bearing device is performed, and that a line arrangement is provided which returns the oil to an oil container without the oil is fed to another storage device. 52. Cone crusher according to claim 51, characterized in that a third Öldurchflußu / eg is provided, which is through the The skirt assembly extends between the eccentric assembly and the skirt assembly on the first outer end to direct oil flowing into the oil reservoir. 53. Cone crusher according to claim 35, characterized in that the roller bearing device comprises a first roller bearing arranged in the vicinity of a first outer end of the eccentric device and a second roller bearing disposed in the vicinity of a second outer end of the eccentric device. 54. Cone crusher according to claim 53, characterized in that the first roller bearing and the second roller bearing completely enclose the stationary housing. 55. Cone crusher according to claim 54, characterized in that the oil grooves are formed in the inner surface of the eccentric device and are in communication with an oil flow path stand, which is formed in the stationary housing to receive lubricating oil therefrom and the lubricating oil directly the To supply rolling bearing device without the oil is first fed into another storage device. 56. Cone crusher according to claim 55, characterized in that the oil grooves communicate with a spacer between the inner surface of the eccentric device and an outer surface of the stationary housing is provided, and which is sufficiently large in size, that lubricant oil directly from the oil grooves in the first roller bearing and directly from the oil grooves in the second roller bearing can flow. 57. Cone crusher according to claim 56, characterized in that Oil from the first roller bearing flows into lubricant channels that pass through the skirt assembly and then to the oil are formed, and that oil flows from the second roller bearing into the oil container. 58. Cone crusher with a stationary housing and a driven one Eccentric device which is rotatably arranged around the stationary housing and cooperates with a crusher head, which is received by a central shaft which is axially movable with respect to the stationary housing, wherein at driven eccentric device of the crusher head a gyratory movement and a rotational movement around the eccentric device executes, characterized in that a) a thrust bearing device is arranged between the crusher head and the center shaft in order to secure the To simplify the crusher head and a relative movement between the crusher head and the center shaft, b) that the thrust bearing device has a spherical sector formed in a predetermined surface of the sector Has oil grooves, c) that the pressure bearing device further comprises a base with a relatively smooth surface, which with the cooperates predetermined surface of the spherical sector, and d) that the oil grooves are spaced from one another in such a way that each point on the surface of the base defines the oil grooves exposed at every cycle of the cone crusher. 59. Cone crusher according to claim 58, characterized in that the oil grooves have a plurality of circular oil grooves and a plurality of radial ones intersecting the circular oil grooves Have oil grooves, and that the predetermined distance between the oil grooves is determined according to the following equation: D = 2 (R) (tan. <A) where D = the distance that a point on the spherical sector on the surface of the base in each gyro cycle of the Cone crusher wanders, R = the length of the radius line from an imaginary point P through the intersection of an axis of rotation X of a outer surface of the eccentric device is determined, <a = the angle at which the X-axis and the Y-axis cut. 60. Cone crusher according to claim 58, characterized in that Oil channels are formed in the center shaft, which at one end with the oil grooves and at the other end with in the center shaft housing trained oil flow paths in communication. 61. Cone crusher according to claim 60, characterized in that the oil flow paths in the center shaft housing have flow paths leading from an oil inlet port in the center shaft housing extend to an oil outlet opening arranged in an inner surface of the center shaft housing, and that a sleeve device arranged in the center shaft housing is, which has an elongated slot extending through the sleeve device extends and the outlet opening of the center shaft housing to the oil flow paths in the Mittenwelle connects. 62. Cone crusher according to claim 61, characterized in that the elongated slot is dimensioned and positioned so that the exit port and the oil flow paths for all axial positions of the center shaft are in communication with each other. 63. Cone crusher with a stationary housing and a driven one Eccentric device which is rotatably arranged around the stationary housing and which has a breaker head as cooperates that when the eccentric device is driven, the crusher head and a circular motion performs a rotational movement about the eccentric device, characterized in that a) the eccentric device has a flywheel device rotatable with it having, b) a counterweight device is provided which is received by the flywheel device, such that it is arranged at a distance from the eccentric device and concentrically therewith, c) the counterweight device is dimensioned and positioned so that it is from a location in the immediate Proximity of a first outer end of the eccentric device to a location in close proximity to a second outer end of the eccentric device extends. 64. Cone crusher according to claim 63, characterized in that the flywheel assembly has a circular wall surrounding an outer surface of the eccentric device at a distance, and that the counterweight device is formed by attaching a counterweight wall between the circular wall and the outer one Surface of the eccentric device is formed over a predetermined circular distance to provide a counterweight set pocket that is open along a plane which intersects the counterweight wall and the circular wall, and that the counterweight pocket is filled with relatively dense material to form a counterweight. 65 ♦ Cone crusher according to claim 64, characterized in that the dense material is lead. 66. Cone crusher according to claim 64, characterized in that the counterweight wall has a substantially circular portion which is substantially concentric with the circular wall and that end parts are provided which connect the circular part to the circular wall. 67. Cone crusher according to claim 66, characterized in that the circular part upwardly and outwardly of at least a part of the circular wall and in a predetermined one Angle diverges. 68. Cone crusher according to claim 67, characterized in that the predetermined angle is chosen so that the oil flow after is achieved below and away from the counterweight device while rotating with the eccentric device. 69. Cone crusher according to claim 68, characterized in that additional parts of the circular wall are formed at the predetermined angle. 70. Cone crusher according to one of claims 1 to 69, with a Lubrication system, characterized by a) a frame (22, 24), b) an eccentric device (40) which is rotatable from the frame about a predetermined axis and with respect to the frame is recorded c) a drive device (30-36) for driving the eccentric device (40), d) a breaker device (20) which is received by the frame and interacts with the eccentric device in such a way that that they depend on the eccentric device and the rotation of which is set in rotary motion and gyratory motion, e) a first bearing device (252) which is arranged between the eccentric device (40) and the frame (22, 24), f) a second storage device (261, 270) between Eccentric device (40) and breaking device (20) are arranged, g) a third storage device between the crushing device and the frame, and h) an oil system with i) an oil container, ii) a first oil flow device through which oil from the Oil container is led into the first storage device, iii) a second oil flow device, the oil from the oil container leads into the second storage device, iv) a third oil flow device, the oil from the Oil container leads into the third storage device, v) the first oil flow device, the second oil flow device and the third oil flow device take oil from the oil container before this oil enters one of the Warehouse is kept,
vi) an oil return flow device which feeds oil after passing through the first, second and third Storage device leads back into the oil tank, vii) the oil return passage device is separate and independent of the first, the second and the third oil passage device » .Cone crusher according to claim 70, characterized in that the frame has a piston assembly, which with the Breaking device cooperates so that the position of the Crusher device selectively set u / ird, and that the third bearing device is arranged between the piston device and the crusher device. 72. Cone crusher according to claim 70, characterized in that the oil system between the oil tank and the first one, the second and third oil passage devices arranged is to divide the amount of oil flowing in from the oil sump in a predetermined manner. 73. Cone crusher according to claim 72, characterized in that the oil flow divider supplies essentially a third of the oil the third oil flow device and about two thirds of the oil into the first and second oil flow devices directs. 74. Cone crusher according to claim 72, characterized in that the third oil flow device is separate from the oil flow divider through a wall of the frame, through the piston assembly, and then to the third bearing device extends. 75. Cone crusher according to claim 72, characterized in that the first oil flow device is separate from the oil flow divider through a wall of the frame, through a circumferential, in an inner surface of the Eccentric formed groove and in the circumferential direction a certain distance around and through a space between the frame and the eccentric device. 76. Cone crusher according to claim 75, characterized in that the third oil flow device is separate from the oil passage device through the piston assembly over at least part of the circumferential oil groove and through a wall of the eccentric device extends therethrough. 77. Process for the formation of a counterweight flywheel, the is operated with the eccentric device of a cone crusher according to claims 1-76, characterized in that a) a flywheel subset is created, which is attached with the eccentric device of a cone crusher, b) that a mold is made with respect to the flywheel subset prior to securing the flywheel assembly is positioned with the eccentric device of a cone crusher, such that the flywheel assembly and the mold in this position fix a counterweight pocket open at the top, c) that relatively dense material in the counterweight pocket is poured, d) that the relatively dense material is cured, and e) that the mold is removed. 78.Verfahren according to claim 77, characterized in that the Flywheel part set a fastening device for the Has counterweight, which extends into the counterweight pocket and within the cast dense Materi.ales at the hardening of which is included. 79.Verfahren according to claim 78, characterized in that the Mold receives a casting surface of predetermined configuration within the counterweight pocket. 80.Verfahren according to claim 79, characterized in that with the predetermined configuration creates an outer surface on at least a portion of the counterweight, which results in a downward flow of the flowing medium which is in contact with the outer surface upon rotation of the Counterweight is coming. 81.Verfahren according to claim 78, characterized in that the Flywheel part set with additional exposed surfaces provided u / ird, which are designed so that they are the outer Surface of the counterweight correspond.