US3666188A

US3666188A - Gyratory crusher

Info

Publication number: US3666188A
Application number: US851283A
Authority: US
Inventors: Arthur W Lippmann
Original assignee: Hewitt Robins Inc
Current assignee: HEWITT-ROBINS CORP; Hewitt Robins Inc
Priority date: 1969-08-19
Filing date: 1969-08-19
Publication date: 1972-05-30
Anticipated expiration: 1989-05-30

Abstract

The present application discloses a gyratory crusher which is actuated by a fluid motor and, more particularly, by a fluid motor having a plurality of sequentially actuated pistons which are positioned radially about the central shaft supporting the movable crushing member and which operate directly on the shaft in order to create the necessary gyratory motion. In addition, a fluid bearing is provided intermediate the movable crushing member and the supporting shaft and which bearing is specifically designed to adjust the vertical position of the movable crushing member within the crushing chamber. The operating mechanism for the movable crushing member is also designed to provide automatic relief in the event uncrushable material in the crushing chamber might create excessive or damaging stresses.

Description

O United States Patent 1151 3,666,l 88 Lippmann 1 May 30, 1972 [54] GYRATORY CRUSHER l,l37,928 10/1962 Germany ...24l/207 l,l57,459 l 1/1963 Germany ..24 1/207 [72] Inventor: Arthur W. Llppmann, Poway. Calif.

[73] Assignee: Hewltt-Roblns Incorporated, Stamford, Primary Emmi"e' Thern Condo Conn. Attorney-John D. Boos 221 Filed: Aug. 19, 1969 ABSTRACT [2]] Appl. No.: 851,283 The present application discloses a gyratory crusher which is actuated by a fluid motor and, more particularly, by a fluid [52] US. Cl ..24l/2l3 motor having a plurality of sequentially actuated Pistons 51 Int CL which are positioned radially about the central shaft support- [58] Field Search ..241/123, 207, 21 1, 212, 213 s the movable crushing member and which Operaw directly on the shaft in order to create the necessary gyratory motion. [56] References cit d In addition, a fluid bearing is provided intermediate the movable crushing member and the supporting shah and which bear- UNITED STATES PATENTS ing is specifically designed to adjust the vertical position of the 850 491 4/1907 Redding 241/207 X movable crushing member within the crushing chamber. The 2 O79'S82 5/1937 Traylor "2 1 X operating mechanism for the movable crushing member is also 2:291:910 8/1942 Malone.. ..91/39 X esigned to provide automatic relief in the event uncrushable 2,908,448 /1959 MacLeodm 241/213 X material in the crushing chamber might create excessive or 3,315,901 4/[967 Pollitz ..241/211 damagmg 3,372,88l 3/l968 Winter ..24l/208 FOREIGN PATENTS OR APPLICATIONS 2 Claims, 8 Drawing Figures 859,318 6/1940 France ..24l/2l$ PATENTEUHM 30 I972 SHEET 3 OF 5 IFJVII) (T m Ar/hur W L/ppmann GYRA'IORY CRUSHER BACKGROUND OF THE INVENTION Gyratory crushers have long been used for pulverizing materials such as rock, ore, coal and similar substances. These crushers have heretofore generally employed rotary drive means to actuate the movable crushing member within the crushing chamber. This type of design has, in turn, required the use of gearing through which the drive means can transmit rotation to the shaft supporting the movable crushing member. In particular, this gearing has generally included a ring gear coupled to the lower end of an eccentric shaft and a pinion gear which is driven by the rotary drive means and which drives the ring gear. This type of drive arrangement has frequently created maintenance and wear problems and adds considerably to the overall height of the crusher. This additional height can create a particular design problem when such crushers are to be incorporated on portable crushing plants adapted for highway travel since state highway regulations frequently set height limits for such vehicles. In order to reduce the headroom requirements for this type of crusher, the gearing can be reduced in size; however, this in turn generally requires a reduction in many of the other crusher components so that the ultimate crushing capacity is limited or reduced. Thus, there is a definite need for a gyratory crusher design which eliminates the use of the relatively complex rotary drive arrangement and which also provides a reduction in the overall height of the crusher without reducing the crusher capacity.

Other problems still encountered in designing gyratory crushers have included (1) reducing the wear normally encountered by many of the crusher components and particularly the bearing rotatably supporting the movable crushing member, (2) providing a simple adjustment means for varying the gyratory displacement of the movable crushing member, (3) providing a simple means for readily adjusting or setting the height of the movable crushing member within the crushing chamber and (4) providing a simple relief mechanism which will automatically release uncrushable material from the crushing chamber when such material threatens to damage or overstress the machine. Prior art gyratory crusher designs have proposed numerous mechanical solutions to these problems; however, there still remains a need for simpler, more efficient solution to each of these basic design problems.

SUMMARY OF THE INVENTION In carrying out the present invention, a gyratory crusher is provided having two relatively movable crushing members, one of which is stationarily supported and the other ofwhich is adapted to be driven by a fluid motor which includes a plurality of sequentially actuated hydraulic pistons which act directly upon the shaft supporting the movable crushing member. The use of such a fluid motor has l) entirely eliminated the use of the conventional rotary drive arrangement, (2) enabled such crushers to be designed with an overall reduction in height, 3) eliminated the need for an eccentric drive shaft which was heretofore generally employed in generating the gyratory motion, and (4) has permitted the gyratory motion of the movable crusher member to be readily changed by simply varying the fluid flow to the fluid motor.

A unique fluid support bearing has also been provided which is interposed between the movable crushing member and the central shaft supporting this member and the bearing chamber is coupled to a source ofsupporting fluid, such as oil, which can be selectively interjected or withdrawn from the bearing chamber so as to thereby provide a simple hydraulic means for adjusting the position of the movable crushing member within the crushing chamber. In addition, an automatic pressure relief means is provided in the form of a gasfilled cushion chamber which is located within the shaft supporting the movable crushing member. This cushion chamber permits the rapid reduction of fluid bearing pressure in the event uncrushable material in the crushing chamber creates forces above a predetermined limit and this reduction in fluid bearing pressure permits the movable crushing member to move relative the stationary crushing member so as to thereby safely release the uncrushable material.

Accordingly, one object of the present invention is to provide an improved gyratory crusher which is simple and durable in construction and highly efficient in its operation.

Yet another object of the present invention is to provide an improved actuating drive and driving control system for a gyratory crusher.

Another object of the present invention is to provide an improved crusher with a simple reliable arrangement for adjusting or setting the spacing between the crushing members so as to facilitate an adjustment of the fineness or coarseness of the crushed product.

A further object of the present invention is to provide an improved gyratory crusher with a simple and reliable control mechanism for varying the gyratory displacement of the movable crushing member.

A yet further object of the present invention is to provide an improved crusher with an automatic release means which permits the movable crushing member to move relative the fixed crushing member and thereby release any uncrushable material which may become jammed between the two members before excessive or damaging stresses are created in the crusher.

BRIEF DESCRIPTION OF THE DRAWINGS Other objects, advantages and novel features of the present invention will become apparent from the following detailed description of the invention when considered in conjunction with the drawings wherein:

FIG. I is a vertical section view through a gyratory crusher, showing an embodiment of the present invention utilizing a fluid support or the relatively movable member and having both a fluid surge chamber and a gas-filled cushion chamber internally of the crusher and which crusher is driven by a fluid motor;

FIG. 2 is an enlarged vertical sectional view of the improved fluid motor structure shown in FIG. 1, taken along line 22 of FIG. 3-,

FIG. 3 is a sectional view taken along lines 3-3 of FIGS. 1 and 2, illustrating details ofthe driving fluid motor structure;

FIG. 4 is an enlarged vertical sectional view illustrating details of another embodiment of a fluid-driving motor adaptable for driving the crushing members shown in FIG. 1;

FIG. 5 is a sectional view taken along lines 5-5 of FIG. 4 and illustrating details of the fluid driving motor;

FIG. 6 is an enlarged vertical sectional view of another embodiment of the fluid-driving motor and its associated valve mechanism, which may be used for actuating the crushing members shown in FIG. 1;

FIG. 7 is a sectional view taken along line 7-7 of FIG. 6 showing details of the fluid-driving motor;

FIG. 8 schematically illustrates an entire system for operating a crusher ofthe type shown in FIGS. 1-7.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to the drawings, an improved gyratory crusher is illustrated in FIGS. 1, 2, and 3 which comprises a pair of relatively movable crushing members. One of these crushing members is fixedly mounted and includes a conventional convex mantle I formed of any suitable material, such as a case hardened steel. This mantle l is shown as formed with an annular supporting flange 2 which is secured to a main frame ring 3 by a plurality of through bolts 4. As shown in FIG. 1, the mantle l is formed with an outer frusto-conical surface arranged in snug engagement with a complementary interior frusto-conical surface on the main frame ring 3. The frustoconical surfaces on the mantle l and the frame ring 3 are formed so that when the through bolts 4 are drawn up tightly these two surfaces wedge together, and their relative size is such that a slight clearance, as shown in FIG. 1, preferably remains between the surface of the flange 2 on the mantle and the adjacent surface of the frame ring 3. The main frame ring 3 is further rigidly supported by a main mounting ring frame 5 to which it is suitably secured as by bolts 6. This mounting ring frame 5 forms the main rigid support for the crusher and is adapted to be mounted and secured wherever it is desired that the crusher be located.

The other relatively movable crushing member of the gymtory crusher comprises a mantle 7 formed with an internal frusto-conical surface which is mounted upon a complementary frusto-conical external surface of a mounting cone 8 on which it is rigidly wedgingly secured in any suitable manner as by a clamping nut 9 which threadedly engages an axially extending collar 10 on the end of the mounting cone 8. The mantle 7 is formed with an outer slightly concave surface and is arranged within stationary crushing member mantle l. The space between mantles l and 7 forms a crushing chamber in which material is crushed by the gyratory motion of the movable crushing member.

In order to support the relatively movable crushing member mantle 7 in position and to provide a mounting which enables vertical adjustment of this mantle relative to the stationary crushing member mantle l, a central shaft 11 is provided which extends through an upper bore in the mounting cone collar 10 and into a thrust bearing housing 12. This bearing housing is rigidly supported by a spider comprising a plurality of spaced legs 13 which integrally secure the bearing housing 12 to the main frame ring 3. The thrust hearing which supports the central shaft 11 is of the ball and socket type in which the socket is formed as a bearing seat l4 mounted in the bearing housing 12. The ball part of the thrust bearing comprises a substantially hemispherical bearing member with a spherical surface complementary to the inner surface of the bearing seat 14 and supported thereby. The bearing 15 is shown as having been cast around the end of the shaft 11, with an inwardly extending flange l6 closely engaging the sides of a groove in the shaft 11 to provide for a secure transmittal of thrust from the shaft to the bearing. It is further secured in position by an end plate 17 which extends over the outer end of both the bearing 15 and the shaft I1 and is rigidly secured to the shaft by a plurality of bolts 18. A locking pin 19 extends through end plate 17 into the bearing 15 so as to prevent relative rotation between the bearing 15 and the shaft 11. Any suitable bearing housing cover 20 is secured over the bearing in order to minimize the entrance of foreign materials and is secured in position by a suitable number of bolts 21. The bearing is further sealed against the entry of foreign materials by a suitable seal, such as an O-ring 22, arranged between the shaft 11 and the inner end of the bearing housing 12.

A gas-pressurized cushion chamber 23 is formed by an enlarged central cylindrical bore 23' in the lower portion of the shaft II which is closed off at the lower end thereof by a threaded plug or cover 24 secured in the end of the bore 23. The other end of the cushion chamber is formed by a floating piston 25 which is slidably mounted in the bore 23 and is provided with suitable sealing rings 26 which prevent the passage of gas from the cushion chamber to the part of the bore above the piston 25. A surge chamber 43 is formed between the head of piston 25 and the top of bore 23' in the lower part of shaft 1! and which chamber receives supporting fluid, as will hereinafter be described. The gas pressure within the cushion chamber can be regulated in any suitable manner as through conventional air valve 27 and passage 28 by, for example, a suitable pump, not shown. Alternatively, the cushion chamber can be pressurized by an external source, such as, for example, by an accumulator, not shown, which supplies pressurized gas through conventional piping, not shown, to passageway 28.

The movable crushing member is slidably mounted on shaft 11 and is adapted to be supported, and positioned axially thereon, by a unique fluid bearing means 34. The fluid bearing means includes fluid bearing support chamber 35 formed between shoulder 29 on shaft 11 and the inner side of collar 10 of the mounting cone 8 which supports the mantle 7. As shown in FIG. 1, the mounting cone 8 is formed with an internal cylindrical bore 30 which is slidably fitted over the lower cylindrical portion of the shaft 11 and a suitable fluid seal, such as generally indicated by

reference numerals

31, 32, 33, is provided on both sides of the fluid support chamber between the shaft 1 l and the mounting cone 8. The fluid bearing means further includes means, such as a motor driven pump 83 shown in FIG. 8, for injecting or supplying supporting fluid, such as oil, from reservoir 82 into the supporting chamber through supply pipe 84, stationary connection 38, piping system 40, bore 42, surge chamber 43 and bores 44.

Connections

39, 41 in piping system 40 are designed to allow the relative movement of the parts during normal gyratory operation of the crusher and consequent movement of the upper end of the shaft 11.

In operation, cushion chamber 23 is supplied with gas to a predetermined pressure through the valve 27, which will normally bias the piston 25 to the upper end of the cylindrical bore 23' in the shaft 11. The movable crushing member mantle 7 is then set with reference to the stationary crushing member mantle 1 by supplying a suitable fluid, such as oil, to the tube connection 38 from which it flows through the passageway 42 into the surge chamber 43 above the piston 25 and from thence outwardly through the passageways 44 into the support chamber. The oil is injected into the supporting chamber until the desired spacing is achieved between the two mantles 1 and 7, thereby providing the desired setting of the movable mantle 7. For normal operation the fluid bearing sup porting chamber will hold the desired setting of the movable mantle 7, so that a substantially uniform maximum size of crushed material is permitted to pass through the crusher. However, the combination of fluid bearing means and the gaspressurized relief means provides an automatic relief means for releasing the setting of the movable mantle 7 in the event uncrushable material, such as tramp iron, is encountered during operation of the crusher. This automatic regulation is obtained in response to the occurrence of a predetermined maximum pressure between the relatively movable mantles l and 7 in such a way that this pressure is transmitted from the movable mantle 7 through its mounting cone 8 to the fluid in the supporting chamber so that this supporting chamber fluid tends to be expelled out of the chamber through the passageways 44 into the surge chamber 43. This results in the exertion of the higher pressure upon the head of the chamber 23. Since fluid such as oil is substantially noncompressible while gas is readily compressible, the piston 25 will move downwardly and reduce the volume of gas in the cushion chamber, thereby expanding the size of the surge chamber 43. This expansion of the surge chamber 43 tends to relieve the pressure of the oil in the fluid supporting chamber, thereby permitting the mounting cone 8 to move downwardly whereby the spacing between the movable and stationary mantles is increased. This movement will normally continue until the spacing between the mantles 7 and 1 has increased sufficiently to permit the uncrushable material to drop from between these two mantles and pass out of the crusher. When this occurs, the fluid pressure in the supporting chamber will momentarily be reduced with the result that the compressed gas in the cushion chamber will tend to expand and reestablish the balance in pressure between the fluid in the supporting chamber and the gas in the cushion chamber. This will tend to move the piston 25 upwardly so as to force the fluid out of the surge chamber 43 through the passageways 44 and back into the supporting chamber, thus resetting the mounting cone 8 and its mantle 7 to the originally set position. In this manner, an automatic relief means is provided whenever uncrushable substances are encountered during operation of this type crusher.

in actual operation, a certain amount of larger than desired crushed material will pass through the crusher after each expulsion of such an uncrushable material until the movable mantle 7 returns to its predetermined set position; however, since the crusher need not be stopped and its drive is continuous during this safety relief operation, the amount of larger particles is maintained at a minimum because the constantly moving and oscillating crushing member tends to accommodate itself fairly rapidly to the normal equilibrium position of the pressures between the fluid in the supporting and surge chambers and the gas pressure in the gas-pressurized cushion chamber.

In order to provide the desired gyratory drive to the movable crushing member mantle 7, a fluid motor 36 is provided which comprises a plurality of circumferentially spaced radially extending cylinders 45 formed in a cylinder block 46. This cylinder block 46 includes a mounting flange 47 which is rigidly secured by a spider to the main mounting ring frame 5. In the illustrated construction, this spider includes a plurality of circumferentially spaced legs 48 which are formed integral with and extend radially from the mounting ring frame 5 inwardly to an axially extending hub 49, which also is formed integral with the inner ends of the legs or spokes 48. The cylinder block flange 47 is demountably secured in any suitable manner to the spider hub 49, and, in the illustrated construction, is thus secured by a plurality of bolts 50. In this structure the fluid motor may be readily disassembled from the crusher simply by removal of the bolts 50, thus providing for ready access to the entire fluid motor for inspection and repairs.

In order to assure against the entrance of undesirable foreign material into the operating mechanism of the crusher, the spider hub 49 is formed with a circular sealing flange 51 which is arranged in telescopically overlapping relationship with a complementary circular sealing flange 52 formed on the lower end of the mounting cone 8. These two sealing flanges extend around the exterior of the operating mechanism and the driving fluid motor, so that material which is crushed by the operation of the mantles is discharged around the outside of the sealing flanges and falls out of the crusher through openings formed between the spokes or legs 48 of the motor supporting spider. In order to permit relative gyratory movement of the sealing flange 52 relative sealing flange 51, the adjacent surfaces of these two flanges are formed on different diameters to provide a predetermined clearance therebetween. The entry of dust into the operating mechanism or the fluid motor is prevented by an improved frusto-spherical sealing ring 53, which is slidably mounted in one of the relatively movable members and slidably engages the other. In FIG. 1 this sealing ring 53 is slidably mounted in the gyratory member by being held in position by a mounting ring 54, which is secured by a plurality of bolts 55 to a lower end of the sealing flange 52. The inner end of the sealing ring 53 forms a snug sliding sealing flt with the outer cylindrical surface of the sealing flange 51 and is adapted to have a snug sliding sealing fit in the mounting space formed between the lower edge of the sealing flange 52 and the adjacent surface of the mounting ring 54. Thus, the gyratory movement of the mounting cone 8 results in a relative gyratory movement of the sealing flange 52 around the sealing flange 51, so that the flange 52 and the sealing ring 53 slide relative to each other in a progressive manner around the stationary sealing flange 51 as the mounting cone 8 gyrates in response to the operation of the fluid motor. This provides a very effective flexible dust seal, which seals off all of the operating parts and materially improves the operation of the crusher and minimizes wear of its operating mechanism.

The fluid motor illustrated in FIGS. 1, 2, and 3 is of the multiple thrustor piston type and provides for the gyratory drive with a desired creep between the crushing members by utilizing a non-direct mechanical connection for transmitting power between the motor and the driven crushing member. This driving connection is obtained by forming each motor cylinder 45 with an open outer end and slidably mounting a thrustor piston 56 in each cylinder for driving engagement with a thrust ring. The outer ends of the pistons 56 are provided with piston heads which form bearing portions 57 on the ends of each piston adapted to contact thrust ring 58 rigidly mounted in any suitable manner on a thrust frame 59 suitably secured by plurality of bolts 60 to the lower end of the main drive shaft 1].

A main control valve 6! of the rotary spool type is provided for sequentially supplying fluid under pressure to successive cylinders of the fluid motor and sequentially exhausting fluid from these cylinders. This spool valve is provided with axially extending fluid supply passageways 62 which communicate with a supply duct 63 through arcuate supply passageways 64 formed in a valve housing portion 65 of the cylinder block 46. A similar set of passageways is provided for exhausting fluid sequentially from the cylinders of the fluid motor. These exhaust passageways include axially extending exhaust passageways 66 in the spool valve body 61 which communicate with the intakes of the cylinders 45 and also communicate with an arcuate exhaust passageway 67 in the valve housing position 65 of the cylinder block. The arcuate exhaust passageway 67 also communicates with a fluid exhaust duct 68 which is adapted to be connected to a fluid reservoir 69, FIG. 8.

The operation of the motor and its control valve can best be understood by a consideration of the details illustrated in FIGS. 2 and 3. As there shown, the body of the spool valve 61 is diametrically divided into two major portions in which the supply and exhaust passageways are formed. On one side of this diametrical division, two fluid supply passageways 62 are adapted to conduct fluid from a suitable source of fluid supply, such as a controllable variable output pump 70, FIG. 8, which is connected to supply fluid under pressure to the valve supply duct 63. Fluid passes from the supply passageways 62 into the intakes of the motor cylinders 45 and the fluid pressure is transmitted through the pistons 56 and the bearing head portions 57 thereof to the thrust ring 58. As can be more clearly understood by reference to FIG. 3, rotation of the spool valve 61 in a counter-clockwise direction, as indicated by the arrow 71, will progressively supply fluid under pressure to successive motor cylinders 45 in counterclockwise direction. As shown in this figure, the respective pistons 56 in the motor cylinders move from an inner retracted dead-center position progressively outwardly to an outer dead-center position. As these pistons move outwardly, the fluid pressure which is transferred by the pistons to the thrust ring 58 causes the ring 58 to move outwardly. Since the ring 58 is rigidly secured to the shaft 11 through the thrust ring frame 59, the outward movement of one part of the thrust ring under the pressure of the outwardly moving pistons tend to cause a corresponding inward movement of the diametrically opposite side of the thrust ring, exerts an inward pressure on the motor pistons 56 which are in engagement with this opposite side of the thrust ring and tends to move these motor pistons inwardly. The spool valve 61 is so constructed that the two exhaust passageways 66 are in communication with the motor cylinder supply passages of the cylinders in which the pistons 56 are being biased inwardly as explained, during the time that the spool valve supply passageways 62 are in communication with the other motor cylinders. In this way, the pistons which are being biased inwardly by the thrust ring 58 are allowed to move inwardly as the pressure on the inner sides of the pistons is relieved through the exhaust passageways 66 of the spool valve. These valve exhaust passageways communicate with the fluid reservoir 69, FIG. 8, through the arcuate exhaust passageways 67 and the exhaust duct 68 which is connected through suitable piping 72 to the reservoir 69. Thus, the motor inherently and automatically forces the fluid out of the cylinders from which it must be exhausted in order to permit the pistons to be retracted, and it is not necessary to provide any external arrangement for withdrawing this fluid.

In order to obtain a continuous operation of the fluid motor and to provide a means for varying the speed of gyration of the crushing member mantle 7, a suitable motor 73 is coupled to the spool valve 61 and is adapted to be driven at a predeterminable speed. In the particular embodiment shown in FIG. 8, the motor 73 is of the hydraulic type and is readily controlled by the speed of a variable output, motor driven, pump 74 which supplies fluid from the reservoir 69 to motor 73 through line 76. The fluid is retumed to the reservoir through line 77.

In order to maintain the most desirable operating temperature for the fluid, the reservoir 69 can be provided with a thermostatically regulated heating and cooling unit 77' connected by suitable piping 78 to the reservoir. In addition, a suitable filter 79 is connected to the main withdrawal conduit 80, so that fluid supplied to the operating parts of the system from the reservoir will be continuously filtered before being recirculated.

It is frequently desirable to regulate the extent of the relative gyratory movement of the crushing members, and this may conveniently be accomplished by varying the stroke or travel of the motor pistons 56. Since these pistons are responsive to the fluid flow thereto in the motor cylinders 45, control of the fluid flow to the cylinders 45 will result in a corresponding control of the length of travel of the pistons 56 within the cylinders 45. This control of the fluid flow to the pistons 56 is conveniently obtained by supplying the fluid to the fluid motor through a conventional, motor driven, variable output pump 70. By controlling the drive speed of pump 70, it is possible to control the fluid output of the pump to fluid motor cylinders 45. In this manner, the stroke or travel of the fluid motor pistons 56 is controlled by the simple control of the variable output pump 70, and a very flexible gyratory crusher control is obtained. In order to prevent excessive pressures in the fluid system for the main fluid motor, as might occur in the event the system became temporarily stalled by some uncrushable substance between the mantles, a safety relief valve 81' is connected in bypass conduit 81 extending from the motor to the reservoir 69.

With this construction of the gyratory driving mechanism, a limited amount of slippage or creep occurs during normal operation of the crusher between the two relatively movable crushing members. The major part of this creep will occur between the thrust ring 58 and the fluid driving motor. In order to minimize the friction and wear between these parts due to this slippage the bearing portions 57 of the heads of the pistons 56 are preferably formed on an arc which has a radius substantially equal to the distance from the center of the fluid motor, that is the axis of the rotary spool valve 61, to the outer periphery of the piston head when the piston is in its fully retracted position. In this manner the curvature of the arc of the bearing portion of the piston head will normally be formed on a shorter radius than that of the inner engaging surface of the thrust ring S8v A slight additional amount of creepage may occur between the movable member mounting cone 8 and the drive shaft 11 as it is not rigidly mechanically connected thereto but simply has a snug driving fit therewith. This snug driving fit, however, is not a rigid connection, as it is essential that the mounting cone 8 can readily slide axially over its mounting surface on the shaft 11 in order to provide for its proper setting and also to allow for its safety release movement whenever an uncrushable substance appears between the crushing member mantles l and 7. Thus, the present improved gyratory crusher incorporates a very versatile controllable mechanism with provisions for its most effective and efli cient operations incorporating automatic safety relief features which further enhance its utility and life.

FIGS. 4 and illustrate another embodiment of the present invention which may be employed where it is desirable to provide for a greater amount of slippage or creep between the relatively movable crushing members. The various similar parts of this construction will not be described in detail as their structure, relationship, and operation are the same as corresponding parts of the previously described crusher embodiment. Corresponding parts in this construction bear the same reference numerals as the crusher illustrated in FIGS. 1, 2, 3, and 8.

The primary difference in the fluid motor construction is in the thrustor pistons and the bearing portions thereof which transmit thrust from the pistons to the thrust ring for actuating the relatively movable crushing member. Added flexibility is provided by this construction in that the bearing portions of the piston heads are formed as separate members. Each of these bearing portion members includes an arcuate shoe preferably integrally formed with a thrust rod 85 which has a universal working seat on the thrustor piston. This universal seat is formed by a ball and socket joint which, in the illustrated embodiment, includes a ball 86 formed on the inner end of the thrust rod 85' seated in a substantially hemispherical thrust bearing seat 86' formed on the head of a thrustor piston 87. This thrustor piston 87 is adapted to be actuated by fluid pressure in cylinders 45 similar to the actuation of the pistons 56in FIGS. I, 2, and 3. The thrust is transmitted from the fluid in the cylinders 45 to the pistons 87 and from the pistons 87 through the thrust rods 85' to the shoes 85 which engage the inner work surface of a thrust ring 88. This thrust ring 88 is mounted in any suitable manner on a thrust frame 89 which functions in the same manner as the thrust frame 59 in the embodiment shown in FIGS. 1, 2, and 3. In the present construe tion, the thrust ring 88 is substantially cylindrical and, therefore, minimizes axial forces on the cylinder block 46. A suitable retaining ring 90 is arranged over the lower end of the thrust ring 88 and is held in position by suitable retaining bolts 91 threadedly secured to the thrust frame 89.

The general operation of this construction is the same as the previously described embodiment, with the added feature that the pivotal connection of the thrustor shoes 85 on the thrustor pistons 87 more readily permit relative movement between the thrust ring 88 and the fluid motor. This, therefore, provides for a more flexible connection between the driving motive power source and the driven gyratory crushing member mantle 7 and further minimizes friction and wear resulting from the slippage or creep of the relatively movable crushing member. The particular construction of the shoes and of the thrustor pistons can readily be varied to include the basic operating features disclosed in order to accent one or another aspect of the driving mechanism.

The fluid motor drives illustrated and described in the preceding embodiments of the present invention have included a centrally arranged motor cylinder block with the thrustor pistons adapted to exert a generally outward pressure on a thrust ring arranged around the outer periphery of the pistons. This specific arrangement of thrustors and thrust ring is not essential to the present invention and the fluid drive motor may well utilize an arrangement wherein the thrust ring is centrally arranged and the thrustors peripherally surround the thrust ring and are adapted to exert inward forces against the thrust ring. This latter type fluid motor is illustrated in the embodiment shown in FIG. 6 and 7.

In this construction, the details of the crusher, including the main crushing members, their mounting, and sealing and adjustment features, illustrated in other embodiments of this invention can be utilized and are, therefore, not illustrated in FIGS. 6 and 7. Similar parts of the crusher shown in these two figures, including the mounting members, the fluid motor, main spool valve, and its fluid connections and driving motor, are essentially the same as those previously described and function in the same general manner.

In this embodiment, the main fluid drive motor is provided with a cylinder block 92 which is rigidly secured, as in the previous embodiments, by a plurality of bolts 50 to the stationary spider hub 49, As in the previously described constructions, the valve housing 65 extends axially of the cylinder block and preferably is formed integral therewith. The spool valve fluid supply passageways 62 communicate with fluid motor cylinders 93 by supply ducts 94 extending through the cylinder block 92, and the fluid exhaust passageways of the spool valve 66 communicate with the cylinders 93 through these same fluid passageways 94. In this construction, the spool valve 61 is essentially the same as that previously described and is divided diametrically into two major portions, one of which communicates with the valve supply passageways 62 and the other half of which communicates with the valve exhaust passageways 66. Thus, there is no interference or crossconnection between the supply and exhaust of the fluid from the fluid motor cylinders, even though both utilize the same fluid passageways 94 which extend from the valve to the cylinders 93.

When fluid pressure is applied to the fluid supply duct 66 and is transmitted through the valve passageways 62 and the cylinder block passageways 94 in communication therewith, this fluid pressure is applied to fluid in the communicating cylinders 93 and thereby biases pistons 95 in these cylinders in an inward direction. These pistons are formed with thrust transmitting cylinder heads having bearing portions thereon similar to those of the embodiment shown in FIGS. 4 and 5. These bearing portions include shoes 96 preferably integrally connected to thrust rods 97, which have substantially universal ball and socket connections with their respective pistons 95. These ball and socket connections are shown as including a ball 98 formed on the ends of the thrust rods 97 opposite the shoes 96 and seated in substantially hemispherical sockets 99 formed in the adjacent faces of the pistons 95. In order to allow for desired gyratory movement of the movable crushing member without interference between the thrustor shoes 96 and also in order to provide a desirable flexibility in the slippage or creep of the movable crushing member, the sum of the circumferential extent of all of the thrustor shoes 96 is less than the complete circumference of the engaged surface of the thrust ring 100 which is rigidly mounted on the adjacent end of the main shaft 11. This thrust ring preferably has a slight crown on the outer working surface thereof in engagement with the working faces of the thrustor shoes 96 so as to allow for a slight shifting of the engaging surfaces of the shoes and ring during the gyratory actuation of the ring by the shoes and also to produce a centering action on these shoes. This also minimizes axial forces between the shaft 11 and the fluid driving motor. In this construction, the thrust ring 100 can be mounted in any suitable manner on the shaft 11, and it is shown as being secured in position by a suitable mounting ring held in position by a plurality of bolts 102. The individual cylinders of the fluid driving motor are each provided with separate demountable cylinder heads 103 which facilitate assembly, inspection, and repairs when these are desirable.

It will be apparent from the above description that use of the multiple thrustor type fluid motor permits design flexibility which was heretofore unknown with conventional rotary drive and gearing arrangements. For example, gyratory crushers employing the present fluid motor drive can be physically oriented in almost any position and it is a simple matter to connect the necessary hydraulic lines to the crusher regardless of how it is oriented. This is in definite contrast to the conventional drive arrangement wherein the position of the pinion gear shaft must always be oriented relative the source of rotary power, which is typically a conventional belt drivev Furthermore, control of the amount of gyratory displacement is achieved by simply providing means, such as a variable displacement pump, for varying the fluid flow to the fluid motor. Likewise, speed of the gyratory action can also be simply varied by varying the speed of rotation of the spool valve which distributes fluid to the motor. It should also be recognized that use of this fluid motor will take up considerably less headroom than with the conventional rotary drive and gearing arrangement and, as a result, it will enable a more compact design for gyratory crushers.

In addition, the provision of the fluid bearing means provides an efficient fluid bearing which supports the movable crushing member and which also provides means for setting or adjusting the movable crushing member relative the fixed crushing member. Finally, the combination of the fluid bearing means and the gas-pressurized support chamber provides an automatic release means which enables reduction of pressure in the fluid support bearing when uncrushable material in the crushing chamber threatens damage to the machine. In this manner the movable crushing member is permitted to move relative the fixed crushing member and thereby allow release of the uncrushable material.

It is to be understood that the above-described embodiments are simply illustrative of the application of the principles of this invention. Numerous other embodiments may be readily devised by those skilled in the art which will embody the principles of the invention and fall within the spirit and scope thereof.

lclaim:

1. In a gyratory crusher comprising relatively movable crushing members, fluid motor means for imparting a relative gyratory crushing movement to one of said members, said fluid motor including a plurality of circumferentially spaced hydraulic thrustors, a thrust ring on said one member arranged for driving engagement with said thrustors, and means for sequentially actuating said thrustors for gyrating said one member through said thrust ring and which is further characterized by supporting means including a central shaft and fluid bearing means for adjustably supporting said one member on said shaft, said one member being slidably mounted on said shaft, said fluid bearing means including a fluid support chamber between said shaft and said one member, said fluid bearing means further including a fluid pump for supplying fluid into said support chamber to a predetermined volume for positioning said one member on said shaft.

2. The gyratory crusher described in claim 1 which is further characterized by a gas-pressurized relief means formed in said shaft for reducing the pressure of the fluid in said fluid support chamber when forces on the said one member exceed a predetermined limit.