US2787425A - Pneumatic release for gyratory crushers - Google Patents

Description

April 2, 1957 o. c. GRUENDER PNEUMATIC RELEASE: Foa GYRATORY cRusHERs 4 Sheehcs-Sheet l Filed Dec. 12. 1952 w www April 2, 1957 o. c. GRUENDER PNEUMATIC RELEASE FOR GYRATORY CRUSHERS 4 Sheets-Sheet 2 Filed Dec.

7 r y im@ W wm w 7, ff am r mf w O. C. GRUENDER PNEUMATI-C RELEASE FOR GYRATORY CRUSHERS April 2, 1957 4 Sheets-Sheet 3 Filed Dc. 12, 1952 COMPRESSOR T72 vena? Oscar 6*, Gruender Q7 pod/La @um 4 Sheets-Sheet 4 O. C. GRUENDER PNEUMATIC RELEASE FOR GYRATORY CRUSHERS April \2, 1957 Filed Dec. 12, 1952 n H n w 6 2 3 www w D Q 9 a 7 C W im; w m. V I y 7 7 lil 9 w, Q n y w ,9 j Z m;

PNEUMATIC RELEASE FR GYRATRY CRUSHERS Oscar C. Gruendcr, Milwaukee, Wis., assigner to Nordberg Manufacturing Company, Milwaukee, Wis., a corporation of Wisconsin Application December 12, 1952, Serial No. 325,733

3 Claims. (Cl. 241-290) My invention relates to an improvement in yielding release mechanisms applicable for use with a wide variety of mechanisms, including Crushers, grinders and attrition mills.

Another purpose is to provide a yielding release which may be efficiently employed with gyratory Crushers, grinders and attrition mills, or with similar mechanisms, in which a crushing, grinding or attrition chamber is formed by opposed and relatively movable members.

Another purpose is to provide a yielding release adapted for use with gyratory cone Crushers.

Another purpose is to provide a yielding release which shall be small and compact, occupying a minimum of space, and which shall be such as to be economically manufactured, the parts being uniform insofar as possible.

Another purpose is to provide a structure whereby sucient pneumatic pressure may be maintained While unit pressure is held to a minimum.

Another purpose is to provide a pneumatic release wherein a piston and cylinder may be easily sealed from dust or powdered materials normally found in an area of crushing operation.

lt will be understood that my system may advantageously operate pneumatically of hydraulically but, as a matter of illustration, a pneumatic system is shown.

Other purposes will appear from time to time in the course of the specification and claims.

I illustrate the invention more or less diagrammatically in the accompanying drawings, wherein:

Fig. l is a vertical, axial section illustrating my invention as applied to a gyratory crusher having a conic head;

Fig. 2 is a section on a slightly reduced scale on the line 2-2 of Fig. 1, with parts omitted;

Fig. 3 is a section on an enlarged scale on the line 3-3 of Fig. l;

Fig. 4 is a diagrammatic illustration of a circuit involved in the delivery of air pressure to the crusher; and

Fig. 5 is a view taken on the same plane as Fig. l, illustrating a variant form of the pneumatic release.

Like parts are indicated by like symbols throughout the specification and drawings.

This application is a continuation-in-part of my copending applications, Serial No. 697,227, tiled September 16, 1946, now abandoned, and Serial No. 259,940, filed December 5, 1951, now Patent No. 2,679,984.

Referring to the drawings, 1 generally indicates a frame member having a top flange 2. 3 is an outwardly extending web or flange having an upwardly extending portion 4 with an inner conic face 5, a flat top portion 6 and an outer and generally cylindrical face 7.

Secured to the frame member 1 as by the webs or spider members 8 is an internal sleeve 9 having an upper and outer enlargement 10 closed by the bearing support 11 which supports an upper spherical bearing plate 12 adapted to receive a correspondingly formed portion of the crusher head 13. The crusher head is shown as secured to a crusher shaft 14 having a downwardly tapered lower extension 15 received in a suitable eccentric aperture in a rotated sleeve 16 which is mounted for rotation within the outer xed sleeve 9. It may be rotated by the top gear 17, received within the enclosure formed by the members 10 and 11, as will be clear from Fig. l. lt is in mesh with the drive pinion 18 on the drive shaft 19 which may be driven by any suitable means not herein shown. The drive shaft 19 is received in any suitable sleeve 20 which extends through an opening or passage 21 in the side frame member 1. Any suitable oil and dust seal between the head and the bearing assembly 11 may be provided. I illustrate, for example, interpenetrating flanges 22 and 23, having opposed spherical surfaces concentric with the spherical upper supporting and head receiving surface 12a of the bearing plate 12. The head supports any suitable mantle 30 held in position, for example, by a nut 31 in mesh with the securing member 32 removably secured to the top of the head 13. 34 is any suitable feed plate support removably carrying a feed plate 35. 36 is any suitable conic sleeve protecting the upper end of the screws 33 and serving as a feed-distributing or feed-receiving surface. It will be understood that in response to rotation of the sleeve 16, the shaft 15 is gyrated and the head 13 gyrates with the shaft, as if it were suspended at the center x which is located above the top of the crushing cavity inwardly dened by the mantle 30.

An essential feature of the type of crusher herein described is the provision of a yielding release which will prevent breakage or binding of parts when uncrushable material becomes lodged in the crushing cavity. I provide a bowl-supporting ring 40 having a lower circumferential aperture or groove 41 conforming generally to the above-described exterior surfaces 5, 6 and '7 of the frame flange 3. The inner surfaces of the groove 41 may be indicated as 5a, 6a and 7a. The annulus 40 includes an inner generally cylindrical portion 42 which is inwardly screw-threaded, as at 43, to receive the outwardly extending threads 44 of the outer bowl Wall 45. The wall 45 has an inwardly extending conic wall 46 and an upper and outwardly extending conic wall 46a which, by the connecting wall 46b, is connected to the outer bowl cylindrical wall 45, to form a closed housing. Positioned in the housing are webs 46c to or between which may be secured U-bolts 47, the lower ends of which pass about hook lugs 48a, extending outwardly from the outer face of the conic bowl liner 48. 49 are any suitable washers, and securing nuts for the U-bolts, as indicated at S0. 51 indicates access apertures closed by closure members 52. 53 indicates an upper removable hopper or conic wear member adapted to receive the feed delivered out over the outer edge of the feed plate 35. Positioned on the top of the above-described bowl assembly is an outer cylindrical hopper or deilector 55. 56 is any suitable closure or guard resting upon the upper end of the ring portion 42 and extending into close contact with the deflector 55. 57 indicates any suitable adjusting and locking screw which may extend down# wardly through the upper part of the guard 56. Each such screw has a nut 58 adapted to engage the lower surface of the portion 46h of the upper wall 46. It will be understood that when the screws 57 are loosened, the bowl assembly may be vertically adjusted in the supporting ring 40, 42, by rotating the bowl assembly, the threads 43 and 44 being in mesh. When the desired adjustment is attained, the screws 57 can be tightened, thereby locking the bowl assembly in relation to the supporting ring 40. Any suitable washers may be employed, as indicated at 59.

it will be understood that the ring 4th, carrying the entire bowl assembly, is tiltable upwardly away from the Patented Apr. 2, 1957- inner conic ange surface 5 of the main frame. For example, with reference to Fig. l, if uncrushable material is positioned in the crushing cavity between the mantle 30 and the liner 48, movement of the head toward the bowl, instead of causing breakage will lift one side of the ring 40, and will thus lift the bowl itself. However, in order to perform the proper crushing function, this lift or release can only be permitted when pressure which is in substantial excess of the normal crushing pressure is created. Otherwise the device will not operate as an etlicient crusher and will not properly size the crushed particles. In order to hold the ring 40 and the bowl assembly normally in the operative position in which they are shown in Fig. l, I provide the pneumatic system illustrated in the drawings herein.

It will be observed that the outer face 7 of the upward projection 2 is slightly arcuate, so that in effect a rolling contact is provided between the face 7a of the bowl-supporting ring 40 and the outer face 7 of the ange 3 when the tilting ring 40 is raised by the presence at one side of the crushing cavity of uncrushable material, such as tramp iron, or packed fines or the like. When the parts are at rest, as shown in Fig. l, there need normally be no contact between the opposed parts of the ring 40 and the' flange 2 except along the tapered surfaces S-Sa. The relationship of the parts is shown in somewhat greater detail in Fig. 5.

The particular drawings filed herewith are of a pneumatic system. It is important to maintain substantially uniform pressure throughout the system of' pistons and cylinders provided. It will be understood that the cylinders may be arranged in groups. In Fig. 2 I illustrate a single pressure supply line for the entire system. It will be understood, however, that in crushers of large size, it may be practical to have two or more supply inlets. Referring, however, for example, to Figs. 2 and 4, 70 illustrates any suitable source of pressure from whicha suitable iluid, such as air, may be delivered to a supply pipe generally indicated at 71. ThisY supply pipe is shown as having a release valveassembly 71a for exhausting to the atomsphere. It also has in communication with it, any suitable pressure gauge 71b;

The supply pipe 71 is shown as delivering air, under pressure, through the elbow 71e, to the interior of `one ofthe cylinders. Each pair of'cylinders is shown as connected by a communication duct 72. I find it advantageous that the duct 72 be slidable` in relation to the cylinder of each pair, in order to compensate automatically for variations in distance between the cylinders. To provide against the loss of air around the slidable ducts 72, I employ an O type sealing ring 73, as shown in Fig. 3. It will be observed that the ducts 72 are aligned between the axes of the cylinders. Where reinforcing Webs 1b are employed, the ducts 72 may be located beneath them, as indicated in Fig. 5, or the webs may be apertured to permit the passage of the ducts 72. By the employment of the system of ducts 72, as shown in Fig. 2, the entire series, or subgroups of cylinders, may be connected to the compressor 70, or to any other suitable source of pressure.

With reference to the supply of air under pressure, 80 illustrates an alternative connection to any suitable plantair supply. 81 is an emergency Valve which can be closed. 82 is any suitable release valve which can be set to the maximum permissible pressure. 83 is any suitable exhaust valve. The valves 71a and 83 may be employed to drain moisture from the system.

In order normally to hold the ring 40 and with it the crushingl element 48 in fixed positionl provide-a plurality of cylinders, each with `its associated piston. As a matter of convenience, I provide a plurality of downwardly open-ended cylinders 90. The cylinders may be held in position, for example, by receiving the screw-threaded lower ends of some of the locking screws 91 which secure said cylinders to the under face 3a of the annulus 3. Whereas I may arrangefthecylinders 90 in a variety of positions or arrangements, I lind it advantageous to arrange sixteen such cylinders in a circle surrounding the frame l, as shown in Fig. 2, to which they are closely adjacent.

Each cylinder has an outer depending cylinder wall 92 and an inner depending cylinder wall 93 which is substantially shorter than the wall 92. Each cylinder 90 receives an outwardly extending substantially hollow open- -top piston 94 which has an outer cylindrical piston wall 95 and an inner cylindrical piston wall 96 which is somewhat longer than the outer wall 95. As will be seen in Fig. l and Fig. 5, the outer piston wall 95 engages the outer cylinder wall 92 and the inner piston wall 96 engages the inner cylinder wall 93. The outer piston wall 95 is provided with the 0 rings 99 and the inner cylinder wall 93 is provided with the O rings 97 which provide an airtight seal for the air under compression and for the air chamber 98 which is created by the engagement of the piston and cylinder walls described. The air. chambers 98 of each cylinder are interconnected by the ducts 72. 150 indicates a dust cover which may be secured in any suitable manner as by the screws 100 to the open cylinders. to provide a cover or dust seal.

The upper portion of each cylinder 90 which is held against the face- 3a of the annulus 3 by the screws 91 is inwardly recessed as at 101 and apertured as at 102. The aperture 102 is in alignment with and forms a circular channel with the inner shorter depending wall 93 of the cylinder 90 and the aperture 102 is located centrally of the recess 101. Disposed within the channel 102 and extendingthrough ythe piston 94 and the cylinder 90 and through an aperture 103 in the annulus 3 and a similar aperture 104 in the outwardly extending flange 105 of the ring mais the tension member 106. lt will be observed that the apertures 104, 103 and 102 are larger than the tension rods 106 to permit a certain amount of relative transverse shiftingof the parts. The recess 101 is filled with the sealing,ring,107 which-surrounds the rod 106. The tension member 106 carries the head 108 which has the sphericall underface 109 adapted to seat within the chamfered opening 110 surrounding the aperture 104 in the ange or extensionr105. The piston 94 has the aperture 111 centrally located, through which the tension rod 106 extends, the aperturelll being equal in size and in alignment with the apertures 102, 103 and 104. The tension member 106v carries the nut 112 which has an upper spherical face 113 adapted to seat within the chamfered face 114' surrounding the aperture 111 and thus to engage the piston.

Fig. 5 illustrates a variant form of my device in which a structure is provided whereby the required amount of pressure may be maintained to hold the ring 40 and the crushing member 48 normally in fixed position, while at the same time the unit pressure may be halved. In this form the cylinder 90 is formed in-two parts 90a and 90b which maybe considered as two cylinders. Cylinder 90a has the outer longer depending wall 92a whichis shorter than the depending wall 92, shown in Fig. l. Cylinder 90a' also has the inner cylindrical shorter depending wall 93a which may be substantially equal in length to thev wall 93, shown in Fig. 1. The `wall 92a is 'provided with the' annular outwardly extending flange 115 whichvis apertured at 116 to receive the securing member 117.V The cylinder 90b has the outer cylindrical depending wall' 92b. and the inner depending wall 93b. The inner depending wall 93b is substantially shorter in length than the outer wall 9211 and depends from the inwardlyextending annulus' 90e; The cylinder 90bl has the outwardlyv extending'ange 118 which is apertured at 119 to permitthe passage of the securing member 117v tosecurecylinder 90b to cylinder 90a, the two cylinders being coaxial and equal in inside diameter.

The cylinder 90a receives thepiston 94a which has the-upwardly extending-outer cylindrical wall 95a. The piston'94a has the upwardly and downwardly extending inner wall 96a. The inner faceof the upward extension 96h of the inner wall 96a engages the outer face of the inner wall 93a of the cylinder 90a and the outer wall 95a of the piston 94a engages the outer wall 92a of the cylinder 90a. The outer face of the lower extension 96e of the wall 96a engages the inner face of the inner depending wall 93h of the cylinder 90b and extends a substantial distance int-o the cylinder 90b. The O rings 99a, 99b, 97a, 9'7b and 97e in the walls of the pistons and cylinders provide an airtight seal for the air under pressure in the chambers 98a and 98h.

Secured to the lower extension 96e of the wall 96a, as by the securing members 120, is the piston 94b, the outer walls of which engage the walls 92b of the cylinder 90b. The washer 121 is placed beneath the piston 94b and surrounds the tension rod member 106. The nut 112 is screwed on to the rod 106 and brought up against the washer 121, the spherical face 113 of the nut 112 seating in the chamfered edges 114a of the aperture 122 in the washer 121.

The inner wall 93a and the top of the piston 90a carry the central circular aperture or channel 130 which is slightly larger in diameter than the rod 106. The inner wall 96a of the piston 94a carries an aperture 131 which is coaxial with aperture 130 but large enough to admit the passage of the inner wall 93a as the piston 94a is raised. The inner wall 93h of the cylinder 90b has the aperture 132 which is coaxial with the apertures 130 and 131 but large enough to admit the passage therethrough of the lower extension 96e of the inner piston wall 96a. The piston 94b is centrally apertured coaxially with apertures 130, 131 and 132, as at 123, to permit the passage of the tension rod 106.

In order to provide uniform pressure in the cylinders 99a and 9lb, `I illustrate in Fig. 5 the passages 140 in the cylinder 90a and 141 in the cylinder 90b into which are threaded the pipes 142 and 143. The elbows 71d and 71e and the connection therebetween, generally indicated as 711i, join the air chambers 98a and 98h. 71g is the supply pipe to the connection 71f to supply pressure from any suitable system, such as that indicated in .i

Fig. 4 and described above. Any suitable pop-olf valve is indicated at 71h and may be located as shown in the pipe 71g adjacent the manifold formed by the members 71d, 71f, 71C, 142, 143.

Connecting ducts 72a and 72b are connected to cylinders 90a and 90b in alignment with the axes thereof, as indicated in dotted lines in Fig. 5, to connect air chambers of adjacent cylinders.

`It will be realized that whereas I have described and shown a practical and operative embodiment of my invention, nevertheless many changes may be made in size, shape, number and disposition of parts without departing from the spirit of my invention. I, therefore, wish my description and drawings to be taken as in a broad sense illustrative or diagrammatic, rather than as limiting me to my specific disclosure herein.

The use and operation of my invention are as follows:

I illustrate a simple and eicient pneumatic release system which may be applied advantageously to Crushers in which a head or crushing member is moved toward and away from a normally fixed crushing member. In the present application II illust-rate my invention as applied to the well known Symons cone Crusher in which the conic ring 3l) is gyrated toward and away from the normally fixed conic ring or element 48. lIt will be understood that the shapes and conformities `and proportions of the opposed crushing elements may be widely varied. Any crusher where a bowl structure needs to be released in response to excess crushing stresses is a proper crusher for the application of this release. In the particular embodiment of my invention as herein shown I employ a plurality of downwardly open, generally cylindrical cylinders adapted to exert an upward thrust against the lower side of the main frame ilange 2. As a matter of easy assembly and simplicity of the structure, I insert hollow, generally cylindrical pistons 94,

94a, 94b into the open ports of thecylinders 90, 90a,

b. lWhere, a pneumatic supply is maintained in the plant, II may use plant pressure in the cylinders. Or I may employ a compressor, as shown at 70 in Fig. 4. Or I may employ a combination of the two. -In any event, I employ some suitable pressure-releasing means or relief valve, as shown at 82, and normally maintain a pressure 'somewhat higher than the pressure at which noncrushable material will pass through the crusher. For example, if the pneumatic release may at 450 lbs. per sq. in. pass tramp iron and the like, and if the maximum permissible pressure is 475 lbs., I set the relief valve 82 to operate at 475 lbs., thereby dropping the pressure at least to 450 lbs.

In my present invention, the cylinders and the pistons are apertured, the apertures being in alignment and being somewhat larger in diameter than a tension rod which extends through the apertures in the cylinders and in the pistons through similar apertures in the outwardly extending flange on the frame 1 and in the outwardly extending portion on the ring 40 in order to grip the piston and the ring 40. When pressure is created in the air chambers within the cylinders, it forces the pistons downwardly against the retaining member on the tension rod, thus exerting a downward pressure on the ring 40 and the crushing member 48 which is carried thereby and holding the entire upper crushing structure seated in the inclined flange face 5 on the frame 1. Since the tension rod extends centrally through the cylinders and pistons, I escape the need for longer tension rods located between groups or pairs of cylinders and pistons and the necessary yoke connecting such pistons to the tension rod, shown in my copending applications listed above.

Since an entire operative structure is essentially conv tained above and within the lower edge of the cylinder wall, I am enabled to provide a dust cap and thus to seal the piston and cylinder from dust. In the variant form of my device, illustrated in Fig. 5, I provide means whereby the unit pressure may be substantially reduced while the required amount of pressure is maintained. It will be realized that whereas I show two pistons in a cylinder in a particular installation, it may be advisable to provide three such pistons thus even further reducing the unit pressure employed. This could be accomplished simply by providing inner depending walls on the piston 94b, much in the manner of the walls 96C, and securing to such inner lower depending walls a third piston which would be formed in the manner of piston 94h, as illustrated in Fig. 5, and attaching a third cylinder formed in the manner of cylinder 90b in which said third piston could slide.

Since the tension rods, in accordance with my present invention, extend through the pistons and cylinders in stead of between them, as shown in my co-pending applications, mentioned above, the connecting ducts 72 may be aligned with the axes of my cylinders. Thus the cylinders may be made uniform and no necessity exists for making different sets of cylinders to permit ducts arranged to by-pass tension rods arranged outside the cylinders. The ducts 72 and 72a, 72b are slidably mounted in the apertures in the cylinder walls, the 0 rings 73 serving to provide an airtight seal. The slidable mounting of the ducts 72 is particularly advantageous in compensating automatically for variations in the distance between cylinders, the alignment of the ducts with the cylinder axes permitting a varying number of cylinders to be used, and obviating concern for stresses due to vibration of the crusher in operation.

I claim:

1. In a yielding release for crushers having a circumferential main frame and a circumferential bowl support normally xed in relation to said main frame, abutment means for said bowl support and means for normally maintaining the bowl support xed in relation to said abutment means, including a plurality of cylinders spaced circumferentially about the main frame, said cylinders having an outer wall and a shorter inner wall, a plurality of second cylinders substantially coaxial with said rst' named cylinders and having an inner wall 'shorter than the inner wall of said rst named cylinders, pistons movable in said first named cylinders, said pistons having an inner wall in engagement with said first named cylinder inner wall and with said second named cylinder inner wall, pistons movable in said second named cylinder and connected with said rst named pistons, said cylinder inner walls and said piston inner walls and said second named pistons being axially bored and means for securing said pistons to said bowl support, said last named means including tension members extending through said axial bore and flexibly secured to said last named piston and said bowl support.

2. In combination, a crusher having a pair of relatively tiltable elements, a plurality of cylinders spaced circumferentially about and secured to one of said elements, each of said cylinders having an inner hollow cylindrical wall, a piston movable in each of said cylinders and means for securing each of said pistons to the other of said elements, said last named means including a tension member exible connected at its ends to said piston and to said last named element, said tension member extending longitudinally through said hollow inner cylindrical wall and having a diameter sufficiently less than the inner diameter of said wall to permit tilting of said tension member within said cylindrical wall.

3. In a yielding release for Crushers having a main frame and a bowl support, said main frame and said bowl support constituting relatively tiltable elements, means for normally maintaining said elements in xed, nontilted relation to each other, including a plurality of cylinders spaced circumferentially about the main frame, said cylinders having an outer wall and a shorter inner wall, a plurality of second cylinders substantially coaxial with said rst named cylinders and having an inner wall shorter than the inner wall of said rst named cylinders, pistons movable in said first named'cylinders, said pistons having an'inner wall in engagement with said first named cylinder inner wall and with said second named cylinder-inner wall,lpistons movable in said second named cylinder and Connected with said first named pistons, said cylinder inner walls and said piston inner walls and said second named pistons being axially bored and means for securing said pistons to one of said relatively tiltable elements, said last named means including tension members extending through said axial bore and flexible secured to said last named pistons and said last named tiltable element.

References Cited in the le of this patent UNITED STATES PATENTS 203,127 Elting Apr. 30, 1878 1,105,953 Bates Aug. 4, 1914 1,434,949 Glasner Nov. 7, 1922 1,503,105 Balcker July 29, 1924 1,544,850 Messier July 7, 1925 1,652,879 Standerwick Dec. 13, 1927 1,852,435 Ritchie Apr. 5, 1932 1,868,338 Symons July 19, 1932 1,889,555 King Nov. 29, 1932 2,020,692 Loudenslager Nov. 12, 1935 2,021,895 Newhouse Nov. 26, 1935 2,107,532 Hollenbeck Feb. 8, 1938 2,110,276 Rumpel Mar. 8, 1938 2,341,544 Gruender Feb. 15, 1944 2,349,790 Johnson May 23, 1944 2,358,038 Symons et al Sept. 12, 1944 2,359,987 Gruender Oct. 10, 1944 2,377,307 Brown June 5, 1945 2,464,733 Traylor Mar. 15, 1949 2,679,984 Gruender June 1, 1954 2,680,571 Bjarme June 8, 1954 FOREIGN PATENTS 623,423 Great Britain May 17, 1949

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