WO2006040641A1 - Rotary crusher for rubble and similar - Google Patents

Rotary crusher for rubble and similar Download PDF

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Publication number
WO2006040641A1
WO2006040641A1 PCT/IB2005/003003 IB2005003003W WO2006040641A1 WO 2006040641 A1 WO2006040641 A1 WO 2006040641A1 IB 2005003003 W IB2005003003 W IB 2005003003W WO 2006040641 A1 WO2006040641 A1 WO 2006040641A1
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WO
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Patent type
Prior art keywords
crusher
variable
outer casing
inside
baffle plate
Prior art date
Application number
PCT/IB2005/003003
Other languages
French (fr)
Inventor
Luca Ortoncelli
Lorenzo Zago
Original Assignee
Officine Meccaniche Di Ponzano Veneto S.P.A.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B02CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02CCRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/02Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft
    • B02C13/06Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor
    • B02C13/09Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor and throwing the material against an anvil or impact plate
    • B02C13/095Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor and throwing the material against an anvil or impact plate with an adjustable anvil or impact plate

Abstract

A crusher (1) for rubble and similar, having an outer casing (2), a cylindrical rotating body (4) mounted for rotation inside a crushing chamber (3) formed inside the outer casing (2), and at least one baffle plate (8) positioned inside the crushing chamber (3) to divert the work material entering the crushing chamber onto the peripheral surface of the rotating body (4); the baffle plate (8) being hinged to the outer casing (2) to oscillate, inside the crushing chamber (3), about a predetermined axis of rotation (B); the crusher (1) also having supporting members (9) interposed between the baffle plate (8) and the outer casing (2) of the crusher, and which permit adjustment as required of the tilt angle of the baffle plate (8) with respect to the vertical; and the supporting members (9) including at least one length­-adjustable anchoring tie (13) and at least one linear hydraulic actuator (14) located side by side and substantially parallel to each other.

Description

ROTARY CRUSHER FOR RUBBLE AND SIMILAR

TECHNICAL FIELD The present invention relates to a rotary crusher for rubble and similar.

More specifically, the present invention relates to a rotary crusher for crushing rubble, rock and quarry materials in general, as well as demolition and roadwork rubble or metal industrial waste such as scrap and similar.

BACKGROUND ART

As is known, rotary crushers comprise a casing or outer machine body; and a substantially cylindrical, jagged rotating body mounted for rotation inside a crushing compartment or chamber formed in the machine body. The top part of the crushing chamber communicates with the outside via a chute, by which the work material is fed onto the rotating body; and the bottom part of the crushing chamber communicates with the outside via a hopper, through which the crushed material drops out of the chamber by gravity.

In addition, known rotary crushers also comprise one or two baffle plates positioned inside the crushing chamber, just above the rotating body, to divert onto the rotating body both the incoming work material off the top chute, and the fragments of material hurled in all directions by rotation of the rotating body. The baffle plates are also positioned inside the crushing chamber so that the bottom lateral edge of each defines, with the peripheral surface of the rotating body, a gap or constriction, the width of which determines the maximum size of the crushed material issuing from the crushing chamber.

To adjust the maximum size of the crushed material issuing from the crushing chamber, the baffle plate or plates of most known rotary crushers are normally hinged to and project from the walls of the casing or outer machine body, so as to oscillate freely about horizontal axes parallel to the axis of rotation of the rotating body, and are maintained in a tilted position inside the crushing chamber by supporting members extending from the plates to the machine casing and designed to permit adjustment of the tilt angle with respect to the vertical, and therefore the distance between the bottom lateral edges of the plates and the peripheral surface of the rotating body. Obviously, in addition to locking the baffle plates in the desired crushing position, the supporting members must also be able to damp and absorb any mechanical stress produced by both routine crushing and penetration of any oversized non-crushable bodies.

This dual function is traditionally performed by all-mechanical or combined mechanical-hydraulic systems. In the case in point, all-mechanical supporting members currently comprise an anchoring tie or rod, with the head connected to the plate, and the shank fitted through an opening formed in the machine casing; and one or more helical thrust springs fitted to the tie shank so that one end rests on the body of the plate, and the other end rests on the machine casing. The anchoring tie obviously has a lock nut tightened adjustably to the end of the shank outside the casing, so as to rest on the outer surface of the casing and permit fine adjustment of the tilt angle of the plate with respect to the vertical; and the helical thrust springs are positioned on the shank to hold the lock nut on the outer surface of the casing.

In addition, the helical thrust springs are normally compressed to function rigidly as long as mechanical stress remains below a given threshold value, and to deform elastically, to permit backup/lift of the plate, when mechanical stress unexpectedly exceeds the threshold value, which is obviously less than the mechanical stress produced by an oversized non-crushable body jammed inside the gap between the plate and the rotating body.

Alternatively, combined mechanical-hydraulic supporting members are also used, in which the thrust springs are replaced by a conventional hydraulic damper, and the anchoring tie again provides for holding the plate in the desired operating position.

A major drawback of both types of crushers, featuring all-mechanical or hybrid supporting members, lies in the painstaking work involved in adjusting the tilt angle of the baffle plates, and in all the additional drawbacks this involves. In the first case, in fact, when working on the machine, particular care must be taken as regards the elastic thrust of the helical springs, which tends to draw the whole shank of the tie sharply inside the machine; whereas, in the second case, the hydraulic dampers being totally passive, the tilt angle of the baffle plate must be adjusted manually or using external handling means. DISCLOSURE OF INVENTION

It is an object of the present invention to provide a rotary crusher for rubble and similar, designed to eliminate the aforementioned drawbacks.

According to the present invention, there is provided a crusher for rubble and similar, comprising an outer casing; a substantially cylindrical rotating body mounted for rotation inside a crushing chamber formed inside the outer casing; and at least one baffle plate positioned inside the crushing chamber to divert the work material entering the crushing chamber onto the peripheral surface of said rotating body,- said at least one baffle plate being hinged to said outer casing to oscillate, inside the crushing chamber, about a predetermined axis of rotation; and the crusher also comprising supporting members extending from the outer casing to the baffle plate, and which permit adjustment as required of the tilt angle of said at least one baffle plate with respect to the vertical; the crusher being characterized in that said supporting members comprise at least one linear hydraulic actuator, in turn comprising a hydraulic jack, which has a hollow cylindrical body extending coaxially with a first longitudinal axis, a piston mounted to slide axially inside the longitudinal cavity of said hollow cylindrical body, so as to divide said cavity into a first and a second variable-volume chamber complementary with each other, and a movable rod inserted partly and in axially-sliding manner inside said hollow cylindrical body, so as to be fixed rigidly to said piston; said first variable-volume chamber reducing its volume alongside an increase in the tilt angle of said baffle plate with respect to the vertical; and said linear hydraulic actuator also comprising a relief device permitting selective outflow of pressurized fluid from said first variable-volume chamber when the pressure of the fluid inside the first variable-volume chamber exceeds a predetermined first threshold value, and a variable-volume pressurized-fluid storage tank for receiving a variable quantity of pressurized fluid from said first variable-volume chamber when the pressure of the fluid in the first variable-volume chamber exceeds a predetermined second threshold value lower than said first threshold value.

BRIEF DESCRIPTION OF THE DRAWINGS

A non-limiting embodiment of the present invention will be described by way of example with reference to the accompanying drawings, in which:

Figure l shows a plan view, with parts removed for clarity, of a crusher for rubble and similar, in accordance with the teachings of the present invention;

Figure 2 shows a larger-scale detail of Figure 1; Figure 3 shows a lateral section along line III-III of the Figure 1 crusher, with parts removed for clarity; Figure 4 shows a larger-scale detail of Figure 3; Figure 5 shows a lateral section along line V-V of the Figure 1 crusher, with parts removed for clarity. BEST MODE FOR CARRYING OUT THE INVENTION

With reference to the accompanying drawings, number

1 indicates as a whole a rotary crusher, particularly suitable for crushing rubble, rock and quarry materials in general, as well as demolition and roadwork rubble, and metal industrial waste such as scrap and similar.

Crusher 1 substantially comprises a casing or outer machine body 2, in which is formed a crushing compartment or chamber 3 of appropriate shape; a substantially cylindrical, jagged rotating body 4 mounted inside crushing chamber 3 to rotate about a respective preferably, though not necessarily, horizontal longitudinal axis A; and a drive unit (not shown) connected mechanically to rotating body 4 to rotate it at preferably, though not necessarily, constant speed about longitudinal axis A.

The top portion of crushing chamber 3 communicates directly with the outside via a work material inlet 5 formed in the top portion of casing 2; and the bottom portion of crushing chamber 3 communicates directly with the outside via a crushed material outlet 6 formed in the bottom portion of casing 2. Rotating body 4 is positioned, inside crushing chamber 3, between inlet 5 and outlet 6, and is designed, as it rotates, to crush the material fed by gravity into crushing chamber 3 through inlet 5.

In the example shown, casing 2 comprises a feed chute 7, at inlet 5, by which the work material is fed onto rotating body 4 along a trajectory inclined at a given angle with respect to the vertical; and the bottom portion of the casing, where outlet 6 is located, is designed for connection to a known hopper (not shown) through which the crushed material drops out by gravity from crushing chamber 3.

With reference to Figures 3 and 5, crusher 1 also comprises at least one baffle plate 8 housed inside crushing chamber 3, just above rotating body 4, and designed to divert onto the peripheral surface of rotating body 4 underneath both the incoming work material off chute 7, and the fragments of material hurled in all directions by rotation of rotating body 4. More specifically, inside crushing chamber 3, baffle plate 8 is tilted with respect to the vertical, so that the bottom lateral edge 8a of baffle plate 8 defines, with the peripheral surface of rotating body 4, a gap or constriction, the width h of which determines the maximum size of the crushed material issuing from crushing chamber 3.

More specifically, baffle plate 8 hangs from, or rather is hinged to, and projects from casing 2 so as to oscillate freely, inside crushing chamber 3, about an axis of rotation B parallel to longitudinal axis A of rotating body 4, and is maintained in a predetermined tilted position by supporting members 9 extending from casing 2 to the body of baffle plate 8, and which provide for adjusting as required the tilt angle of the plate with respect to the vertical.

In other words, supporting members 9 provide for adjusting as required the minimum distance between the bottom lateral edge 8a of baffle plate 8 and the peripheral surface of rotating body 4, i.e. the width h of said gap or constriction.

With reference to Figures 3 and 5, the example shown comprises two baffle plates 8 housed inside crushing chamber 3 so that the first baffle plate 8 is located directly over rotating body 4, facing chute 7, and the second baffle plate 8 is located lower down, immediately downstream from the first baffle plate 8, in the space between rotating body 4 and the lateral wall of casing 2, and is aligned with the gap or constriction defined by the bottom lateral edge 8a of baffle plate 8 and the peripheral surface of rotating body 4.

In addition, in the example shown, each of the two baffle plates 8 comprises a flat, substantially C- or L- shaped front plate 10 extending parallel to longitudinal axis A of rotating body 4, with its concavity facing rotating body 4; and a rear supporting frame 11 fitted at the top with a cylindrical pin 12 extending coaxially with axis of rotation B, and both axial ends of which are inserted in freely rotating manner inside the lateral walls of casing 2.

With reference to Figures 1, 2, 3, 4 and 5, each supporting member 9 comprises at least one length- adjustable anchoring tie 13 and at least one linear hydraulic actuator 14 located side by side and substantially parallel to each other, so that each connects rear supporting frame 11 of corresponding baffle plate 8 mechanically to outer casing 2 of the crusher.

More specifically, with reference to Figures 3 and 4, anchoring tie 13 substantially comprises a connecting rod 15 which has one of its two ends hinged to rear supporting frame 11 of baffle plate 8, and which extends through an opening 16, formed in the wall of casing 2, so as to project partly outside casing 2; and a mechanical stop member 17 which is fixed adjustably to the end portion of connecting rod 15 projecting outside casing 2, and rests on the outer surface of casing 2 to prevent complete withdrawal of connecting rod 15 inside casing 2. In the example shown, connecting rod 15 is defined by a threaded bar 15 having an articulated head hinged to rear supporting frame 11 of baffle plate 8 by a cylindrical pin extending parallel to axis of rotation B to allow threaded bar 15 to oscillate freely in a vertical plane perpendicular to axis of rotation B.

Mechanical stop member 17 is divided into two separate parts resting one on top of the other, and of which one is fixed rigidly to the wall of casing 2 at opening 16, and the other is fixed adjustably to the end portion of threaded bar 15.

More specifically, with reference to Figures 3 and 4, the part of mechanical stop member 17 fixed to the wall of outer casing 2 is defined by a locating bush 18 fixed rigidly to the wall of outer casing 2 at opening 16, and fitted in axially-sliding manner to the end portion of threaded bar 15 projecting outside casing 2 through opening 16. The top end portion of the central through hole of locating bush 18, i.e. the end portion facing away from opening 16, is flared to form a spherical-bowl-shaped cavity or seat 18a.

In the example shown, locating bush 18 is fixed rigidly to the wall of casing 2 with the interposition of a substantially U-shaped supporting plate 19 positioned astride opening 16 and having a central through opening through which the end portion of threaded bar 15 is fitted.

With reference to Figures 3 and 4, the part of mechanical stop member 17 fixed adjustably to threaded bar 15 comprises a cylindrical tubular sleeve 20 threaded internally to screw onto the end portion of threaded bar 15; and a spherical-bowl-shaped stop bush 21 fitted rigidly to cylindrical tubular sleeve 20 so as to rest on the top end portion of the central through hole of locating bush 18.

Mechanical stop member 17 also comprises a lock member 22 screwed to the end portion of threaded bar 15 and resting directly on the end of cylindrical tubular sleeve 20 to lock the body of cylindrical tubular sleeve 20, and therefore stop bush 21, rigidly to threaded bar 15.

In the example shown, lock member 22 comprises a lock nut screwed to threaded bar 15 so as to rest on the end of cylindrical tubular sleeve 20; and a hexagonal- headed cylindrical tubular sleeve welded directly to the lock nut, so as also to be fitted to the end portion of threaded bar 15. Spherical-bowl-shaped stop bush 21 is obviously sized to engage the spherical-bowl-shaped cavity 18a formed in locating bush 18, and so form, with locating bush 18, a spherical joint enabling the whole defined by cylindrical tubular sleeve 20 and threaded bar 15 to assume tilted positions with respect to the reference axis of locating bush 18.

In other words, spherical-bowl-shaped stop bush 21 is fixed rigidly but adjustably to connecting rod 15, so as to rest inside cavity or seat 18a of locating bush 18 to form a spherical joint.

With reference to Figures 1, 2 and 5, each linear hydraulic actuator 14 comprises a double-acting hydraulic cylinder or jack 23 interposed between casing 2 of the crusher and rear supporting frame 11 of baffle plate 8.

Hydraulic jack 23 extends coaxially with a longitudinal axis C lying preferably, though not necessarily, in a plane perpendicular to axes A and B, and substantially comprises a hollow cylindrical body 24 extending coaxially with longitudinal axis C; a movable rod 25 extending coaxially with longitudinal axis C and inserted telescopically and in axially-sliding manner at least partly inside hollow cylindrical body 24; and a movable piston 26 fitted in axially-sliding manner inside the longitudinal cavity of hollow cylindrical body 24 and fixed rigidly to the end of movable rod 25.

Hollow cylindrical body 24 is hinged to casing 2 to oscillate freely about an axis of rotation D perpendicular to longitudinal axis C of hollow cylindrical body 24 and at the same time parallel to axis of rotation B of baffle plate 8; and movable rod 25 extends through an opening 27 in the wall of casing 2 of the crusher, and is hinged at its free end to rear supporting frame 11 of baffle plate 8 to oscillate freely about an axis E parallel to axis of rotation D.

In the example shown, the cylindrical pin connecting the articulated head of threaded bar 15 to rear supporting frame 11 of baffle plate 8 also extends coaxially with axis E.

With particular reference to Figures 1 and 2, hollow cylindrical body 24 preferably, though not necessarily, comprises a cylindrical tubular sleeve 28 of appropriate length, extending coaxially with longitudinal axis C; and an endpiece 29 and a cap 30 closing the two ends of the sleeve. Cap 30 has a central through hole sized to be engaged in sliding manner by movable rod 25 with no pressurized-oil leakage.

Movable rod 25 is defined by a cylindrical bar of appropriate length, and by a connecting fork fixed rigidly to the free end of the bar and hinged to rear supporting frame 11 of baffle plate 8 by a known cylindrical pin coaxial with axis E.

* Movable piston 26 has a cross section complementary to that of the longitudinal cavity of hollow cylindrical body 24, so as to slide freely inside the longitudinal cavity in a direction parallel to longitudinal axis C, and divides the empty space inside the longitudinal cavity into two complementary variable-volume chambers 24a and 24b. Variable-volume chamber 24a is therefore bounded laterally by the body of movable piston 26 and by endpiece 29, while variable-volume chamber 24b is defined laterally by the body of movable piston 26 and by cap 30. The two variable-volume chambers 24a, 24b are obviously isolated from each other, and each is filled with pressurized oil. For which purpose, hollow cylindrical body 24 has two pressurized-oil feed passages by which pressurized oil is fed to or drawn from the two variable- volume chambers 24a, 24b. The passage for feeding pressurized oil to variable-volume chamber 24a is indicated 23a.

With reference to Figure 2, variable-volume chamber 24a reduces its volume when movable rod 25 withdraws inside hollow cylindrical body 24, i.e. alongside an increase in the tilt angle of baffle plate 8 with respect to the vertical, and communicates with the outside through pressurized-oil feed passage 23a.

With reference to Figures 1 and 2, each linear hydraulic actuator 14 also comprises a relief valve 32 which permits selective outflow of pressurized oil from variable-volume chamber 24a when the pressure of the oil in variable-volume chamber 24a exceeds a predetermined first threshold value; and a variable-volume pressurized- oil storage tank 33 which receives a variable quantity of pressurized oil from variable-volume chamber 24a when the pressure of the oil in variable-volume chamber 24a exceeds a predetermined second threshold value lower than the first threshold value associated with relief valve 32.

More specifically, in the example shown, relief valve 32 and storage tank 33 are located on endpiece 29 of hydraulic jack 23, on opposite sides to each other, so that both communicate directly with variable-volume chamber 24a. In the example shown, variable-volume pressurized- oil storage tank 33 is defined by a conventional bag-type pressurized-oil tank substantially comprising an airtight vessel fitted inside with an elastically deformable partition membrane (not shown) which divides the internal volume into two complementary variable-volume chambers. The first chamber communicates directly with variable- volume chamber 24a and receives pressurized oil; and the second chamber is isolated from the outside and contains gas at a predetermined adjustable reference pressure lower than the first threshold value governing operation of relief valve 32.

Finally, each supporting member 9 has a first on-off valve (not shown) for regulating pressurized-oil flow to and from variable-volume chamber 24a, and a second on-off valve ,(not shown) for regulating pressurized-oil flow to and from variable-volume chamber 24b, in both cases along respective pressurized-oil feed passages.

Crusher 1 obviously also comprises a hydraulic circuit (not shown) for appropriately conducting pressurized oil to and from the two variable-volume chambers 24a, 24b of hydraulic jack 23 along respective pressurized-oil feed passages.

Operation of crusher 1 as a whole is easily deducible from the foregoing description, with no further explanation required.

As regards operation of supporting members 9, on the other hand, assuming baffle plates 8 are already tilted as required, the control unit (not shown) of crusher 1 closes the on-off valve controlling pressurized-oil flow to and from variable-volume chamber 24a, thus cutting off variable-volume chamber 24a from the hydraulic circuit of the crusher, and leaves the on-off valve controlling pressurized-oil flow to and from variable-volume chamber 24b open to permit free pressurized-oil flow to and from variable-volume chamber 24b.

In this condition, mechanical stop member 17 of anchoring tie 13 is obviously maintained resting on the outer surface of casing 2 (i.e. stop bush 21 is maintained resting on locating bush 18) by the weight of baffle plate 8 itself and by the thrust produced by linear hydraulic actuator 14. If, during normal operation of crusher 1, an oversized non-crushable body gets jammed inside the gap between baffle plate 8 and rotating body 4, movable rod 25 is subjected to severe axial thrust which causes it to withdraw inside hollow cylindrical body 24, thus moving movable piston 26.

Variable-volume chamber 24a being full of non- compressible fluid and isolated from the outside, the axial thrust transmitted by movable rod 25 to movable piston 26 produces a rapid increase in pressure of the oil inside variable-volume chamber 24a.

When the pressure of the oil inside variable-volume chamber 24a exceeds the pressure of the gas inside storage tank 33, i.e. the predetermined second threshold value, the partition membrane of storage tank 33 deforms to allow the pressurized oil in variable-volume chamber 24a to flow out into the tank, thus reducing the total volume of variable-volume chamber 24a and so producing axial movement of movable piston 26 and partial withdrawal of movable rod 25. Obviously, the axial movement of movable piston 26 produces an increase in the volume of variable-volume chamber 24b, so that pressurized oil flows into variable-volume chamber 24b along the corresponding pressurized-oil feed passage.

In fact, at this operating stage, the on-off valve controlling pressurized-oil flow to and from variable- volume chamber 24b is still open, thus allowing free pressurized-oil flow to and from variable-volume chamber 24b.

If the partial withdrawal of movable rod 25 raises baffle plate 8 sufficiently to let the non-crushable body through between baffle plate 8 and rotating body 4, the drastic reduction in axial thrust produces a sharp fall in pressure of the oil inside variable-volume chamber 24a, and the gas inside storage tank 33 forces pressurized oil back into variable-volume chamber 24a, which increases in volume to restore movable piston 26 to its initial position and so restore baffle plate 8 to its initial operating position.

Conversely, if the pressure of the oil inside variable-volume chamber 24a continues to rise, despite partial withdrawal of movable rod 25 - indicating baffle plate 8 has not yet been raised high enough to let the non-crushable body through between baffle plate 8 and rotating body 4 - relief valve 32 comes into play, and, when the first threshold value is exceeded, allows controlled outflow of pressurized oil from variable- volume chamber 24a until movable rod 25 is withdrawn sufficiently to let the non-crushable body through.

In which case, once the non-crushable body is expelled, the control unit (not shown) of crusher 1 temporarily opens the on-off valve controlling pressurized-oil flow to and from variable-volume chamber 24a, to allow pressurized oil to flow into variable- volume chamber 24a and so re-tension anchoring tie 13, which is completed when mechanical stop member 17 of anchoring tie 13 comes to rest on the outer surface of casing 2, i.e. when stop bush 21 comes to rest on locating bush 18.

In the above operating mode, the control unit (not shown) of crusher 1 obviously keeps the on-off valve controlling pressurized-oil flow to and from variable- volume chamber 24b open to permit free pressurized-oil flow to and from variable-volume chamber 24b.

Conversely, if start-up of crusher 1 calls for adjusting the tilt of one (or both) of baffle plates 8, the control unit (not shown) of crusher 1 opens both the on-off valves controlling pressurized-oil flow to and from respective variable-volume chambers 24a and 24b, and, by means of the crusher hydraulic circuit, feeds pressurized oil into variable-volume chamber 24a, which expands gradually to produce a simultaneous gradual reduction in the volume of variable-volume chamber 24a with consequent outflow of pressurized oil. The increase in the volume of variable-volume chamber 24b obviously produces axial displacement of movable piston 26 towards endpiece 29, and consequent withdrawal of movable rod 25 inside hollow cylindrical body 24, thus completely raising baffle plate 8. Once baffle plate/s 8 is/are raised, the operator sets the new tilt angle of baffle plate 8 manually by adjusting the position of mechanical stop member 17 along connecting rod 15, which can be done extremely quickly by screwing or unscrewing cylindrical tubular sleeve 20 along threaded bar 15, after first loosening lock member 22.

Once mechanical stop member/s 17 is/are positioned, the control unit of crusher 1 inverts the pressurized-oil flow and feeds pressurized oil into variable-volume chamber 24a, which again expands. Obviously, the increase in the volume of variable-volume chamber 24a produces axial displacement of movable piston 26 towards cap 30, and consequent extraction of movable rod 25 from hollow cylindrical body 24, so that mechanical stop member 17 is again brought to rest on the outer surface of casing 2, but with baffle plate/s 8 set to the new tilt angle with respect to the vertical.

Once baffle plates 8 are set to the new work position, the control unit (not shown) of crusher 1 closes the on-off valve controlling pressurized-oil flow to and from variable-volume chamber 24a, and leaves the on-off valve controlling pressurized-oil flow to and from variable-volume chamber 24b open to commence crushing the material.

The advantages of supporting members 9 as described above are obvious: using linear hydraulic actuators 14 as described enables baffle plates 8 to be positioned quickly, with no particular danger to the operator performing the operation.

Linear hydraulic actuators 14 also provide for absorbing any mechanical stress, produced by an oversized non-crushable body jammed in the gap between either one of baffle plates 8 and rotating body 4, much more effectively as compared with currently used hydraulic dampers.

Clearly, changes may be made to crusher 1 as described and illustrated herein without, however, departing from the scope of the present invention.

Claims

1) A crusher (1) for rubble and similar, comprising an outer casing (2) ; a substantially cylindrical rotating body (4) mounted for rotation inside a crushing chamber
(3) formed inside the outer casing (2) ; and at least one baffle plate (8) positioned inside the crushing chamber
(3) to divert the work material entering the crushing chamber (3) onto the peripheral surface of said rotating body (4) ; said at least one baffle plate (8) being hinged to said outer casing (2) to oscillate, inside the crushing chamber (3) , about a predetermined axis of rotation (B) ; and the crusher (1) also comprising supporting members (9) extending from the outer casing (2) to baffle plate (8) , and which permit adjustment as required of the tilt angle of said at least one baffle plate (8) with respect to the vertical; the crusher (1) being characterized in that said supporting members (9) comprise at least one linear hydraulic actuator (14) , in turn comprising a hydraulic jack (23) , which has a hollow cylindrical body (24) extending coaxially with a first longitudinal axis (C) , a piston (26) mounted to slide axially inside the longitudinal cavity of said hollow cylindrical body (24) , so as to divide said cavity into a first (24a) and a second (24b) variable-volume chamber complementary with each other, and a movable rod (25) inserted partly and in axially-sliding manner inside said hollow cylindrical body (24) , so as to be fixed rigidly to said piston (26) ; said first variable-volume chamber (24a) reducing its volume alongside an increase in the tilt angle of said baffle plate (8) with respect to the vertical; and said linear hydraulic actuator (14) also comprising a relief device (32) permitting selective outflow of pressurized fluid from said first variable- volume chamber (24a) when the pressure of the fluid inside the first variable-volume chamber exceeds a predetermined first threshold value, and a variable- volume pressurized-fluid storage tank (33) for receiving a variable quantity of pressurized fluid from said first variable-volume chamber (24a) when the pressure of the fluid in the first variable-volume chamber exceeds a predetermined second threshold value lower than said first threshold value.
2) A crusher as claimed in Claim 1, characterized in that said supporting members (9) also comprise at least one length-adjustable anchoring tie (13) mechanically connecting said baffle plate (8) to the outer casing (2) of the crusher.
3) A crusher as claimed in Claim 2, characterized in that said at least one anchoring tie (13) and said at least one linear hydraulic actuator (14) are located side by side and substantially parallel to each other. 4) A crusher as claimed in Claim 2 or 3, characterized in that said at least one anchoring tie (13) comprises a connecting rod (15) which has one of its two ends hinged to said baffle plate (8) , and which extends through a first opening (16) , formed in the outer casing (2) , so as to project partly outside said outer casing (2) ; and a mechanical stop member (17) fixed adjustably to the end portion of said connecting rod (15) projecting outside said outer casing (2) , so as to rest on the surface of the outer casing (2) to prevent complete withdrawal of the connecting rod (15) inside the outer casing (2) .
5) A crusher as claimed in Claim 4, characterized in that said mechanical stop member (17) comprises a locating bush (18) positioned on the outer casing (2) of the crusher, at the first opening (16) , so as to fit in axially-sliding manner onto the end portion of said connecting rod (15) projecting outside said outer casing (2) through said first opening (16) ; said locating bush (18) having a central through hole, whose end portion, facing away from said first opening (16) , is flared to form a spherical-bowl-shaped cavity or seat (18a) .
6) A crusher as claimed in Claim 5, characterized in that said mechanical stop member (17) also comprises a spherical-bowl-shaped stop bush (21) fitted rigidly and adjustably to said connecting rod (15) , so as to rest on said spherical-bowl-shaped cavity or seat (18a) on the locating bush (18) to form a spherical joint. 7) A crusher as claimed in Claim 6, characterized in that said mechanical stop member (17) comprises a cylindrical tubular sleeve (20) screwed to the end portion of said connecting rod (15) ; said stop bush (21) being fitted rigidly to said cylindrical tubular sleeve (20) .
8) A crusher as claimed in any one of the foregoing Claims, characterized in that said hydraulic jack (23) has two pressurized-fluid feed passages (23a) , by which pressurized fluid is fed to or drawn from said first
(24a) and said second (24b) variable-volume chamber; and in that said supporting members (9) comprise on-off valves for regulating pressurized-fluid flow to and from said feed passages (23a) .
PCT/IB2005/003003 2004-10-12 2005-10-11 Rotary crusher for rubble and similar WO2006040641A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
ITTO20040705A1 ITTO20040705A1 (en) 2004-10-12 2004-10-12 Machine crushing rubble and related to rotating mass
ITTO2004A000705 2004-10-12

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2037104A1 (en) * 1970-07-27 1972-02-03
US4729517A (en) * 1985-07-13 1988-03-08 O&K Orenstein & Koppel Aktiengesellschaft Rebound crusher
EP0728524A1 (en) * 1995-02-22 1996-08-28 SBM WAGENEDER Gesellschaft m.b.H. Impact crusher

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2037104A1 (en) * 1970-07-27 1972-02-03
US4729517A (en) * 1985-07-13 1988-03-08 O&K Orenstein & Koppel Aktiengesellschaft Rebound crusher
EP0728524A1 (en) * 1995-02-22 1996-08-28 SBM WAGENEDER Gesellschaft m.b.H. Impact crusher

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