RU2576449C1 - Cone slugged crusher with advanced balancer - Google Patents

Abstract

FIELD: manufacturing technology.

SUBSTANCE: crusher can be used in the construction and mineral processing industries. Crusher provides a simply supported on base 9 through elastic shock body 1 with outer cone 2 and placed inside spherical bearing 4 inner cone 3. On drive shaft 5 of internal cone 3 through the sliding sleeve with the possibility of adjusting the center of gravity relative to rotational axis 6 is eccentric weight. Bushing sliding unbalance 12 is connected through ball-supporting compensating sleeve 20 with toothed wheel 16 connected with the motor gear. Ball bearing compensation coupling 20 comprises upper 21 and lower 23 half-coupling. Lower half-clutch 23 via slide bearing support 22 is mounted inside the simply supported on flange 15 balancer rotation axis 11, which with the help of sliding sleeve 19 mounted balancer 11. Thus balancer 11 is rigidly connected to gear wheel 16 and with lower coupling half 23 so as to form balancer 11, gear 16, lower half coupling 23 and sliding sleeve 19 of balancer single mobile node 11, the flange is rigidly fixed in the bottom of housing 1 of the crusher.

EFFECT: in the crusher balancer provides dynamic stabilization, which allows to reduce the height of the crusher, to increase the degree of fragmentation.

10 cl, 6 dwg

Description

The invention relates to the field of heavy engineering, to crushing grinding equipment, in particular to cone crushers, and can be used in technological processes in the construction and mining and processing industries.

The crushing units currently in use are structurally difficult to create and labor-intensive in operation. Therefore, one of the most pressing problems is the possibility of creating a design that has both excellent performance and at the same time ease of operation and maintenance.

An inertial cone crusher is known in the art. The design of the crusher comprises a housing with an outer cone and an inner cone placed inside it, the surfaces of which face each other form a crushing chamber. On the drive shaft of the inner movable cone there is an unbalance driven into rotation by the transmission unit. When the unbalance rotates, a centrifugal force is created, forcing the inner cone to run around the outer cone without a gap if there is no recyclable material in the crushing chamber (at idle speed); or through a layer of crushed material.

However, the large value of the centrifugal force created by the unbalance and leading to an increase in crushing force, at the same time leads to a disturbance in the dynamic equilibrium and to an increase in vibration loads on all elements of the crusher, especially on the casing. This in turn leads to the need to increase the strength characteristics of the housing, such as wall thickness, the strength of shock absorbers, the strength of the foundation on which the housing is mounted, drive elements and other parts.

The mentioned problem of dynamic balancing is solved by introducing counterbalance into the design of the crusher, that is, an additional unbalanced unbalance established in antiphase to the unbalance, generating its own centrifugal force directed opposite to the centrifugal forces of the inner cone and its unbalance.

Thus, the provision of dynamic balancing of the crusher, that is, the creation of such working conditions when the sum of all the forces and moments acting in it would be close to zero, is the main issue in creating a reliable effective design.

The theory of dynamic calculation of crushers is described in special literature, for example, “Vibratory crushers”, L. Vaysberg And others, VSEGEI Publishing House, St. Petersburg, 2004, ISBN 93761-061-X, Chapter 6 “Dynamics of an inertial cone crusher with an additional vibrator on the body”, p. 103, [1].

Known invention "Inertial cone crusher" RU 2174445, which is one of the effective solutions to the problem of dynamic balancing of the crusher.

According to this invention, in an inertial cone crusher containing a housing with an outer cone supported on a foundation through elastic shock absorbers and an inner cone placed inside it on a spherical support, on the shaft of which a drive unbalanced rotor is mounted with a bearing with the possibility of adjusting its center of gravity relative to the axis of rotation connected through a ball support and compensation coupling and through an intermediate shaft located in the bearings of the housing with a drive pulley and motor; in which the rotor bearing housing and the pulley housing are made with cylindrical surfaces eccentric with respect to the axis of rotation, the pulley is provided with an unbalanced load and said unbalanced loads are also made eccentric and mounted with the possibility of complete rotation on the reciprocal eccentric cylindrical surfaces of the rotor bearing and pulley and the possibility of fixing them in the necessary position relative to the eccentricity of the mentioned surfaces and each other.

The invention is known as “Inertia cone crusher and method of balancing such crusher”, WO 2012/005650 A1, priority data 09.07.2010, SE 20100050771.

According to this invention, the known construction of an inertial cone crusher comprises a housing, an external cone, an internal cone, on which a unbalance is mounted on a vertical shaft; and a system of counterbalances consisting of two separate parts. One part of the counterbalance is mounted on the intermediate drive shaft below the sliding bearing and is located below the outside of the crusher body, while the second part of the counterbalance is attached to the intermediate drive shaft above the sliding bearing and is located inside the crusher body. The total total weight of both counterbalances and the weights of each are calculated in such a way that they correspond to those required to create the necessary centrifugal force and to solve the problem of matching and dynamically balancing the unbalance and the counterbalance.

This technical solution allows you to resolve a wide range of aspects of the dynamic balancing of the crusher by changing the ratio of the weights of the counterbalance parts, their relative position and their relative position with unbalance. An important advantage of the double distribution of counterbalance weights is that the loads on the intermediate drive shaft are reduced and distributed more evenly, therefore, the service life of the drive unit increases.

The main disadvantage of both of the technical solutions described above is the location of the lower counterbalance at a level that is significantly lower than the bottom of the housing, under which in turn there is a pulley drive shaft and the drive pulley itself. The engine can be connected, for example via a V-belt drive, to a pulley. Based on this design, it is necessary to provide access to the crusher strictly from below, in the area located below the housing, to place the actual unbalance, the pulley and its shaft, the drive, the engine itself, and also to provide an access area for adjustments and maintenance.

This requirement can be achieved either by lifting the entire structure of the body to a certain height, or by creating a large discharge chute. Consequently, the overall design height of the crushing unit increases significantly and, as a result of this, the height of the entire processing chain that delivers the initial crushed material to the upper feed hopper increases.

In addition, the output of the finished product is also carried out in the area located directly under the housing and below the level of the housing, and the combination of the service area and the unloading zone of the finished product complicates the work of maintenance personnel.

Significant disadvantages of the double anti-imbalance system are obviously the double cost of its manufacture, additional costs for installation, adjustment and maintenance. It is also necessary to provide a special space inside the housing to accommodate the internal counterbalance, which further increases the height of the housing.

For any crushing unit, the height of the casing is an important and critical parameter, which should be kept within specified limits, if possible, and at best reduced as much as the design allows.

Based on the foregoing, the objectives of the present invention is to modernize the design, increase the reliability of the design of the crusher and simplify its maintenance due to the fact that:

- all moving parts of the unit must be located strictly inside the housing,

- service should be carried out only on top of the housing,

- The overall height of the structure should be reduced.

The goal can be achieved by improving the problem of providing dynamic balancing of the crusher.

One of the possible ways to improve the dynamic balancing of the crusher is to create an improved design of the counterbalance unit, which must simultaneously meet the following requirements:

- create the required value of the centrifugal force, compensating for the centrifugal force generated by the unbalance;

- the location of the counterbalance should not require a special equipped area located under the crushing unit, and should not be combined with the unloading area of the finished material;

- the place of placement of the counterbalance should be as close as possible to the place of placement of the unbalance to optimize the dynamic balance, that is, the node must be placed inside the existing crusher body;

- the method and location of the counterbalance should not increase the overall dimensions of the crushing unit in height or in width;

- the unit must have a reliable and simple design, at least not leading to an increase in the cost of the crusher;

- the design should contribute to the simplification, acceleration and cheapening of the service maintenance of the crusher.

The tasks are solved in an inertial cone crusher, which contains:

a housing with an outer cone supported on a foundation through elastic shock absorbers and an inner cone placed inside it on a spherical support,

on the drive shaft of which with the help of the sliding sleeve there is an unbalance with the possibility of adjusting its center of gravity relative to the axis of rotation,

the unbalance slip sleeve is connected via a ball support and compensation coupling to a gear connected by a gear to the engine,

while the ball support and compensation coupling includes upper and lower coupling halves.

In accordance with the present invention:

the lower coupling half is mounted through the plain bearing on the inside of the anti-unbalance rotation axis supported on the flange, onto which the anti-unbalance is installed using the sliding sleeve,

wherein the anti-imbalance is rigidly connected to the gear and the lower coupling half in such a way that the said anti-balance, the gear, the lower coupling half and the sliding sleeve form a single movable "anti-imbalance unit",

and the flange is rigidly fixed to the bottom of the crusher body.

The crusher additionally has the following characteristics.

The axis of rotation of the counterbalance is made in the form of a hollow cylindrical glass with an oil-conducting hole in the center of the bottom, the inner diameter of the glass is equal to or greater than the outer diameter of the lower coupling half.

The flange is made in the form of a stepped disk with a central mounting hole, the diameter of which is made equal to the outer diameter of the axis of rotation of the counterbalance, has mounting holes along the edges of the disk.

The axis of rotation of the counterbalance and the flange can be made as a single part.

The mounting holes along the edges of the flange are designed so that the heads of the mounting bolts are completely recessed into the aforementioned mounting holes.

The plain bearing is made in the form of two disks with oil-conducting holes in the center.

The mounting holes of the counterbalance coincide with the mounting holes of the gear wheel, coincide with the mounting holes of the lower coupling half.

The anti-imbalance in the first embodiment is made in the form of a disk segment, in the center of which there is a mounting hole equal to the outer diameter of the anti-unbalance slide sleeve, along the edges of which are mounting holes, the upper surface of the disk has two rectangular lowering ledges, the lower surface of the disk has a figured shape installation fixture of the flange, the end is rounded off from the bottom edge.

The anti-imbalance in the second embodiment is made in the form of a disk segment, in the center of which there is a mounting hole equal to the outer diameter of the anti-unbalance slide sleeve, along the edges of which there are mounting holes, the upper surface of the disk has one rectangular lowering ledge, the lower surface of the disk has a conical ledge made for installation flange fasteners.

As an embodiment, the anti-imbalance has two installation end flats.

The essence of the present invention is illustrated by drawings.

In FIG. 1 is a cross-sectional diagram of an inertial cone crusher.

In FIG. Figure 2 presents a separate crusher assembly linking unbalance and anti-imbalance, indicating the forces and moments acting on them.

In FIG. Figures 3 and 4 show the anti-imbalance in two versions in the form of a three-dimensional drawing, as well as in the form of a sectional drawing.

In FIG. 5 and 6 show the anti-imbalance with additional installation end faces in two versions in the form of a volumetric drawing, as well as in the form of a sectional drawing.

The invention is structurally implemented as follows.

The housing (1) is mounted on the foundation (9) through elastic shock absorbers (10). The external crushing cone (2) and the internal crushing cone (3) placed on the spherical support (4) form a crushing chamber between them. An unbalance unit (6) is installed on the shaft (5) of the inner cone (3), which consists of the unbalance itself mounted on the unbalance sleeve (12), which is mounted on the shaft (5) with the possibility of rotation around it.

The unbalance unit (6) is connected by a ball support and compensation coupling (20) with a gear wheel (16) through the upper coupling half (21) and the lower coupling half (23).

The coupling half (23) is placed inside the axis of rotation of the counterbalance (15), which is made in the form of a hollow cylindrical cup with an oil-conducting hole in the center of the bottom. The coupling half (23) is supported by a plain bearing (22), which is made in the form of two thin disks with oil-conducting holes in the center.

The anti-imbalance (11) is mounted on the sliding sleeve (19) by the press fit method, and the sleeve (19), in turn, is mounted on the axis of rotation of the anti-balance (15) with the possibility of rotation around it.

The axis of rotation (15) is supported on the flange (34), which is made in the form of a stepped disk with a central mounting hole and is rigidly fixed to the bottom of the housing (1) using fixing bolts (32) located around the perimeter of the flange disk.

The anti-imbalance (11) is rigidly connected to the gear wheel (16) and to the coupling half (23) through the mounting holes (24) by means of fixing bolts. Thus, the “anti-imbalance unit”, which includes the actual anti-imbalance (11), the gear wheel (16), the lower coupling half (23) and the sliding sleeve (19), form a single moving unit, all of whose elements are rigidly connected to each other by means of fixing bolts and press fit.

The movable “counterbalance unit”, in turn, is mounted rotatably on the fixed axis of rotation (15), which is either supported on the flange (34) or made as a solid axle-flange part.

The movable “anti-imbalance unit” is mounted in such a way that the anti-imbalance (11) is always in antiphase to the unbalance (6).

The pipe (8), the oil-conducting channel (7) of the axis of rotation (15), the oil-conducting holes in the disks of the plain bearing (22), the oil-conducting channel in the support spherical spindle of the coupling (20) form a common oil-conducting channel.

The invention works as follows.

From the engine (18) through an external coupling (17), the torque is supplied to the gear transmission: the shaft - gear (25) and gear wheel (16). The gear wheel (16) rotates the “anti-imbalance unit”, which also includes anti-imbalance (11), the sliding sleeve (19) and the lower coupling half (23).

The movable “counterbalance unit” rotates around the axis of rotation (15), so that the inner diameter of the slide sleeve (19) and the outer diameter of the axis of rotation (15) form a counterbalance slip bearing.

The coupling half (23) is an element of the ball joint-compensation coupling (20), which transmits torque through the ball spindle and the upper coupling half (21) to the unbalance unit: unbalance (6) and the unbalance slip sleeve (12) mounted on the shaft (5) of the internal cone (3).

The unbalance unit develops centrifugal force, the inner cone (3) comes into motion and performs a run-in along the outer cone (2) acting on crushed material in the crushing chamber.

FIG. 2 illustrates in detail the design of the "counterbalance unit" and the principles of its operation.

The vector F ₁ conditionally represents the centrifugal force developed by the unbalance, CG ₁ - the center of gravity of the unbalanced mass G ₁ unbalance; R ₁ is the radius of rotation of the center of gravity of the unbalanced mass of unbalance, in other words, the distance by which the center of gravity of its unbalanced mass is removed from the axis of symmetry of the shaft (5).

The vector F ₂ conditionally represents the centrifugal force developed by the anti-imbalance, CG ₂ is the center of gravity of the unbalanced mass G _{2 of the} anti-imbalance; R ₂ is the radius of rotation of the center of gravity of the unbalanced mass of unbalance, in other words, the distance by which the center of gravity of its unbalanced mass is removed from the central axis of the crusher.

According to the theory of dynamic stabilization [1], the full dynamic balancing of the crusher is achieved when the sum of the (centrifugal) forces and moments acting in it crushes to zero. Accordingly, the closer to each other the centers of gravity of the unbalanced mass of the unbalance CG ₁ and the anti-unbalance CG _{2 are located} , the smaller the centrifugal force F ₂ is required to develop the anti-imbalance (11) to compensate for the centrifugal force F ₁ developed by the unbalance (6).

Therefore, to achieve the goals in this invention, the “anti-imbalance unit” not only moves from under the casing (1) into its limits, but is also installed as close to the unbalance (6) inside the crusher casing (1) as the unit design allows.

The centrifugal force F1 unbalance (6) is determined by the formula:

[1] $$F_{\text{one}}=G_{\mathrm{one}}{R}_{\text{one}}{\left(\frac{\text{πn}}{\text{thirty}}\right)}^{\text{2}}$$

[one]

where F ₁ is the centrifugal unbalance force, N;

G ₁ - unbalanced mass of unbalance, kg;

R ₁ is the radius of rotation of the center of gravity of the unbalanced mass of unbalance, m;

π = 3.14;

n is the unbalance rotation speed, rpm

The centrifugal force F ₂ anti-imbalance (11) is determined by the formula:

[2] $${\mathrm{<figure-callout\; id="2"\; label="F"\; filenames="00000004.png"\; state="\{\{state\}\}">F</figure-callout>}}_{\text{2}}=G_2{R}_{\text{2}}{\left(\frac{\text{πn}}{\text{thirty}}\right)}^{\text{2}}$$

[2]

where F ₂ is the centrifugal force of the anti-imbalance, N;

G ₂ - unbalanced mass counterbalance, kg;

R ₂ is the radius of rotation of the center of gravity of the unbalanced mass of the unbalance, m;

π = 3.14;

n - anti-unbalance rotation speed, rpm, is equal to the unbalance rotation speed.

According to [2], the centrifugal force F ₂ is greater, the larger the radius R _{2 of} rotation of the center of gravity of the unbalanced mass of unbalance, in other words, the distance by which the center of gravity CG _{2 is} removed from the central axis of the crusher. The proposed anti-imbalance is designed so that the parameter R ₂ was the maximum possible for a given profile of the housing (1).

The center of the vertical generatrix of the counterbalance sliding bearing formed by the sliding sleeve (19) and the axis of rotation (15) is indicated in FIG. 2 as a CFB point.

The anti-imbalance design (11) is designed so that the center of gravity CG _{2 of} its unbalanced mass is located exactly in the center of the vertical generatrix of the sliding bearing. In other words, the points CG ₂ and CFB must be located at the same level. If the height dimension of the vertical generatrix of the plain bearing is taken to be “a,” then the distance from the top edge of the plain bearing to the point CFB and the distance from the point CFB to the bottom edge of the plain bearing are equal to each other and equal to ½ a.

In this case, the load on the sliding bearing is distributed evenly, therefore, there is no skew load, therefore, the wear of the friction surfaces of the bearing occurs evenly, therefore, the bearing lasts longer.

In the case where the center of gravity of the CG _{2 is} shifted relative to the CFB point above or below, the load on the bearing is distributed unevenly, respectively, above or below the central point of the CFB, that is, the load is skewed, therefore, the bearing undergoes asymmetric wear of the friction surfaces, therefore it leaves faster out of service.

Based on the tasks mentioned above, anti-imbalance (11) can be constructively performed in two versions.

The first embodiment is shown in FIG. 3, is made in the form of a disk segment, in the center of the disk there is a mounting hole (13) equal to the outer diameter of the sliding sleeve (19), along the edges of which are mounting holes (24). The upper surface of the anti-imbalance disk has two rectangular lowering ledges (26), the lower surface of the disk has a figured selection (28), made strictly according to the shape of the mounting fixture (32) of the flange (34), the end of the disk is rounded from the bottom edge (14), repeating the inner body profile (1).

The complex form of the first version of the counterbalance is due to a compromise between the design of the internal profile of the housing (1), in other words, the free space that is allocated to accommodate the counterbalance without changing the parameters of the housing, and the required characteristics of the actual anti-balance.

The advantage of this option is the maximum use of the housing space (1) with anti-unbalance parameters close to the optimal design ones. The disadvantage of this option is the high cost of execution of this form of the part.

A second variant of counterbalance is shown in FIG. 4 is also made in the form of a disk segment, in the center of the disk there is a mounting hole (13) equal to the outer diameter of the sliding sleeve (19), along the edges of which are mounting holes (24), the upper surface of the disk has two rectangular lowering ledges (26), the lower surface of the disk has a lowering conical ledge (29), made under the mounting fixture (32) of the flange (34).

The form of the second version of the counterbalance is a modified form of the first option and a compromise between the requirements for compliance with the design characteristics and the requirements for reducing the cost of manufacturing parts, since the option has a simpler configuration.

The advantage of this option is the lower cost of manufacturing the part, as is known from the prior art, the simpler the part, the cheaper it is to manufacture; and the disadvantage is a deviation from the best design characteristics.

Any of the mentioned anti-imbalance options may have two end flats (27), the designs are shown in FIG. 5 and 6, located on both sides of the disk, which are designed to facilitate the installation of counterbalance in the case when the required design diameter of the counterbalance disk is larger than the mounting openings of the case of this unit size.

As an embodiment, the method of fastening the flange (34) in the bottom of the housing (1) can be modified so that the bolt heads (32) are recessed into the mounting holes along the edges of the flange (34), FIG. 4 and 6.

As an embodiment, the rotation axis (15) and the flange (34) can be made as a single part. The advantage of such a solution is a significant improvement in the strength characteristics of the “anti-imbalance unit”, since details (15) and (34) have a significant dynamic load. The disadvantage of this option is the increase in the cost of manufacturing a single part and the cost of its installation.

Through the pipe (8), the oil-conducting channel (7) of the rotation axis (15), the oil-conducting holes in the disks of the plain bearing (22) and the oil-conducting channel in the supporting spindle of the coupling (20), oil is supplied to all friction surfaces of the crusher.

Compared with the solutions known from the prior art, the implementation of the claimed design of the crusher will allow, as indicated above, to significantly improve the dynamic balancing of the unit with the existing overall dimensions of the casing. In addition, it will make it possible to work at high engine speeds, which, according to [1], will lead to an increase in crushing force and, in turn, can lead to an increase in the degree of crushing by 10-15%.

The vertical size of the proposed design of the crusher is smaller than the corresponding size of analogues, primarily due to the movement of the “counterbalance unit” inside the unit’s body, and also due to the improvement of the counterbalance design itself, which allows more efficient distribution of its mass and use of the internal space of the casing, therefore, greater efficiency with less material cost.

As a result of this, the overall height of the crushing unit can be reduced by about 20% of the original height with the same sizes.

The zone located below the level of the crusher body is freed from the counterbalance unit and other drive parts, therefore there is no need to increase the discharge heat zone, there is no need to provide “lower access” for after-sales service: for the proposed design, after-sales service is carried out only from above, which is more pragmatic. The total savings in the cost of manufacturing the proposed design, depending on the chosen option, can be from 5 to 10%.

All original parts of the crushing unit proposed in the present invention can be made by any methods known in the art, such as casting, waterjet or plasma cutting and the like.

Claims (10)

1. An inertial cone crusher containing a housing with an outer cone supported on a foundation through elastic shock absorbers and an inner cone placed inside it on a spherical support, on the drive shaft of which an unbalance is located with the help of a sliding sleeve with the ability to adjust its center of gravity relative to the axis of rotation, unbalance sliding sleeve connected through a ball support and compensation coupling to a gear connected by a gear to the engine, while the ball support and compensation coupling includes upper and lower half-coupling, characterized in that the lower half-coupling is mounted through a support sliding bearing inside the anti-unbalance axis of rotation that is supported on the flange, onto which an anti-imbalance is installed using the sliding sleeve, while the anti-unbalance is rigidly connected to the gear wheel and to the lower half-coupling in such a way that the anti-imbalance, the gear wheel, the lower coupling half and the sliding sleeve form a single movable anti-imbalance unit, and the flange is rigidly fixed in the bottom of the crusher body. 2. Inertial cone crusher according to claim 1, characterized in that the axis of rotation of the counterbalance is made in the form of a hollow cylindrical cup with an oil-conducting hole in the center of the bottom, the inner diameter of the cup is equal to or greater than the outer diameter of the lower coupling half. 3. The inertial cone crusher according to claim 1, characterized in that the flange is made in the form of a stepped disk with a central hole, the diameter of which is made equal to the outer diameter of the axis of rotation of the counterbalance, which has mounting holes on the edges of the disk. 4. The cone inertial crusher according to claim 1, characterized in that the axis of rotation of the counterbalance and the flange are made as a single part. 5. The cone inertial crusher according to claim 1, characterized in that the mounting holes along the edges of the flange are made so that the heads of the mounting bolts are completely recessed into the said mounting holes. 6. Inertial cone crusher according to claim 1, characterized in that the pillow block bearing is made in the form of two disks with oil-conducting holes in the center. 7. Cone inertial crusher according to claim 1, characterized in that the mounting holes of the counterbalance coincide with the mounting holes of the gear wheel, coincide with the mounting holes of the lower coupling half. 8. The cone inertial crusher according to claim 1, characterized in that the counterbalance is made in the form of a disk segment, in the center of which there is a mounting hole equal to the outer diameter of the counterbalance slip bush, along the edges of which are mounting holes, the upper surface of the disk has two rectangular lowering ledges , the lower surface of the disk has a figured selection made according to the shape of the mounting fixture of the flange, the end face is rounded from the lower edge. 9. The inertial cone crusher according to claim 1, characterized in that the counterbalance is made in the form of a disk segment, in the center of which has a mounting hole equal to the outer diameter of the counterbalance slip bush, along the edges of which are mounting holes, the upper surface of the disk has two rectangular lowering ledges , the lower surface of the disk has a lowering conical ledge made under the mounting hardware of the flange. 10. Cone inertial crusher according to claim 1, characterized in that the anti-imbalance has two installation flats.

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