JP2007038146A - Jaw crusher - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a simply structured jaw crusher capable of effectively crushing a variety of materials to be crushed and easily removing a hard foreign matter such as a metal lump. <P>SOLUTION: The jaw crusher crushes materials to be crushed charged in between a stationary tooth 35 fixed to a frame 31 constituting the jaw crusher main body and a movable tooth 34 rockably disposed to face the stationary tooth 35. The jaw crusher is equipped with a toggle plate 41 that supports the movable tooth 34 with its one end Q connected to the lower part 34b of the movable tooth 34 to form a fulcrum point of its rocking motion, an arm block 43 configured so as to be able to rotate around a pin 44 as its center axis with its one end connected to the other end P of the toggle plate 41 and its middle part pivotally supported by means of the pin 44 on the frame 31, and a first hydraulic cylinder 45 capable of causing the arm block 43 to rotate with its one end connected to the other end of the arm block 43. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a jaw-type crushing apparatus that can handle various objects to be crushed by adjusting the swing trajectory of the tip of a movable tooth.

Conventionally, self-propelled, equipped with a jaw crusher (jaw crusher) as a work machine that handles and recycles construction waste such as rocks generated in civil engineering work, earth and sand, concrete glass and asphalt glass generated in construction work. A type crusher is known.
As shown in FIG. 5, the self-propelled crusher 1 is disposed below the jaw crushing device 10 and a jaw crushing device 10 that crushes rocks and construction waste materials (hereinafter referred to as a material to be crushed) finely. The crawler type traveling device 2, the supply device 3 for supplying the object to be crushed into the jaw type crushing device 10, and the discharging device 4 for discharging the object to be crushed by the jaw type crushing device 10 to the outside. And.

  As shown in detail in FIG. 6, the jaw type crushing device 10 is a compression type that is provided with two pressing plate members of a movable tooth 11 and a fixed tooth 12 facing each other so as to expand upward. The crushing device is such that the fixed tooth 12 is fixed to the frame 13, while the movable tooth 11 provided relative to the fixed tooth 12 is pivotally supported by the frame 13 via the rotating shaft 14, The lower part is connected to the frame 13 via a toggle block 15 and a toggle plate 16.

  Then, the flywheel 17 is driven via a belt by a hydraulic motor (not shown), the upper part of the movable tooth 11 eccentrically attached to the rotating shaft 14 rotates eccentrically, and the lower part of the movable tooth 11 is supported by the toggle plate 16. Therefore, the movable tooth 11 is oscillated (moved) while drawing an elliptical locus in a direction in which the lower end (tip) of the movable tooth 11 is in contact with and away from the fixed tooth 12, and crushing between the movable tooth 11 and the fixed tooth 12 is performed. The object to be crushed between the chambers 10a can be crushed by applying a compressive force.

  The movable teeth 11 and the fixed teeth 12 are closest to each other at the lower ends, and the maximum size after crushing of the material to be crushed that is sandwiched between the crushing chambers 10a and crushed (that is, the particle size after crushing) is It is determined according to the minimum dimension (hereinafter referred to as the outlet dimension) W of the gap at the lower end of the movable tooth 11 and the fixed tooth 12. For this reason, the exit dimension W can be arbitrarily set so that a desired particle size can be obtained after crushing.

  The exit dimension W is set by adjusting the position of the movable tooth 11 with respect to the lower frame 13. For example, a plate between the toggle block 15 connected to the lower back of the movable tooth 11 and the frame 13 is used. This is done by inserting a shaped shim 22. Specifically, the hydraulic cylinder 18 connected to the toggle block 15 is extended to move the toggle block 15 to the movable tooth 11 side, the number of shims 22 to be inserted is adjusted, and the position of the sheet 19 that receives the toggle plate 16 is determined. The exit dimension W is set. In order to prevent the toggle plate 16 from falling off when the shim 22 is attached / detached, the rod 21 is fixed to the frame 13 via the spring 20 at one end and fixed to the lower portion of the movable tooth 11. Thus, the movable teeth 11 are drawn toward the sheet 19 side.

  By the way, the jaw crushing apparatus 10 is a soft and hard type of a soft crushed object such as asphalt (hereinafter referred to as a soft material) and a hard crushed object such as rock or concrete (hereinafter referred to as a hard material). It is not suitable for crushing the object to be crushed with a single unit. This is because the jaw crushing device 10 has been developed mainly for crushing hard materials. When the jaw crushing device 10 tries to crush soft materials, the soft materials are appropriately crushed. This is because they are not crushed or become sticky and adhere between the teeth of the movable teeth 11 and the fixed teeth 12 and do not fall from the crushing chamber 10a toward the discharge port 10c.

On the other hand, it is known that the crushing ability of a hard object increases or the crushing ability of a soft object increases by changing the elliptical swing locus of the tip of the movable tooth 11. Such a technique is disclosed in Patent Document 1, for example.
In Patent Document 1, the angle of the movable tooth tip is changed by changing the mounting angle of the toggle plate with respect to the horizontal plane, and a single jaw crusher can handle both soft and hard crushed objects. ing.
JP-A-9-187668

However, according to the technique described in Patent Document 1, it is possible to change the trajectory of the swing, and it is possible to cope with the crushing of various objects to be crushed, and the productivity is improved. There is a problem that the structure for changing the mounting angle is complicated.
In addition, according to the jaw type crushing device such as the mechanism described in the technology described in Patent Document 1 and the background art, when a hard foreign object such as a metal lump is sandwiched in the gap between the movable tooth and the fixed tooth, it is mechanically movable. Since it is difficult to open the teeth, it is difficult to remove foreign matter, and there is a problem that productivity is reduced due to long-time foreign matter removal work.

This problem will be described with reference to the jaw crusher 10 shown in FIG.
The jaw-type crushing device 10 has a frame 13 disposed on the direction side in which the toggle block 15 moves when the gap between the movable tooth 11 and the fixed tooth 12 is expanded with respect to the position where the toggle block 15 is disposed. The shim 22 is sandwiched between the frame 13 and the toggle block 15. In other words, the reaction force against the compressive force that tries to crush the object to be crushed acts in a direction to increase the gap (exit size W) between the movable tooth 11 and the fixed tooth 12, and therefore the reaction force Each element is arranged so that force can be received by the frame 13 via the toggle block 15 and the shim 22 so that the object to be crushed can be effectively crushed.

  In the case of the structure in which the frame 13 receives a reaction force applied when the object to be crushed is crushed, in order to adjust the exit dimension W of the movable tooth 11 and the fixed tooth 12, it is necessary to narrow the dimension W once. That is, in order to adjust the exit dimension W, it is necessary to widen the space between the frame 13 and the toggle block 15 so that the inserted shim 22 can be replaced and detached. Must be moved to the side. Therefore, it is difficult to remove and replace the shim 22 in the state where the object to be crushed is in the gap between the movable tooth 11 and the fixed tooth 12.

  However, when crushing concrete glass, a metal lump may be mixed in the concrete glass. Since the metal lump in the concrete glass is not crushed by the compressive force of the jaw crushing device 10, it bites into the gap between the movable tooth 11 and the fixed tooth 12 and stops the swinging reciprocating motion of the movable tooth 11. (Jaw type crushing device 10) may stop. Therefore, in this case, the exit dimension W of the movable tooth 11 and the fixed tooth 12 cannot be increased or decreased, and thus it becomes difficult to remove the sandwiched metal mass.

  Similarly to the jaw-type crushing device 10 of the general mechanism shown in FIG. 6, even with the technique described in Patent Document 1, there is a state where the exit dimension W of the movable tooth 11 and the fixed tooth 12 cannot be increased or decreased. It is thought that it will be difficult to get rid of the metal block that is generated and pinched.

  The present invention has been made in view of such a problem, and it is possible to easily remove various foreign objects to be crushed with a simple configuration and to easily remove hard foreign matters such as a metal lump. An object is to provide a jaw type crushing apparatus.

  In order to achieve the above object, the jaw type crushing device of the present invention according to claim 1 is capable of swinging in a direction in which the fixed teeth fixed to a frame forming the main body of the device are in contact with and away from the fixed teeth. A jaw-type crushing device that has movable teeth arranged opposite to each other, and crushes the object to be crushed between the fixed teeth and the movable teeth by the swinging, and has one end portion of the movable teeth A toggle plate that supports the movable tooth, and one end of the toggle plate is engaged with the other end of the toggle plate, and an intermediate portion of the toggle plate with respect to the frame. An arm block that is pivotally supported via a pin and is configured to be rotatable about the pin as a central axis, and one end of the arm block is connected to the other end of the arm block so that the arm block can be rotated. With 1 hydraulic cylinder It is characterized in that.

According to a second aspect of the present invention, there is provided the jaw type crushing apparatus according to the first aspect, wherein the jaw block is formed between the concave portion formed at the one end of the arm block, the bottom surface of the concave portion, and the toggle plate. And a plurality of shim plates that are detachably inserted and are capable of adjusting a gap between lower ends of the movable teeth and the fixed teeth.
According to a third aspect of the present invention, there is provided a jaw type crushing device according to the first or second aspect, wherein the first hydraulic cylinder has a hydraulic pressure equal to or higher than a predetermined pressure. A relief valve for releasing hydraulic oil inside one hydraulic cylinder is provided.

  The jaw type crushing device according to a fourth aspect of the present invention is the jaw type crushing device according to any one of the first to third aspects, wherein one end of the jaw type crushing device is connected to a lower portion of the movable tooth, A second hydraulic cylinder having the other end connected to the other end is provided, and the second hydraulic cylinder has a built-in spring that biases the stroke in a direction to reduce the stroke.

  According to the jaw type crushing apparatus of the present invention, the arm block can be swung by changing the stroke of the first hydraulic cylinder to change the connecting position between the toggle plate and the arm block. . Since this connection position is one swing fulcrum of the toggle plate, the mounting angle of the toggle plate is changed, and the tip of the movable tooth supported by the toggle plate is engaged with one end of the toggle plate. The movement trajectory is changed. Therefore, since the swing locus of the tip of the movable tooth can be changed, various objects to be crushed can be crushed well, and productivity can be improved.

In addition, since one swing fulcrum of the toggle plate can be adjusted by the expansion and contraction of the stroke of the first hydraulic cylinder, the swing locus of the tip of the movable tooth can be easily changed with a simple configuration.
Further, the gap between the movable tooth and the fixed tooth can be expanded by extending and contracting the stroke of the first hydraulic cylinder and rotating one end portion of the arm block in a direction away from the fixed tooth. Accordingly, it is possible to easily remove hard foreign matters such as a metal lump that are difficult to crush and cause the apparatus to stop.

  According to the jaw type crushing apparatus of the present invention, the size of the gap between the movable tooth and the fixed tooth can be adjusted by changing the number and thickness of the shim plates inserted into the recesses of the arm block. it can. Therefore, the particle size of the object to be crushed can be changed. At the same time, since the position of the toggle plate with respect to the fixed tooth can be changed in the front-rear direction by inserting the shim plate, one swing fulcrum of the toggle plate can be changed in the front-rear direction. It is possible to easily increase the degree of freedom in changing the swing locus.

  According to the jaw type crushing device of the present invention as set forth in claim 3, since the relief valve is provided, when the load pressure acting on the first hydraulic cylinder is equal to or higher than the predetermined pressure, the first hydraulic cylinder expands and contracts. The arm block rotates in a direction away from the fixed teeth, and the gap between the movable teeth and the fixed teeth can be easily expanded with a simpler configuration, which makes crushing difficult and causes the apparatus to stop. Hard foreign matters such as metal lumps can be easily removed. For example, a relief valve is provided for the head side oil chamber, the hydraulic fluid in the head side oil chamber is released, the stroke of the first hydraulic cylinder is shortened, and the movable teeth and fixed teeth can be easily moved with a simpler configuration. The gap can be enlarged.

  According to the jaw type crushing device of the present invention as set forth in claim 4, the stroke of the second hydraulic cylinder is appropriately adjusted so that the urging force for pulling the toggle plate toward the other end of the second hydraulic cylinder is applied, The stroke can be held to prevent the toggle plate from falling off. At the same time, the toggle plate can be prevented from dropping off more effectively by the biasing force of the spring built in the second hydraulic cylinder.

  Further, since the second hydraulic cylinder is connected to the arm block, when the gap between the movable tooth and the fixed tooth is enlarged, the lower part of the movable tooth is moved along with the retreat in the direction away from the fixed tooth of the arm block. Is pulled in a direction away from the fixed tooth, the gap between the movable tooth and the fixed tooth can be easily expanded. Accordingly, it is possible to more easily remove hard foreign matters such as a metal lump that are difficult to crush and cause the apparatus to stop.

Further, the shim plate can be easily attached and detached by extending the stroke of the second hydraulic cylinder and moving the movable tooth in a direction approaching the fixed tooth.
And since the function of shim adjustment and the function of preventing the shim plate from falling off are combined in one hydraulic cylinder called the second hydraulic cylinder, the number of parts can be reduced and the structure can be simplified.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
1 to 4 show a jaw type crushing apparatus according to an embodiment of the present invention. FIG. 1 is a side sectional view, FIG. 2 is a view taken along an arrow A in FIG. 1, and FIG. FIG. 4 is a graph showing the swing locus of the tip of the movable tooth. Note that the same members as those used for the description in the background art will be described with the same reference numerals, and FIG.

The jaw crushing device 30 of the present invention is mounted on the self-propelled crusher 1 shown in FIG. 5 in place of the jaw crushing device indicated by reference numeral 10 described in the background art.
A self-propelled crusher 1 includes a crawler type traveling device 2 and a jaw that is disposed on the traveling device 2 via a gantry frame (not shown) at a substantially central portion in the front-rear direction of the machine body to crush the object to be crushed finely. Type crushing device 30, supply device 3 for supplying the material to be crushed to jaw crushing device 30, and discharge device 4 for discharging the material to be crushed by jaw crushing device 30 to the outside of the apparatus. ing.

  As shown in FIGS. 1 and 2, the jaw crushing device 30 includes a frame 31 as a framework that forms the device main body, a rotating shaft 32 supported by the frame 31, and a hydraulic pump 61 (see FIG. 3) described later. A crushing hydraulic motor (not shown) that is supplied with the discharged pressure oil and rotates, and provided at both ends of the rotary shaft 32, rotate around the rotary shaft 32 based on the driving force generated by the crushing hydraulic motor. The flywheel 33 and the rotary shaft 32 are eccentrically supported by the upper part of the rotary shaft 32, the movable tooth 34 swings as the flywheel 33 rotates, and the fixed fixed to the frame 31 so as to face the movable tooth 34. And teeth 35. 1 and 2, each part of the frame 31 (and its cross-sectional shape, etc.) is shown in various places, but these parts are firmly fixed to each part of the frame 31 integrally formed. These are all shown with the same reference numerals.

Then, the wedge-shaped gap between the movable tooth 34 and the fixed tooth 35 is configured as a crushing chamber 30a, and the object to be crushed is introduced through the supply device 3 from the inlet 30b above the crushing chamber 30a. After being crushed by the swinging of the movable teeth 34 in the crushing chamber 30a, the crushing chamber 30a is discharged toward the discharge device 4 from the lower discharge port 30c.
Here, a fitting part 34 a having a groove 34 b that is recessed in an arc shape is formed in the lower part of the back surface of the movable tooth 34 near the discharge port 30 c. Further, a pair of brackets 34c are formed in the vicinity of the fitting portion 34a.

As a movable tooth tip locus adjusting device for adjusting the swing locus of the tip of the movable tooth 34 (that is, at the discharge port 30c of the movable tooth 34), a toggle plate 41, a toggle seat 42, an arm block 43, and a hydraulic cylinder for arm block. (Hereinafter referred to as an arm cylinder) 45.
Further, as a gap adjusting device that adjusts the size of the gap (exit size) W of the discharge port 30c between the movable tooth 34 and the fixed tooth 35, a plurality of sheets that are inserted in order to adjust the position of the toggle plate 41. And a shim hydraulic cylinder (hereinafter referred to as a shim cylinder) 52 for adjusting the number of shims 51 to be inserted. The shim cylinder 52 also has a function of preventing the toggle plate 41 from falling off, as will be described later.

When describing each member in detail, the toggle plate 41 is a plate-like member formed by protruding both ends 41a, 41b in an arc shape in a side view. The arc-shaped one end portion (movable tooth 34 side end portion) 41 a is pivotally attached to the groove 34 b of the fitting portion 34 a of the movable tooth 34 to support the lower portion of the movable tooth 34.
The toggle sheet 42 is a plate-like member in which an arc-shaped groove 42a is formed at one end (the end portion on the movable tooth 34 side), and the groove 42a and the other end 41b of the toggle plate 41 are pivotally attached. Thus, the other end 41b of the toggle plate 41 is received.

  That is, both end portions 41a and 41b of the toggle plate 41 are in contact with the groove 34b of the movable tooth 34 or the groove 42a of the toggle sheet 42, and both the grooves 34b and 42a are formed into curved surfaces. (Or the contact line) is configured to be slidable within the curved surface of the groove 34b of the movable tooth 34 or the groove 42a of the toggle sheet 42. Here, the contact portion between the other end portion 41b of the toggle plate 41 and the groove 42a of the toggle sheet 42 is also referred to as a first swing fulcrum P, and the contact between the one end portion 41a of the toggle plate 41 and the groove 34b of the movable tooth 34 is determined. The contact portion is also referred to as a second swing fulcrum Q. The contact portion is also referred to as an engagement portion.

The arm block 43 is a flat plate member, and an intermediate portion thereof is rotatably attached to first brackets 31 a and 31 a formed on the frame 31 by a first pin 44. The arm block 43 has a recess 43a at one end (the end on the side of the movable teeth 34), and the toggle sheet 42 is accommodated in the recess 43a. That is, when the first swing fulcrum P is disposed in the recess 43a and the arm block 43 is rotated, the arc as shown by a one-dot chain line in FIG. 1 with the center point O44 of the first pin ₄₄ as an axis. It is designed to swing around.

As shown in FIG. 3, the arm cylinder 45 includes a piston 45 a that is slidably fitted on the inner peripheral surface of the arm cylinder 45, a rod 45 b that is integrally fixed to the piston 45 a, and a piston 45 a inside the cylinder 45. The head side oil chamber 45c and the rod side oil chamber 45d are formed on both sides in the axial direction with the piston 45a as a boundary. Further, as shown in FIG. 1, the rod 45 b faces downward and is pivotally supported by a second pin 46 on a second bracket 31 b formed on the frame 31. The tip of the rod 45 b is pivotally attached to the other end of the arm block 43. As a result, when the rod 45 b is expanded and contracted, the arm block 43 rotates about the center point O ₄₄ of the first pin 44. For example, if reach out an arm cylinder 45, the arm block 43 is rotated into the Figure 1 in the clockwise direction (P ₁ direction), the first rocking fulcrum P of the aforementioned moves upward, conversely, the arm cylinder 45 if Chijimere the arm block 43 is rotated to FIG 1 in the counterclockwise direction (P ₂ direction), the first rocking fulcrum P is adapted to move downward.

Therefore, the movable tooth tip locus adjusting device has a four-bar linkage mechanism including the first swing fulcrum P, the second swing fulcrum Q, the center point O ₃₂ of the rotating shaft 32, and the eccentric point O ₃₄ of the movable tooth 34. It is like that. The position of the center point O ₃₂ is fixed with respect to the apparatus main body, and the first swing fulcrum P is movable as the arm block 43 rotates. The swing trajectory of the lower end of the movable tooth 34 changes greatly only by moving it slightly. The adjustment by the movable tooth tip locus adjusting device is performed in advance before the crushing operation is started, the angle of the arm block 43 is set by the arm cylinder 45, and the exit dimension W is adjusted by the shim 51. Thereafter, the first swing fulcrum P is fixed, and the second swing fulcrum Q moves slightly following the movement of the movable tooth 34 while restricting the movement of the movable tooth 34.

  Next, the gap adjusting device will be described in detail. The shim 51 is a plate-like member having a predetermined thickness, and a plurality of sheets are attached to the recess 43a of the arm block 43 so that a plurality of sheets can be inserted and removed between the bottom surface of the recess 43a of the arm block 43 and the toggle sheet 42. Yes. That is, the toggle sheet 42 and the shim 51 are arranged in the concave portion 43a in this order from the movable tooth 34 side. Then, the position where the toggle sheet 42 receives the toggle plate 41 is determined by adjusting the number of shims 51 to be inserted. Therefore, the adjustment of the outlet dimension W is performed by taking in and out the plurality of shims 51, and the processing particle size of the object to be crushed is determined by the size of the outlet dimension W.

  As shown in FIG. 3, the shim cylinder 52 includes a piston 52 a that is slidably fitted on the inner peripheral surface of the shim cylinder 52, a rod 52 b that is integrally fixed to the piston 52 a, and a shaft of the piston 52 a inside the shim cylinder 52. Head side oil chamber 52c and rod side oil chamber 52d formed on both sides in the direction of the piston 52a as a boundary, and further attached to the rod side oil chamber 52d so as to extend in the cylinder axial direction, and the piston 52a is always attached to the head. And a spring 52e that urges toward the side oil chamber 52c. That is, the spring 52e reduces the stroke of the shim cylinder 52. The rod 52b [one end portion of the shim cylinder 52 (the end portion on the movable tooth 34 side)] is pivotally supported by the bracket 34c of the fitting portion 34a of the movable tooth 34 with a pin, and the other end portion on the head side is formed on the arm block 43. The bracket 43b is fixed.

  In addition, the hydraulic circuit of the jaw type crushing device 30 for driving the arm cylinder 45 and the shim cylinder 52 with hydraulic pressure is configured as shown in FIG. On this hydraulic circuit, a hydraulic pump 61 that is a hydraulic source, a first supply line A and a second supply line B through which hydraulic oil supplied from the hydraulic pump flows, and a hydraulic tank that stores the returned hydraulic oil 62 is disposed.

The first supply line A and the second supply line B are branched, and a shim cylinder 52 is interposed in the first supply line A. Between the shim cylinder 52 and the hydraulic pump 61, the hydraulic oil passage is upstream. From the side, a first pilot check valve 63, an accumulator 64, and a first electromagnetic switching valve 65 are interposed in this order.
The first pilot check valve 63 is a valve for preventing backflow, and the accumulator 64 is a pressure accumulator for keeping the hydraulic pressure supplied to the shim cylinder 52 constant. The first electromagnetic switching valve 65 is an electromagnetic two-position switching valve having two positions, a t ₁ position and a t ₂ position, and hydraulic fluid is supplied to the head side oil chamber 52c of the shim cylinder 52 at the t ₁ position. is supplied, the t ₂ position are adapted to oil operation in the rod side oil chamber 52d is supplied with the switching of the position, so that the stroke of Shimushirinda 52 is adjusted. The first electromagnetic switching valve 65 is set so as to be in the t ₂ position when de-excited.

In addition, an arm cylinder 45 is interposed in the second supply line B. Between the arm cylinder 45 and the hydraulic pump 61, a second electromagnetic switching valve 66 and a pair of second pilot check valves 67 and 68 are overloaded. A load relief valve 70 is interposed.
The second electromagnetic switching valve 66 is an electromagnetic three-position switching valve having three positions of s ₁ position, s ₂ position, and s ₃ position, and hydraulic oil is supplied to the head side oil chamber 45c at the s ₁ position. In the s ₂ position (neutral position), the supply of hydraulic oil to the arm cylinder 45 itself is cut off, and in the s ₃ position, the hydraulic oil is supplied to the rod side oil chamber 45d. Note that the second electromagnetic switching valve 66 is set to be in the s ₂ position when de-energized.

  The overload relief valve 70 is a valve for releasing hydraulic oil in the head side oil chamber 45c and returning it to the hydraulic tank 62 when the hydraulic pressure in the head side oil chamber 45c of the arm cylinder 45 is equal to or higher than a predetermined pressure. Here, the predetermined pressure is a load pressure that acts on the arm cylinder 45 when the engagement between the movable tooth 34 and the fixed tooth 35 occurs, and is naturally higher than the pressure during normal crushing work. The support pressure is set so that it does not interfere with normal crushing operations. The pair of second pilot check valves 67 and 68 are valves for preventing a backflow from the oil chambers 45 c and 45 d of the arm cylinder 45.

Since the jaw type crushing apparatus according to one embodiment of the present invention is configured as described above, the following actions and effects are obtained.
First, in order to crush the object to be crushed, the operator (operator) drives the crushing hydraulic motor to rotate the flywheel 33 around the rotating shaft 32. Then, with the rotation of the flywheel 33, the movable tooth 34 swings. At this time, the movable tooth 34 is swung while being moved up and down by the rotation of the rotary shaft 32 provided at the upper portion, and the lower portion is suppressed from being vibrated by the support of the toggle plate 41. A circular motion close to a perfect circle and a horizontally long elliptical motion in the vicinity of the lower discharge port 30c cause a grinding action in the crushing chamber 30a.

In the present embodiment, since the arm block 43 and the arm cylinder 45 that swings the arm block 43 are provided, the swing trajectory of the tip of the movable tooth 34 can be changed, and this grinding action can be changed to achieve various types. It can cope with crushing of the material to be crushed. Therefore, working efficiency can be improved.
FIG. 4 shows a swing locus of the tip of the movable tooth 34, and a method for adjusting the swing locus will be described. The XY axis in FIG. 4 corresponds to the XY axis in FIG.

First, as an initial setting, the first swing fulcrum P is disposed at the position depicted in FIG. At this time, the piston 45a of the arm cylinder 45 is positioned at a substantially middle portion in the cylinder axial direction, and the toggle plate 41 is supported at an attachment angle θ ₀ (not shown) with respect to the horizontal plane.
Here, the second electromagnetic switching valve 66 is energized to the s ₁ position, hydraulic oil is supplied to the head side oil chamber 45 c of the arm cylinder 45, and the stroke of the arm cylinder 45 is extended. Then, the other end portion of the arm block 43 is pushed by the rod 45b of the arm cylinder 45 and moves downward, and one end portion of the arm block 43 moves upward. That is, the other end portion 41b of the toggle plate 41 is swingably supported by the groove 42a of the toggle sheet 42 located at one end portion of the arm block 43, so that the first swing fulcrum P is upward (see FIG. 1). P ₁ mounting angle theta ₁ moves in the direction) is increased than _{θ 0 (θ 1> θ 0} ), the movable teeth 34 tip, such as c in FIG. 4, the locus of the more linear long elliptical shape Swing while drawing. This is generally suitable for crushing hard materials.

Conversely, to s ₃ position by energizing the second solenoid switching valve 66 supplies the working oil to the rod side oil chamber 45d of the arm cylinder 45, shortening the stroke of the arm cylinder 45. Then, the other end portion of the arm block 43 is dragged through the rod 45b and moves upward, and one end portion of the arm block 43 moves downward. That is, the first rocking fulcrum P is downwardly moved to (P ₂ direction in FIG. 1) mounting angle theta ₂ is reduced than _{θ 0 (θ 2 <θ 0} ), the movable teeth 34 tip of FIG. 4 It swings in a more circular short elliptical locus like e. This is generally suitable for crushing soft materials.

That is, by adjusting the stroke of the arm cylinder 45, the elliptical shape of the swinging locus of the tip of the movable tooth 34 can be changed, and various crushed objects can be crushed. Therefore, working efficiency can be improved.
Further, since the swing locus is adjusted by the stroke of the arm cylinder 45, the change can be easily performed and a minute change can be dealt with.

After the stroke of the arm cylinder 45 is set, the second electromagnetic switching valve 66 is de-energized and returned to the neutral position s ₂ , and the stroke is held by the pair of second pilot check valves 67 and 68.
Moreover, in this embodiment, since the shim 51 and the shim cylinder 52 are provided, the exit dimension W can be adjusted and the particle size of a to-be-crushed object can be changed.

To explain the method of adjusting the outlet dimensions W, first, the t ₁ position by energizing the first electromagnetic switching valve 65, extending the stroke of Shimushirinda 52 by supplying hydraulic oil to the head-side oil chamber 52c of Shimushirinda 52. Then, there is a slight margin between the arm block 43 and the toggle sheet 42, and the number of shims 51 inserted between the arm block 43 and the toggle sheet 42 can be adjusted. Then, the position of the toggle sheet 42 that receives the toggle plate 41 is determined according to the number of inserted shims 51, and the exit dimension W can be adjusted.

After setting the outlet dimension W, the first electromagnetic switching valve 65 is de-energized and returned to the t ₂ position, the shim cylinder 52 is contracted, and the accumulator 64 applies pressure to the rod-side oil chamber 52b of the shim cylinder 52. Accordingly, the piston 52a is pushed in the direction of the head-side oil chamber 52c, the shim cylinder 52 is contracted, and the tip of the movable tooth 34 is pulled in the direction of the shim cylinder 52, so that the toggle plate 41 can be held so as not to drop off.

Further, since the spring 52e is built in the rod side oil chamber 52d of the shim cylinder 52, the spring 52e pushes the piston 52a of the shim cylinder 52 toward the head side to contract the shim cylinder 52, and the toggle plate 41 is more effectively used. Can be held.
In order to prevent the toggle plate 41 from falling off, the shim 51 is connected to a single hydraulic cylinder called a shim cylinder 52 as compared to the conventional technique in which a spring and a rod attached to the spring are provided separately from the hydraulic cylinder for shim adjustment. This function can be used in combination with the function of preventing the toggle plate 41 from falling off, and the number of parts can be reduced to achieve a simple configuration.

At the same time, since the front / rear position of the toggle sheet 42 with respect to the movable tooth 34 can be changed, the first swing fulcrum P of the toggle plate 41 can be changed in the front / rear direction, and the swing locus of the tip of the movable tooth 34 can be changed. The degree of freedom of change can be easily increased.
Further, since the overload relief valve 70 is provided for the arm cylinder 45, the hydraulic oil in the head side oil chamber 52c is released when the pressure is higher than a predetermined pressure, and the stroke of the arm cylinder 45 is shortened, resulting in a simple configuration. The outlet dimension W can be easily enlarged, and even if a hard foreign matter such as a metal lump that causes the crushing device 30 to stop is caught in the discharge port 30c, the foreign matter can be easily removed. Can do.

As mentioned above, although embodiment of this invention was described, this invention is not limited to the said embodiment, A various deformation | transformation is possible in the range which does not deviate from the meaning of this invention.
For example, in the above-described embodiment, the configuration including two arm cylinders 45 is illustrated. However, the number of the arm blocks 43 is not limited to this as long as the arm block 43 can be rotated so that the swing locus of the movable tooth 34 can be adjusted. For example, the number may be one or three.

  In the above embodiment, the overload relief valve 70 is provided with respect to the head side oil chamber 45c. For example, when the mounting angle of the arm cylinder 45 with respect to the arm block 43 is less than 90 degrees, the rod side oil chamber It may be provided for 45d. That is, it is sufficient that the overload relief valve 70 is attached to at least the oil chamber on the side where a large load due to the compression reaction force of the object to be crushed is applied.

  This is because, when the mounting angle of the arm cylinder 45 with respect to the arm block 43 exceeds 90 degrees as in the above-described embodiment, the outlet dimension W is increased when an object to be crushed is clogged in the discharge port 30c. This is because the load acts in the direction in which the arm block 43 is separated from the fixed tooth 35, that is, in the direction in which the stroke of the arm cylinder 45 is shortened. Therefore, the overload relief valve 70 is installed with respect to the head side oil chamber 45c so as to release the hydraulic pressure increased by this load. However, when the mounting angle is less than 90 degrees, the load acts to pull the arm cylinder 45, that is, to extend the stroke of the arm cylinder 45, and the pressure in the rod side oil chamber 45d of the arm cylinder 45 is reduced. On the other hand, since the head side oil chamber 45c has a negative pressure, the overload relief valve 70 is preferably provided for the rod side oil chamber 45d.

  In the above embodiment, the spring 52e of the shim cylinder 52 is mounted inside the rod side oil chamber 52d and biases the piston 52a toward the head side oil chamber 52c. The spring 52e may be provided in the cylinder 52c so as to extend in the cylinder axial direction, and the piston 52a may be biased toward the head. That is, it is only necessary that the force of the spring 52e is biased in the direction in which the stroke of the shim cylinder 52 is shortened. Further, the spring 52e is not built in the shim cylinder 52, but a spring is disposed at a position different from the shim cylinder 52, one end of the spring is connected to the lower portion of the movable tooth 34, and the lower portion of the movable tooth 34 is connected to the arm block 43. The toggle plate 41 may be prevented from falling off by being pulled toward the other end side.

It is a sectional side view of the jaw type crushing apparatus which concerns on one Embodiment of this invention. It is A arrow directional view of FIG. FIG. 2 is a hydraulic circuit diagram of the hydraulic cylinder of FIG. 1. It is a graph which shows the rocking locus of the movable tooth tip of FIG. It is a side view of a general self-propelled crusher. It is side sectional drawing of the jaw type crushing apparatus which concerns on background art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Self-propelled crusher 2 Traveling device 3 Feeding device 4 Discharge device 10 Jaw crushing device 10a Crushing chamber 10c Discharge port 11 Movable tooth 12 Fixed tooth 13 Frame 14 Rotating shaft 15 Toggle block 16 Toggle plate 17 Flywheel 18 Hydraulic cylinder 19 Sheet 20 Spring 21 Rod 22 Shim 30 Jaw crushing device 30a Crushing chamber 30b Input port 30c Discharge port 31 Frame 31a, 31b Bracket 32 Rotating shaft 33 Flywheel 34 Movable tooth 34a Fitting part 34b Groove 34c Bracket 35 Fixed tooth 41 Toggle plate 41a one end 41b other end 42 toggle sheet 42a groove 43 arm block 43a recess 43b bracket 44 first pin (pin)
45 Arm cylinder (hydraulic cylinder for arm, 1st hydraulic cylinder)
45a Piston 45b Rod 45c Head side oil chamber 45d Rod side oil chamber 46 Second pin 51 Shim (Shim plate)
52 Shim cylinder (hydraulic cylinder for shim, second hydraulic cylinder)
52a Piston 52b Rod 52c Head side oil chamber 52d Rod side oil chamber 52e Spring 61 Hydraulic pump 62 Hydraulic tank 63 First pilot check valve 64 Accumulator 65 First electromagnetic switching valve 66 Second electromagnetic switching valve 67, 68 Second pilot check valve 70 Overload relief valve (Relief valve)
A 1st supply line B 2nd supply line c, d, e Oscillation locus O ₃₂ , O ₄₄ Center point of rotating shaft O ₃₄ Eccentric point P of movable tooth P, Q Oscillation fulcrum (contact part)
s ₁ , s ₂ , s ₃ , t ₁ , t ₂ switching position X, Y axis W outlet dimension (gap)

Claims (4)

A fixed tooth fixed to a frame forming the apparatus main body, and a movable tooth disposed so as to be swingable in a direction of contact with and away from the fixed tooth, and between the fixed tooth and the movable tooth A jaw-type crushing device that crushes an object to be crushed by the swinging,
A toggle plate for supporting the movable tooth by engaging one end thereof with a lower portion of the movable tooth as the fulcrum of the swing;
An arm block having one end engaged with the other end of the toggle plate and an intermediate portion pivotally supported on the frame via a pin and configured to be rotatable about the pin as a central axis; ,
A jaw-type crushing apparatus comprising: a first hydraulic cylinder that has one end connected to the other end of the arm block and capable of rotating the arm block. A recess formed in the one end of the arm block;
A plurality of shim plates, which are detachably inserted between a bottom surface of the concave portion and the toggle plate and are capable of adjusting a gap between lower ends of the movable teeth and the fixed teeth, are provided. The jaw type crusher according to 1. 3. A relief valve is provided for releasing hydraulic oil inside the first hydraulic cylinder when the hydraulic pressure inside the first hydraulic cylinder is equal to or higher than a predetermined pressure set in advance. Jaw crusher. A second hydraulic cylinder having one end connected to the lower portion of the movable tooth and the other end connected to the other end of the arm block;
The jaw type crushing device according to any one of claims 1 to 3, wherein the second hydraulic cylinder includes a spring that urges the second hydraulic cylinder in a direction of shortening its stroke.

Images