JP4969626B2 - Cycle hammer for drilling hard rock ground - Google Patents

Description

  TECHNICAL FIELD The present invention relates to a drilling hammer for striking and drilling a hard rock ground or a layer with a boulder, and more specifically, a plurality of air hammers operating on the same principle as a conventional danza hole hammer (down the hole hammer). It is a bundle of cycle hammers that enable drilling of rock mass with low vibration and low noise, and belongs to the civil engineering field.

  In the civil engineering basic technology field, so-called down-the-holes, holes, hammers (commonly known as: danza-hole hammers) that use rock hammers, boulders, or concrete grounds with hammers driven by high-pressure air are commonly used. In order to reduce the vibration and noise of the dancer hole hammer, a technique of bundling a plurality of small dancer hole hammers into a single multi-danza hole hammer has been put into practical use.

9 shows a conventional cycle hammer (multi-danza hole hammer) cited as Patent Document 1. FIG. 9A is an overall schematic sectional view, FIG. 9B is a bottom view, and FIG. The principal part expansion longitudinal cross-sectional view of a hammer, (D) is a principal part disassembled perspective view of one hammer (air hammer).
In the conventional cycle hammer CH, as shown in FIG. 9A, an upper case 104 is connected to a hex plate 101 connected to a basic machine, a main body case 106 is connected to a lower portion of the upper case 104, and , One air hammer AH in the center and five air hammers AH in the periphery to make one cycle hammer CH, each air hammer AH is operated independently and one cycle hammer CH is a civil engineering foundation machine Operation is to be performed.

  That is, as shown in FIG. 9A, the upper case 104 divides the high-pressure air chamber S4 by an intermediate support B1, and a pressure air dispersion cone 105 is disposed at the center of the support B1. A pipe P107 for feeding high-pressure air is extended downward from the base plate B1, and each pipe P107 is connected to the piston bolt 107 at the upper end of the air hammer AH via the bottom plate B2, and each air hammer AH is As shown in FIG. 9B, in the case 106, there are five air hammers with a bit 116 having an equilateral triangular bottom surface at the periphery, and an air with a bit 116 having a circular bottom surface at the center. A hammer AH is arranged.

Each air hammer AH itself is formed by screwing and joining a piston case 112 to a lower portion of a piston bolt 107, screwing a drive sub 115 to the lower end of the piston case, and supporting a bit 116 by the drive sub 115.
9 (C) and 9 (D), the rod portion R116 of the bit 116 has a ring groove 116A for engagement disposed at the upper end of the small diameter portion protruding from the drive sub 115, as shown in FIGS. The vertical groove G116 group is arranged in the inner peripheral surface corresponding portion of the drive sub 115, the vertical groove G115 group is also arranged in the inner peripheral surface of the drive sub 115, and the rod portion R116 of the bit 116 is inserted into the drive sub 115. The ring ring 116A at the upper end of the small-diameter projecting portion of the rod portion R116 is fitted with a two-part retaining ring 119 and the inner circumferential projecting ring 119A is fitted into the annular groove 116A. Even if the bit 116 is suspended, the retaining ring 119 is supported by the drive sub upper end t115 so that the bit 116 is prevented from falling off. Going on.

Each air hammer AH has a check valve 108, a check valve presser 110, and a rigid valve 111 through a coil spring 109 in a piston bolt 107 as in a conventional dancer hole hammer. Is configured.
Therefore, if each air hammer AH supplies high-pressure air from the air pipe P107, the piston 113 is vibrated at high speed in the piston case 112 which is closely fitted in the main body case 106 and the lower end is held by the bottom pad B106. The piston lower end d113 gives high-speed vibration hitting to the bit upper end t116, and the bit 116 makes a high-speed repetitive hitting hole in the ground while being able to vibrate up and down and unable to rotate with respect to the drive sub 115.

Japanese Patent No. 3721381

In the conventional cycle hammer CH (FIG. 9), the high-pressure air chamber S4 for distributing and supplying high-pressure air to the air hammer AH is airtight by the hex plate 101 and the support B1 with respect to the upper case 104. However, the cycle hammer CH may break the rod or screw connected to the upper part during construction, and stone or earth and sand may enter the cycle hammer CH. A piece of rubber packing used for airtightening upstream of the plate 101 may enter the air hammer AH and become clogged.
Therefore, in order to remove foreign matter such as earth and sand and rubber pieces mixed in the cycle hammer CH, the hex plate 101 is gas-cut from the upper case 104 and cleaned, and the hex plate 101 is again welded and fixed. In short, maintenance was complicated.

  Further, from the high-pressure air chamber S4 to each air hammer AH, the length from the outside of the air distribution cone 105 arranged at the lower center of the high-pressure air chamber S4 to the central air hammer AH and the peripheral air hammer AH is individual. Since the different air pipes P107 are connected, the space between the lower half B1 and the bottom B2 of the upper case 104 becomes the arrangement chamber RP of the air pipe P107, and the conventional cycle hammer CH used in the related art (FIG. 9). In this case, the vertical dimension of the cover plate (bottom plate) 101B of the hex plate 101 and the tip of the bit 116 is large (standard: 2293 mm), the vertical dimension of the air pipe placement chamber RP is about 800 mm, and the weight is about 2000 kg. It was large and inconvenient to adopt in a small leaderless basic machine.

  In addition, each air hammer AH that is individually driven by each air pipe P107 has its bit 116 not rotatable by a drive sub 115 that is screwed to a piston case 112 that is rigidly fixed to the main body case 106. In addition, since it is guided so as to vibrate up and down and exerts an up and down vibration hitting action, the acting posture of each bit 116 on the drilling rock is constant, and the wear of the working head 116F of each bit 116 is greater in the outer peripheral part than in the inner peripheral part. The bit 116 is removed from the drive sub 115 at regular intervals, and the part with less wear is changed to a part with much wear, such as the outer peripheral protrusion of the main body case 106, and the bit 116 is removed again. It is necessary to attach the bit 116, and maintenance for using the drilling head 116F of the bit 116 effectively is troublesome.

Further, as shown in FIG. 9 (B), each gap ga between the peripheral bit 116 and the central bit 116 between the drilling heads (heads) 116F is constant. In the rock at the gap ga, the portion not subjected to the action of the bit 116 remains in a cylindrical shape, and the remaining cylindrical rock does not have the cutting tip b116. Further, the hole breaking efficiency of the cycle hammer CH is low because of the impact breaking action at the bottom plate B106 (bottom cover) that closes the lower surface of the case 106.
The present invention provides a cycle hammer CH having a small size, high performance, and excellent maintainability, which solves or improves the above-mentioned problems of the conventional cycle hammer CH (FIG. 9) at once. .

As shown in FIG. 1, the cycle hammer of the present invention includes an upper case 4 that defines a high-pressure air chamber S4 on the lower surface of a hex plate 1 having an air inflow port O1, and from the high-pressure air chamber S4 in the upper case 4. The cycle hammer CH is configured to supply high-pressure air to each air hammer AH housed in the hammer case 6 so that each air hammer AH gives a vertical vibration hit to the ground. Each air hammer AH is moved up and down by the high-pressure air. Each of the drill bits 16 includes a vibrating piston 13 and a striking drill bit 16, and each drill bit 16 is slidable up and down and rotatable in each piston case 12 held in the hammer case 6 so as not to rotate. each air hammer AH holds is a plurality of the peripheral portion of the hammer case 6, a single place in the center, and the air hammer AH of the heart, It is obtained by eccentrically disposed from over scan center position C6.

In this case, the hammer case 6 is formed by boring a hole into which each air hammer AH is inserted into one iron cylinder, as in the conventional example (FIG. 9). ), If one hole is formed in the center and four holes H14 are inserted in the periphery, and each air hammer AH is inserted into each insertion hole H14 from the lower end of the hammer case 6, Each air hammer AH is non-rotatably held in the hammer case 6, and the fitting and holding means of each air hammer AH with respect to the hammer case 6 is the same as the conventional example (FIG. 9). .
Also, the mechanism and action itself of the vertical vibration motion of each air hammer AH by the high-pressure air of the piston 13 and the vibration hitting of the drill bit 16 to the rock by the piston 13 are the same as in the conventional example (FIG. 9). is there.

  And the cycle hammer CH of the present invention is also similar to the cycle hammer of the conventional example (FIG. 9), with the tip of the drilling bit 16, that is, the drilling head 16F, in contact with the ground, While applying pressing force and slow rotation to the hammer CH, vertical vibration by high pressure air is applied to the piston 13 of each air hammer AH, and the rock mass is drilled by the drill bit 16 that receives the action of the piston 13. However, in the cycle hammer CH of the conventional example (FIG. 9), the drill bit 116 is held in the piston case 112 so as not to rotate and to be slidable up and down. The cycle hammer CH has a completely different action behavior of the drill bit 16 in that the drill bit 16 is held so as to be rotatable and slidable up and down with respect to the piston case 12.

Therefore, the cycle hammer CH of the present invention, during the drilling work of the rock mass, presses the lower surface of the cycle hammer CH against the rock mass as shown in FIG. However, in order to give the hammer case 6 the slow revolution of the arrow R1 by the suspending machine, and each drill bit 16 is rotatably held, the four surrounding drill bits 16 are moved by the slow revolution R1. The rotation of the arrow R2 due to the resistance from the ground at the outer edge is exhibited.
Therefore, in the cycle hammer CH of the present invention, during the drilling action, the drilling bit 16 of each air hammer AH performs the drilling action accompanied by the rotation R2, and the drilling head of each drilling bit 16 Since the wear of 16F is uniform on the entire circumferential surface, the drill bit 16 does not require complicated maintenance work such as changing between a worn part and a non-worn part and remounting as in the conventional example during the service life. The present invention provides a high-performance cycle hammer in which each drilling bit 16 always exhibits a uniform drilling action and has a high operating rate.
In the cycle hammer CH of the present invention, as shown in FIG. 1B, each air hammer AH is provided with a plurality of peripherals in the hammer case 6 and one in the central part. The point that the central air hammer AH is eccentrically arranged from the case center position C6 is also an essential requirement .
In this case, the eccentric arrangement of the air hammer AH at the center is to reduce the bit non-operation area generated between the innermost peripheral edge of the peripheral bit 16 and the outer peripheral edge of the central bit by the revolution hole of the cycle hammer CH. For a cycle hammer with a working diameter of 560 mm (hammer case diameter of 550 mm + peripheral bit protrusion of 5 mm), a peripheral bit diameter of 180 mm, and a central bit diameter of 130 mm, as shown in FIG. The vertical / lateral eccentric dimension gs from the center position C6, that is, the center bit eccentric dimension gs is typically 15 mm .
Therefore, in the form in which the center bit 16 is eccentric, the projecting wall of the non-perforated region that inevitably remains between the peripheral bit 16 and the center bit 16 due to slow rotation by the suspension of the cycle hammer CH is theoretically inevitable. As in the conventional example (FIG. 9), it is not necessary to blow and crush the non-drilled wall on the bottom case bottom surface, and the rock drilling hole is only a blow drilling hole in each drilling bit. The drilling force of the cycle hammer CH is improved .

  In the present invention, each air hammer AH has a check valve 8 and a piston bolt 7 connected to the high pressure air chamber S4 fixed to the upper end of the piston case 12 as shown in FIG. The piston 13 and the guide sleeve 14 are built in, and the drive sub 15 is screwed and fixed to the lower end of the piston case 12 in contact with the lower end of the guide sleeve 14, and the drill bit 16 is slid up and down on the drive sub 15. It is preferable to fit and hold so as to be able to rotate and slide.

In this case, the conventional example (FIG. 9) can be adopted as the configuration and operating principle of the rigid valve 11, the piston 13, and the guide sleeve 14 itself provided with each check valve 8 disposed in the piston case 12.
Further, as means for fitting and holding the drill bit 16 by the drive sub 15 so as to be slidable in the vertical direction and to be rotatable, the drive sub 15 itself has a fall prevention structure with a bottom pad 17 disposed at the lower end of the hammer case 6. Therefore, if the structure is made to prevent even the drilling bit 16 from being pulled out downward from the drive sub 15, the inner peripheral surface of the drive sub 15 is made smooth, and the insertion rod of the drilling bit 16 into the drive sub 15 is made. The outer peripheral surface of R16 may be a smooth surface and may be fitted and held so as to be able to slide smoothly. A smooth sliding protrusion may be formed to protrude from the outer peripheral surface of the rod R16 or the inner peripheral surface of the drive sub 15.

Therefore, in the conventional example (FIG. 9), the drill bit 16 of the present invention can be rotated and vertically slidably held by the drive sub 15 in the inner peripheral surface of the drive sub 115 or the drill bit. One of the outer peripheral surfaces of the rod portion R116 116 is effective as a smooth surface and the other as a vertical groove uneven surface, or both as smooth surfaces. Typically, as shown in FIG. The outer peripheral surface of the rod portion R16 of the drill bit 16 and the inner peripheral surface of the drive sub are smooth surfaces, a small diameter portion 16C is formed in the rod portion R16, and the presser pin P15 is projected from the drive sub 15 to the small diameter portion 16C. A relative vertical sliding area is formed.
Therefore, the cycle hammer CH of the present invention can be reasonably manufactured by diverting most of the structural members of the cycle hammer CH of the conventional example (FIG. 9), and the drill bit 16 is in operation as shown in FIG. Since the rotation indicated by the arrow R2 in B) occurs, uniform wear and uniform hole drilling are exhibited.

Further, in the present invention, as shown in FIG. 5, the drill bit 16 has a small diameter portion 16C in the middle of the rod portion R16 above the drill head 16F, and is fitted into the drive sub 15 on the outer periphery of the rod portion R16. It is preferable that the presser pin P15 protrudes from the small diameter portion 16C to support the drill bit 16 so as to be slidable up and down and rotatable.
In this case, the presser pin P15 may be inserted into the drive sub 15 as long as the presser pin P15 can be held in a projecting form on the rod small diameter portion 16C of the drill bit 16 and may be screwed into the drive sub 15 or slidably inserted. good.

  Accordingly, the structure for preventing the drill bit 16 from being pulled out from the drive sub 15 is achieved by reducing the diameter of the drill bit 16 with respect to the rod portion R16 and drilling the pin hole hp for inserting the presser pin P15 into the drive sub 15. Therefore, the machining operation and the arrangement operation of the presser pin P15 are the same as the conventional example (FIG. 9), in which the split stop ring 119 is fitted to the upper end of the rod portion R116 of the drill bit 116 protruding to the upper portion of the drive sub, and the guide sleeve. The air hammer AH of the present invention is easy to assemble, disassemble, and maintain easily, as the air hammer AH of the present invention can be freely rotated and held by the drive sub 15 of the drilling rod 16. I can do it.

  In the cycle hammer CH of the present invention, as shown in FIG. 5, the drive sub 15 includes an upper cylindrical portion 15A having a screw surface 15S on the outer periphery, and a base portion 15B having a polygonal outer periphery. The presser pin P15 is inserted into and projected from the rod small diameter portion 16C of the drill bit 16 from the pin hole hp, and the polygon insertion hole H14 of the hammer case 6 in which the piston case 12 is inserted prevents the presser pin P15 from being removed. preferable.

In this case, the drive sub 15 may be prepared by drilling a pin hole hp group at the base of the drive sub 115 of the conventional example (FIG. 9) having a regular hexagonal cross section.
Further, the rod small-diameter portion 16C receives the protruding tip of the presser pin P15 for preventing the drilling bit 16 from being pulled out and dropped from the drive sub 15, and also the drooping projection of the drilling bit 16 from the drive sub 15 The outer diameter DR of the drive sub sliding contact portions 16B and 16D that are in sliding contact with the inner peripheral surface of the drive sub 15 is typically 80 mm, and the outer diameter Dr of the small rod diameter portion 16C is 75 mm. The vertical dimension hr of the rod small diameter portion 16C is 70 mm.

  Therefore, in the cycle hammer CH of the present invention, the polygon drive sub base 15B of each air hammer AH is fitted into each polygon insertion hole H14 of the hammer case 6 as in the cycle hammer CH of the conventional example (FIG. 9). In the base portion 15B of the drive sub 15, a pin hole hp for inserting the presser pin P15 is formed, and the drill bit 16 simply cuts the small diameter portion 16C in the middle of the rod portion R16. The shaft support structure of the drill bit 16 that can be rotated and slid up and down can be formed, and the upper and lower ends of the small-diameter portion 16C by the presser pin P15 can be removed and dropped from the drive sub 15 of the drill bit 16. It is possible to prevent by the support at, and it is easier to manufacture and maintain than the bit shaft support structure (thrust shaft support structure) that can slide up and down in the conventional example (Fig. 9). 6, and rotates when accompanied drilling action the revolution cycle hammer CH, becomes to achieve the uniform drilling action and uniform wear action.

In the cycle hammer CH of the present invention, as shown in FIG. 1 (A), the hex plate 1 hangs down an unnecessary material inflow prevention network 3 for capturing unnecessary materials flowing in from the air inlet O1 on the lower surface. Therefore, it is preferable to detachably and air-tightly arrange at the upper end of the upper case 4 that partitions the high-pressure air chamber S4.
In this case, the “unnecessary matter” flowing in from the air inlet O1 means that if it flows into the air hammer AH that is operated by precise control of high-pressure air, the operation of the piston of the heart of the air hammer is hindered. These are earth and sand that the rod or screw guide breaks and enters, and rubber seals at the screw joints.

  Further, the unnecessary material inflow prevention net 3 may be a net that allows the inflow of high-pressure air and captures the above-mentioned unnecessary materials, and can be engaged and disengaged on the lower surface of the bottom plate 1B of the hex plate 1 by a conventional attaching / detaching means. 2A. Typically, as shown in FIG. 2A, a stainless steel thin plate in which through holes h3 having a diameter of 10 mm are dispersedly arranged on the outer peripheral surface and the bottom surface, a diameter of 300 mm and a height of 120 mm. The bottomed cylinder is fixed to the hex plate bottom plate 1B by welding.

  Therefore, the cycle hammer CH of the present invention can prevent the inflow of harmful substances such as earth and sand and rubber packing fragments into the air hammer AH. In general maintenance, the hex plate 1 can be removed and the inside of the upper case 4 can be cleaned, and the unnecessary material inflow prevention network 3 of the thin steel plate can be removed and re-welded easily by interval welding. In the example (Fig. 9), when the dust is clogged with the cycle hammer CH, maintenance is much simpler than maintenance such as open cleaning by gas melting cutting of the upper case, re-welding of the upper case, etc. It becomes an easy-to-use cycle hammer.

  In the cycle hammer CH of the present invention, as shown in FIG. 1A, an annular upper plate 2 is fixed to the upper end of the upper case 4, and the bottom plate 1B of the hex plate 1 is fixed to the upper plate 2. It is preferable to fasten with a plurality of bolts b and to insert a pin P extending over the upper pin hole hp of the upper plate 2 and the lower pin hole hp of the bottom plate 1B at an appropriate position between the bolts b.

  In this case, the annular upper plate 2 provides a means for attaching and detaching the hex plate 1 and the upper case 4 and transmits a strong rotational force of the hex plate 1 to the upper case 4. It has the same diameter as the hex plate bottom plate 1B and the same diameter as the upper case 4 and is welded and fixed onto the upper case 4 made of iron and having a thickness of 20 mm. Typically, the outer diameter is 550 mm, the annular portion width is 80 mm, As shown in FIG. 2 (B), eight bolt holes hb are arranged at equal intervals in the annular portion, and one upward pin is provided for every other section between the bolt holes hb. The holes hp are arranged with a depth of 15 mm and a diameter of 20 mm.

Further, the bottom plate 1B having a thickness of 24 mm of the hex plate 1 is also provided with a downward pin hole hp having a depth of 15 mm and a diameter of 20 mm at the position corresponding to the pin hole hp of the upper plate 2 and the bolt corresponding to the position corresponding to the bolt hole hb. The holes hb are arranged.
Accordingly, the hex plate 1 is assembled to the upper plate 2 by inserting and embedding a pin P1 having a diameter of 20 mm and a height of 30 mm in the four pin holes hp between the hex plate 1 and fastening the bolt b1 to each bolt hole hb. Therefore, in the upper plate 2 that receives the strong rotational force of the hex plate 1, the four embedded pins P1 between the eight bolts b1 also have a stress transmission function, and are integrated with the upper case 4 from the hex plate 1 side. Strong rotational stress resistance connection to the upper plate 2 can be achieved with a small number of bolts (standard: 8).

  Further, in the cycle hammer CH of the present invention, as shown in FIG. 1A, the bottom plate 4B of the upper case 4 is located at a position corresponding to the air inlet O7 at the upper end of the piston bolt 7 of each air hammer AH. An air outlet O4 is provided, a plurality of base pieces B5 are fixed on the bottom plate 4B so as not to interfere with the air outlet O4, and a high-pressure air dispersion cone 5 is fixed on the base piece B5. It is preferable to hold the space S5 between the bottom surface BS and the bottom plate upper surface US.

In this case, as shown in FIG. 1 (B), in the hammer case 6, each air hammer AH is arranged at the peripheral part, four at regular intervals and one at the central part, for a total of five. Five air outlets O4 are arranged in 4B, but the base piece B5 may be arranged at a position where each air outlet O4 is removed. Typically, the base piece B5 is a square having a side of 50 mm. As shown in FIG. 2 (C), an iron piece having a thickness of 20 mm is fixed to the bottom plate 4B by removing the air outlet O4 and welding and fixing at equal intervals, and a high-pressure air dispersion cone (standard: outer diameter 300 mm, height 200 mm). The conical bottom surface BS is fixed to each base piece B5 by welding.
Therefore, each air hammer AH is fitted into the hammer case 6 so that the air inlet O7 at the upper end of the piston bolt 7 is connected to the air outlet O4 of the upper case bottom plate 4B via the air inlet O6 of the hammer case 6. The high-pressure air in the high-pressure air chamber S4 in the upper case 4 is supplied with equal high pressure and equal supply to each air hammer AH including the air hammer AH at the center.

  Therefore, in the cycle hammer CH of the present invention, the path from the high-pressure air chamber S4 to the air inlet O7 at the upper end of the piston bolt is rigid in that the air outlet O4 of the bottom plate 4B and the air inlet O6 drilled in the upper end of the hammer case are rigid. An air inlet integrated with structural communication is formed and fitted into the hammer case 6 so as to contact and communicate with the air inlet O7 at the upper end of each air hammer AH. Therefore, as in the conventional example (FIG. 9), the arrangement for the air pipe P107 is provided. The chamber RP (standard vertical dimension: 800 mm) is not required, and the length of the cycle hammer CH can be shortened, and the high-pressure air dispersion communication structure between each air hammer AH and the high-pressure air chamber S4 can be rationalized. This is a cycle hammer CH with a reduced length that is easy and easy to maintain and can be used with small leaderless basic machines.

The cycle hammer CH of the present invention holds the drill bit 16 of each air hammer AH housed and mounted in one hammer case 6 so that it can rotate and slide up and down. The drill bit 16 of each air hammer AH exerts the drilling action under the pressure and gentle rotation of the cycle hammer CH by the civil engineering foundation machine, and each drill bit 16 group Each air hammer AH has a high and low vibration hitting action with the slow rotation R1 of the hammer AH and the rotation R2 due to the frictional force of the peripheral surface from the ground accompanying the revolution R1 of each drilling bit 16. In the drilling bit 16, the most severely worn portion is rotationally displaced by the rotation R2, and the wear of the drilling head 16F of each drilling bit 16 becomes uniform all around, and the drilling head 16F is always the uniform drilling hole. Product Achieve the.
In addition, the cycle hammer CH of the present invention has a plurality of hammer hammers 6 arranged in the periphery of the hammer case 6 and one in the center, and the center air hammer AH is arranged eccentrically from the case center position C6. In the form in which the center bit 16 is eccentric, the non-drilling region that inevitably remains between the peripheral bit 16 and the central bit 16 by the slow rotation revolution by the suspension machine of the cycle hammer CH, that is, the peripheral bit 16 is the highest. The protruding wall of the bit non-working area generated between the inner peripheral edge and the central bit outer peripheral edge can be substantially collapsed, and it is necessary to hit and crush the non-drilled wall on the lower surface of the bottom case as in the conventional example (FIG. 9). However, the rock drilling is only a blow drilling hole in each drilling bit, and the drilling force of the cycle hammer CH is improved .

It is explanatory drawing of the cycle hammer of this invention, Comprising: (A) is a whole vertical side view, (B) is a bottom view. It is A section explanatory drawing of FIG. 1, Comprising: (A) is an exploded side view, (B) is an exploded perspective view. It is assembly explanatory drawing of the cycle hammer of this invention, Comprising: (A) is a disassembled perspective view of a cycle hammer, (B) is bottom explanatory drawing. It is explanatory drawing of an air hammer, (A) is a vertical side view, (B) is an exploded perspective view, (C) is the elements on larger scale of (B), (D) is a top view of the check valve holder 10. . It is a partial explanatory view of an air hammer, (A) is a lower longitudinal side view of the air hammer, (B) is a longitudinal sectional view of a guide sleeve 14, (C) is a perspective view of a drive sub 15, (D) is a drive FIG. 4E is a perspective view of the drill bit in the vertical side view of the sub. It is explanatory drawing of piston 13, Comprising: (A) is a front perspective view, (B) is a side perspective view, (C) is the CC sectional view taken on the line of (A), (D) is D of (A). It is -D line longitudinal cross-sectional view. It is an air hammer assembly explanatory drawing, (A) is the state before the piston bolt incorporating the check valve is mounted on the piston case, (B) is the state where the piston bolt is mounted on the piston case, (C ) Is a view showing a state in which a piston and a guide sleeve are inserted into a piston case, and (D) is a view showing an assembled state. It is an action explanatory view of an air hammer, (A) is the state where the piston hits the drill bit, (B) is the state where the piston is raised, (C) is the state where the piston hit the drill bit again FIG. It is a prior art figure, (A) is an overall vertical side view, (B) is a bottom view, (C) is a longitudinal sectional view of the main part of the air hammer, and (D) is an exploded perspective view of the main part of the air hammer. .

As shown in FIG. 1, an example in which the present invention is applied to a cycle hammer CH in which a hammer case 6 having an outer diameter of 550 mm is accommodated with one air hammer AH at the center and four at the periphery is described in detail. .
1A is a longitudinal side view of the cycle hammer CH, and FIG. 1B is a bottom view of the cycle hammer.
The overall shape of the cycle hammer CH includes a detachable hex plate 1 at the upper end, an upper case 4 in which a high-pressure air chamber S4 is airtightly partitioned on the lower surface of the hex plate, and a hammer case 6 integrally fixed to the lower surface of the upper case 4. In the hammer case 6, as shown in FIG. 1 (B), five air hammers AH are arranged at regular intervals around the hammer case, and one is arranged in an eccentric form at the center.

Each of the drill bits 16 of the peripheral air hammer AH has a disc-shaped drill head 16F having an outer diameter of 180 mm, and the outer periphery of the drill head 16F is projected 5 mm from the outer periphery of the hammer case 6 so that the cycle hammer CH The drilling ability diameter is 560 mm, which is the outer diameter of the hammer case 6 +550 mm + the outward projecting dimension of 10 mm of the drilling head 16F.
And the lower end of each air hammer AH is prevented from falling off from the hammer case 6 by the bottom pad 17 as in the conventional example (FIG. 9), and the bottom pad 17 is protected by the bottom cover 18 on the lower surface.
Further, an unnecessary material inflow prevention net 3 is attached to the lower surface of the hex plate 1, and the drill bit 16 of each air hammer AH is held so as to be slidable up and down and rotatable.

  Accordingly, the cycle hammer CH of the present invention is different from the conventional cycle hammer CH (FIG. 9) in that (a) the hex plate 1 includes the unnecessary material inflow prevention network 3 and is detachable from the upper case 4. (B) The high-pressure air chamber S4 of the upper case 4 and the air inlet O7 of each air hammer AH are directly rigidly joined to eliminate the need for an air pipe, and (c) each drill bit 16 is rotatable. This is fundamentally different.

[Hex plate and upper case (Fig. 2)]
2A is an exploded side view of the hex plate and the upper case, and FIG. 2B is an exploded perspective view.
As shown in FIG. 2, the hex plate 1 itself, like the hex plate 101 of the conventional example (FIG. 9), includes a joint pin fitting portion 1A at the upper part and is connected to a screw having a high-pressure air inlet O1. And a bottom plate 1B having the same diameter (550 mm diameter) as the upper case 4, but the bottom surface of the bottom plate 1B is made of a stainless steel plate and has an outer circumference of 300 mm and a height of 120 mm. A large number of holes 3h having a diameter of 10 mm are scattered on the surface, and the unnecessary material inflow prevention net 3 is welded and fixed in a concentric form with the bottom plate 1B, and the outer peripheral portion of the bottom plate 1B having a thickness t1 of 24 mm is shown in FIG. As shown in Fig. 8, eight bolt holes hb are arranged at equal intervals (45 ° intervals), and a total of four downward pin holes hp are arranged with a depth of 15 mm and a diameter of 20 mm every other section between the bolt holes hb. To do.

  In addition, the annular upper plate 2 having the same diameter as the hex plate bottom plate 1B, a thickness t2 of 34 mm, and a width W2 of 80 mm is also provided with bolt holes hb at positions corresponding to the bolt holes hb of the hex plate bottom plate 1B. An upward pin hole hp having a depth of 15 mm and a diameter of 20 mm is formed at the corresponding position, and a notch C2 for welding is formed in the lower half of the peripheral surface of the upper plate 2 in advance.

  The upper case 4 is provided with a bottomed cylinder having a wall thickness t4 of 20 mm, an outer diameter of 550 mm, and a height of 360 mm. The bottom plate 4B has an air outlet O4 at a position corresponding to the air inlet O7 of each piston bolt 7. And a steel base piece B5 having a side of 50 mm and a thickness of 20 mm for supporting a high-pressure air dispersion cone (diameter 300 mm, height 200 mm) at the periphery of the cone bottom at a position where it does not interfere with each air outlet O4 As shown in FIG. 2 (A), a space S5 having a height of 20 mm is held between the conical bottom surface BS and the bottom plate upper surface US, and an air outflow function from the air outlet O4 at the center is provided. To secure.

Further, a notch C4 for phase crack welding is also arranged at the upper end of the upper case 4, and the upper plate 2 is integrated with the upper case 4 by phase crack welding of the notch C2 and the notch C4.
Then, a pin P1 having a height of 30 mm and a diameter of 20 mm is fitted into each upward pin hole hp of the upper plate 2, and each pin hole hp of the hex plate bottom plate 1B is fitted to the protruding portion of the pin P1, so that the hex plate bottom plate 1B The bolt b1 is screwed and fixed to the bolt hole hb of the upper plate from each bolt hole hb.
Accordingly, the upper plate 2 reinforces the upper surface of the upper case 4, and the hex plate 1 and the upper case 4 have eight embedded pins P 1 that assist the anti-shearing force of the bolt b 1 against strong rotational stress. The plate 1 ensures detachable and strong bonding to the upper case 4.

[Air hammer AH (FIGS. 4, 5, 6)]
The air hammer AH is a hammer that is housed in a hammer case 6 and drills rock by receiving high-pressure air. The basic structure and operating principle of the air hammer AH itself are the conventional examples (FIG. 9). 4 (A) is an overall vertical side view of the air hammer AH, FIG. 4 (B) is an exploded perspective view, and FIG. 4 (C) is a diagram. 4B is an enlarged view of the valve system, and FIG. 4D is a top view of the check valve presser 10.

  That is, in the air hammer AH, as shown in FIG. 4A, the piston case 12 having an outer diameter of 136 mm and an inner diameter of 115 mm is screwed onto the outer peripheral thread surface 7S at the lower end of the piston bolt 7 with the inner peripheral thread surface 12S at the upper end. The piston bolt 7 is joined flush with the outer periphery of the piston bolt 7 and is integrally screwed with the outer peripheral thread surface 15S of the cylindrical portion 15A of the drive sub 15 at the lower inner thread surface 12S, and a valve mechanism is held inside the piston bolt. The piston 13 is stored below the mechanism, the drilling bit 16 is stored at the lower part of the piston 13, and the drilling head 16 F at the lower end is stored in a form protruding downward from the lower end of the drive sub 15. The drive sub 15 that is rigidly integrated with the piston case 12 is held so as to be rotatable and slidable up and down.

  The valve mechanism itself is the same as the conventional air hammer (FIG. 9). As shown in FIGS. 4 (A) and 4 (C), the rubber check valve 8 is connected to the check valve holder 10 via the coil spring 9. Enclosed in the upper bottomed cylinder 10A, the lower cylinder 10B of the check valve retainer 10 is fitted into the upper cylinder 11A of the rigid valve 11, and the pin P8 connects the check valve retainer 10 and the rigid valve 11 to the lower part of the piston bolt. The lower cylinder 11B of the rigid valve 11 is fitted into the upper part of the central hole of the piston 13 which is the same as that of the conventional example (FIG. 9). The outlet O11 is communicated with the air path of the piston 13.

  In the piston case 12, as shown in FIG. 4 (A), a guide sleeve 14 is placed at the upper end of the drive sub 15 in order to guide the high-vibration vertical movement of the piston 13 as in the conventional example (FIG. 9). The lower air pool Sd is formed between the lower outer periphery of the piston 13 and the guide sleeve 14, and the upper air pool Su is formed between the upper end of the piston 13 and the lower end of the piston bolt, and flows into the piston bolt 7 from the upper air inlet O 7. As with the conventional example (FIG. 9), the high pressure air flow causes the piston 13 to vibrate up and down by the action of the high pressure air flow among the rigid valve 11, the piston 13, and the piston case 12, and a drill bit is formed at the lower end d13 of the piston 13. The upper end t16 of 16 is hit.

5A and 5B are diagrams for clarifying differences between the air hammer AH of the present invention and a conventional air hammer, in which FIG. 5A is a longitudinal side view of a lower portion of the air hammer, and FIG. 5B is a longitudinal section of a guide sleeve. 4C is a perspective view of the drive sub 15, FIG. 4D is a longitudinal side view of the drive sub 15, and FIG.
As shown in FIG. 5 (B), the guide sleeve 14 is a steel pipe having an outer diameter D14 of 105 mm, a height L14 of 117 mm, and a wall thickness of 10 mm. An upper end annular flange 14A and a lower end annular flange 14B are provided for sliding contact with the inner peripheral surface of the piston case 12, and an inner periphery with an inner diameter of 70 mm is provided on the upper inner peripheral surface to guide the outer periphery of the piston lower portion 13B. A flange 14C is provided.

[Drive sub 15 (FIGS. 5C, 5D)]
As shown in FIG. 5D, the drive sub 15 of the present invention has an inner diameter d15 having an upper cylindrical portion 15A having an outer periphery that is a screw surface 15S and a base portion 15B having an outer periphery that is a polygon (standard: regular hexagon). Is a steel cylinder having an outer diameter D15 of 115 mm, and the base portion 15B has a maximum diameter Ad protruding in a square shape, that is, a diagonal dimension of 140 mm, and faces 50 mm above the lower end of the base portion 15B. A pin hole hp with a diameter of 10 mm for inserting the presser pin P15 is formed.

[Drilling bit 16 (FIGS. 1 and 5)]
The drill bit 16 includes a rod portion R16 and a drill head 16F. As shown in FIG. 1, the four outer peripheral bits and the center bit differ only in the shape of the drill head 16F.
That is, as shown in FIGS. 5 (A) and 5 (E), the peripheral drilling bit 16 includes a disk-shaped drilling head 16F having an outer diameter of 180 mm and a lower surface of the drilling head 16F. A bottom pad fitting portion 16E having an outer diameter of 120 mm and a rod axial length of 20 mm, and a rod portion R16. The rod portion R16 is a guide sleeve having an outer diameter of 75 mm and an axial length of 70 mm from the upper end. Sliding contact portion 16A, outer diameter 80mm, drive sub sliding contact portion 16B with axial length 115mm, press pin P15 with outer diameter 75mm and vertical length 70mm, small diameter portion 16C for sliding contact, outer diameter 80mm, length 55mm Drive sub-sliding contact portion 16D.

[Piston 13 (FIG. 6)]
6A and 6B are explanatory views of the piston 13, wherein FIG. 6A is a front perspective view, FIG. 6B is a side perspective view, FIG. 6C is a cross-sectional view taken along the line CC of FIG. ), And the piston 13 itself is the same as the piston 113 of the conventional example (FIG. 9).
That is, the piston 13 is a cylinder having an outer diameter 115 mm, an upper portion 13A having a length of 218 mm, and a lower portion 13B having an outer diameter of 70 mm and a length of 112 mm, through which the center hole O13 passes. There are four air holes Ou through which air flows upward, and the cutouts C13 on the left and right side surfaces have air holes Od through which air flows downward, and air holes Ou through which air flows upward also flow downward. The air hole Od is also in communication with the center hole O13.

[Assembly of air hammer AH (Figs. 4 and 7)]
As shown in FIG. 4, first, the check valve 8 is inserted into the upper bottomed cylinder 10A of the check valve retainer 10 via the coil spring 9, and then the check valve retainer is inserted into the upper bottomed cylinder 11A of the rigid valve. The lower cylinder 10B is inserted, and the pin hole (not shown) below the piston bolt, the pin hole hp of the rigid valve, and the pin hole hp of the check valve presser are aligned and integrated through the connecting pin P8. As shown to (A), the piston bolt with a built-in valve mechanism similar to a prior art example (FIG. 9) is prepared.

Further, the rod portion R16 of the drill bit 16 is fitted from the base portion 15B of the drive sub 15, and the presser pin P15 is inserted into the drill bit small diameter portion 16C from each pin hole hp of the drive sub base portion 15B. As shown in (A), a drill bit 16 fitted with a drive sub 15 is prepared.
Next, as shown in FIG. 7B, the piston bolt is screwed onto the inner periphery of the upper end of the piston case, and as shown in FIG. 7C, the piston 13 is inserted into the piston case 12 from below, and then the guide sleeve 14 is inserted. Then, as shown in FIG. 7D, when the screw surface 12S at the lower end of the piston case 12 is screwed to the screw surface 15S on the outer periphery of the cylindrical portion of the drive sub 15, the assembly of the air hammer AH is completed.
In this case, the air hammer AH at the center of the cycle hammer CH may be a small diameter (standard: 130 mm outer diameter) of the drilling head 16F as the drilling bit 16.

  As shown in FIG. 8, the obtained air hammer AH has a check valve in which the high-pressure air flow a is in the landing state of the drill bit as shown in FIG. 8, as in the conventional example (FIG. 9) and a conventional dancer hole hammer. If the pressure 8 is pressed and flows into the lower part of the check valve 8, the high-pressure air flow a is, as indicated by the arrow, the air inlet O 10 of the check valve holder 10 → the interior of the rigid valve 11 → the air outlet O 11 of the rigid valve → the piston 13. The air hole Od going to the lower part of the piston flows into the lower air reservoir Sd of the piston, the piston 13 rises due to the increase in pressure of the lower air reservoir Sd, and the state shown in FIG. a flows through the piston bolt air outlet O11 → the air hole Ou going to the upper part of the piston 13 → the upper air reservoir Su, and the high pressure air in the upper air reservoir Su presses the piston 13 downward. The piston lower end d13 strikes the upper end t16 of the drill bit 16, and the state shown in FIG. 8C, that is, the state shown in FIG. 8A, is obtained. The hole bit 16 exerts a high-speed vertical vibration hitting action on the ground.

[Assembly of cycle hammer CH (Fig. 3)]
As shown in FIG. 3 (A), the hammer case 6 is a solid iron round bar having an outer diameter of 550 mm and a length of 1050 mm. As shown in FIG. 1 (B), the hammer case 6 has a wide width of 10 mm in depth and 70 mm in width. As shown in FIG. 3A, the circumferential recess 6A is cut and arranged over the entire length, and the outer circumferential surface extends 500 mm from the lower end, and the entire circumferential surface is reinforced with wear resistance by quenching Ht. .
Next, similarly to the conventional example (FIG. 9), each air hammer insertion hole H14 and case coupling bolt insertion hole H19 are bored.
In this case, the insertion hole H14 has a shape in which the lower end portion is aligned with the hexagonal base portion 15B of the drive sub 15 and the intermediate portion is a cylinder, like the air hammer insertion hole in the conventional example (FIG. 9). The upper part is the form which fits the piston volt | bolt 7 in the shape matched with piston case 12 of this.

Next, the coupling bolts 19 extending from the bottom plate 4B of the upper case 4 are passed through the insertion holes H19 of the hammer case 6 so that the lower end of the coupling bolt 19 does not protrude from the lower surface of the hammer case 6 with the nut n19. The upper case 4 integrated with the hex plate 1 and the hammer case 6 are integrated.
Further, a bolt hole hb for fastening the bottom pad and a bolt hole hb for fastening the bottom cover are also formed in the lower surface of the hammer case 6.

  Next, a packing material is arranged in the annular groove 7G on the outer periphery of the upper end of the piston bolt 7 and the annular recess 7C on the outer periphery of the piston bolt 7, and each air hammer AH is inserted from the insertion hole H14 in the lower end of the hammer case 6, 9) Similarly, as shown in FIG. 3 (B), the bottom pad 17 in a divided form is provided on the bottom pad fitting portion 16E that provides a locking dimension to the lower end of the drilling head 16F and the drive sub 15 of each air hammer AH. The bottom pad 17 is fastened to the lower end surface of the hammer case 6 with a bolt b17, and the bottom cover 18 is brought into contact with the lower surface of the bottom pad 17, and the bottom cover 18 is secured to the bottom pad by the bolt b18. What is necessary is just to screw in the lower end surface of the hammer case 6 with the form which penetrated 17.

  The obtained cycle hammer CH is a space S5 having a thickness of 20 mm for high-pressure air circulation between the conical bottom surface BS and the bottom plate 4B upper surface US via the bottom plate 4B. Since the piston bolt 7 at the upper end of each air hammer AH and the air outlet O4 of the high-pressure air chamber S4 can be directly rigidly connected to the air inlet O6 of the hammer case 6, the cycle hammer CH Since the arrangement chamber RP for the air pipe P107 in the conventional example (FIG. 9) has been deleted, the total length from the hex plate bottom plate 1B to the bottom surface of the drilling head 16F is 1611 cm, which is a cycle hammer having the same equivalent drilling capability ( It can be much shorter than the overall length (standard: 2293cm) of Fig. 9), and the weight is also 1800kg, the weight of the conventional cycle hammer (Fig. 9) (standard: 2000kg) It has become a small, high-performance cycle hammer that can be reduced in weight and can be easily mounted and used on a small civil foundation machine (hydraulic excavator-mounted pile driver).

  Further, during the construction work, each drilling bit 16 is held by the drive sub 15 so as to be rotatable and slidable in the vertical direction. Therefore, along with the revolving action of the slow rotation R1 of the cycle hammer CH. The drilling head 16F in the form of a disc of a drilling bit freely rotates R2 due to the frictional resistance difference from the ground between the outer peripheral portion and the inner peripheral portion (outer peripheral surface> inner peripheral surface), and the cycle hammer CH As each of the drilling bits 16 on the outer peripheral portion is leveled, and there is no uneven wear on the drilling bit as in the conventional example (FIG. 9), the mounting change maintenance corresponding to the wear of the drilling bit becomes unnecessary. Occupancy rate improved.

Further, since the drill bit 16 of the air hammer AH in the central part is arranged eccentrically (standard: 15 mm eccentric) from the air hammer central part C6, the center bit and the peripheral bit 16 are aligned with the slow rotation R1 revolution of the cycle hammer CH. The hole inactive area ga between the bits 16 could be greatly reduced, and the rock in the inactive area that remained slightly could be crushed with a small stress without damaging the bottom cover 18.
Moreover, because the center air hammer AH also has an eccentric arrangement, the drill bit 16 has a rotation R2 action accompanying the revolution R1 of the cycle hammer CH, similarly to the peripheral drill bit 16, so that the wear of the drill bit 16 is reduced. Leveled.

In addition, the hammer case 6 has a circumferential circumferential recess 6A extending over the entire length on the outer circumferential surface, and the outer circumferential surface lower end portion has a quenching Ht wear resistance function, so that the drilling of the drilled earth and sand is smooth, The wear of the hammer case 6 was also reduced, and in combination with the leveling wear of each drill bit 16, the drilling work could be continued for a long time.
Since the lower end of the hammer case 6 is hardened and reinforced, damage and deformation of the hammer case 6 due to rock drilling can be prevented, so that deformation of the insertion hole H14 for the air hammer AH can also be prevented. It became a highly durable cycle hammer CH that does not interfere with the attachment / detachment of the air hammer AH.
In addition, since the hex plate 1 is detachable from the upper case 4 and includes the unnecessary material inflow prevention network 3, there is no fear of malfunction due to accidental inflow of foreign matter into the air hammer AH. It became a high cycle hammer.

1 Hex plate 1A Joint pin insertion part 1B, 4B Bottom plate 2 Upper plate 3 Unnecessary material inflow prevention network 4 Upper case 5 Cone (high pressure air dispersion cone)
6 Hammer case (case)
6A circumferential recess 7 piston bolt 7C annular recess 7G annular groove 7S, 12S, 15S thread surface 8 check valve 9 coil spring 10 check valve presser 11 rigid valve 12 piston case 13 piston 14 guide sleeve 14A upper end flange 14B lower end flange 14C inner circumference Flange 15 Drive sub 15A Cylindrical portion 15B Base 16 Drilling bit (bit)
16A Guide sleeve sliding contact portion 16B, 16D Drive sub sliding contact portion 16C Small diameter portion 16E Bottom pad fitting portion 16F Drilling head (head)
17 Bottom pad 18 Bottom cover 19 Case coupling bolt a High pressure air flow AH Air hammer B5 Base piece BS Conical bottom b1, b17, b18 Bolt b16 Cutting tip CH Cycle hammer C6 Center position hb Bolt hole hp Pin hole h3 Through hole H14, H19 Insertion hole Ht Quenching O4, O11, O16 Air outlet (Air outlet)
O1, O6, O7, O10 Air inlet (air inlet)
P, P1, P8 Pin P15 Presser pin R1 Revolution R2 Rotation R16 Rod part S4 High pressure air chamber S5 Space Sd Lower air reservoir Su Upper air reservoir US Bottom plate upper surface

Claims (7)

The lower case of the hex plate (1) provided with the air inlet (O1) is provided with an upper case (4) that partitions the high-pressure air chamber (S4), and from the high-pressure air chamber (S4) in the upper case (4), A cycle hammer (CH) for supplying high-pressure air to each air hammer (AH) housed in a hammer case (6), and each air hammer (AH) imparts vertical vibration hitting to the ground, each air hammer (AH) includes a piston (13) that vibrates up and down by high-pressure air and a striking drill bit (16), and each drill bit (16) is held non-rotatable in the hammer case (6). Each piston case (12) is slidable up and down and can be rotated, and each air hammer (AH) has a plurality of peripherals in the hammer case (6) and one in the center. Placed and inside The Department air hammer (AH), an eccentric arrangement of the case center position (C6), cycle hammer.   Each air hammer (AH) is provided with a check valve (8) and a piston bolt (7) connected to the high-pressure air chamber (S4) is fixed to the upper end of the piston case (12). (13) The guide sleeve (14) is built in, the drive sub (15) is screwed and fixed to the lower end of the piston case (12) in a contact form with the lower end of the guide sleeve (14), and the drill bit (16) is 2. The cycle hammer according to claim 1, wherein the cycle hammer is fitted and held on the drive sub (15) so as to be slidable up and down and rotationally slidable. The drilling bit (16) has a small diameter part (16C) in the middle of the rod part (16R) above the drilling head (16F), and a presser pin fitted into the drive sub (15) on the outer periphery of the rod part (16R) ( The cycle hammer according to claim 2, wherein P15) projects to the small diameter portion (16C) and supports the drill bit (16) so as to be slidable up and down and rotatable.   The drive sub (15) includes an upper cylindrical portion (15A) having a thread surface (S15) on the outer periphery, and a base portion (15B) having a polygonal outer periphery, and a presser pin from a pin hole (hp) of the base portion (15B). (P15) is inserted into and projected from the rod small diameter portion (16C) of the drill bit (16), and the polygon insertion hole (H14) of the hammer case (6) into which the piston case (12) is inserted is formed on the presser pin (P15). The cycle hammer according to claim 3, wherein withdrawal is prevented. The hex plate (1) is an upper case (4) that divides an unnecessary material inflow prevention network (3) that traps unnecessary materials flowing in from the air inlet (O1) to the lower surface to partition the high-pressure air chamber (S4). The cycle hammer according to any one of claims 1 to 4 , wherein the cycle hammer is detachably and airtightly arranged at an upper end of the stub. An annular upper plate (2) is fixed to the upper end of the upper case (4), and the bottom plate (1B) of the hex plate (1) is fastened to the upper plate (2) with a plurality of bolts (b). with, in place between the bolt (b), was fitted into pin over downward pin hole (hp) upward pin holes of the upper plate (2) (hp) and bottom plate (1B) (P), according to claim 5 Cycle hammer as described in. The bottom plate (4B) of the upper case (4) includes an air outlet (O4) at a position corresponding to the air inlet (O7) at the upper end of the piston bolt (7) of each air hammer (AH). ), A plurality of base pieces (B5) are fixed at positions not interfering with the air outlet (O4), and a high pressure air dispersion cone (5) is fixed on the base piece (B5). The cycle hammer according to claim 5 or 6 , wherein a space (S5) is maintained between the bottom surface (BS) and the bottom plate upper surface (US).

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