JPS5890476A - Method of controlling impulse motor and impulse motor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] A, Lugi, Jt, transforms into wave energy and uses this temporary energy as a jackhammer stem.
The present invention relates to a method rζ of controlling an impact motor with a reciprocating hammer piston configured to transmit to a long tool.

The present invention also utilizes the above-described ratio-forming impact motor with a 14-speed adjustment device that increases the impact velocity of the hammer piston by $4.

It is known that in a rock drill, the amount of deflection can be increased to a certain level by increasing the impact energy per strike. If the impact energy is increased above the above-mentioned level, the amount of penetration increases only slightly, whereas the wear of the rock drill increases significantly.

It is also known in the art that a worn rock drill requires 911i6 more impact energy to achieve the same amount of penetration than a new or freshly ground rock drill.

Normally, in a jackhammer, the condition of the jackhammer changes gradually and irrespective of the changes in the sex of the rock.

The hammer piston applies an equal impact with a constant impact energy per impact.

An object of the present invention is to enable control of K impact eta in order to utilize impact energy more effectively. Therefore, the *Hayabusa motor according to the present invention can be used, for example, as an impact motor for a rock drill or jackhammer. This object is achieved by the features described in the characterizing part of the claims.

The kinetic energy of the hammer piston is transferred in the form of compression waves to the tool, which may constitute a PA rock machine stem.

Most of the shock wave energy that is not used to fracture the rock is reflected as shock wave energy in the form of compression waves or tension waves. This energy can also be reflected partly as a compression wave and partly as a tensile wave.

According to the present invention, reflected shock waves are sensed and impact velocity is adjusted in response to the sensed reflected shock waves.

An advantage of the present invention is that it senses the motion coupled to the reflected shock wave and minimizes this motion. transmitting force to the tool 5 and sensing the rebound of an elastically I-formable element configured to match the impact velocity of the hammer piston; It is particularly advantageous to ensure that the particles do not disappear, but become smaller. Compressive wave energy only causes the deformable element to bounce back, so there should be only a small amount of bounce.Tension wave energy has no negative effect on bounce, and 1 if there is no bounce p at all. Is the impact velocity accurate?

The invention will now be explained with reference to the drawings.

The percussion device shown in Figure 1 represents a hydraulic rock drill, hydraulic jar, jack drill, or similar device. The illustrated device has a cylinder /J in an outer casing l/.

A hammer piston/J is configured to reciprocate within this cylinder and apply an impact to an unpillar element/l such as a chisel, a jackhammer stem or an adapter for a jackhammer stem. The shoulder lj on the ampilling element is supported on the sleeve /j of the damping piston l7, which dampens the reflected compression shock waves. The cylinder chamber /I is continuously pressurized through the passage I, and the fluid pressure in this cylinder chamber I presses the damping piston I7 forward to its front end position as shown in the drawing. The pressure in the cylinder chamber lr acts on the annular piston surface of the buffer piston. Hammer piston/J
〇 randos. A front cylinder chamber λλ is formed between the piston/3 and the cylinder I.
A rear cylinder chamber 23 and an intermediate cylinder chamber λhiro are formed.

The piston l3 is propelled forward by the pressure acting on its surface r111 and backward by the pressure acting on its surface knob. The valve core has an inlet λt leading to a source of high pressure fluid and an outlet λt leading to the tank. #i accumulator 30 is connected to these inlet 21 and outlet lokota.
, 3/ are connected to each other. The intermediate cylinder chamber 21 is continuously connected to the outlet 2 by a conduit aK. The valve core is connected to the rear cylinder chamber 3 via a supply passage 32,
It is connected to the front cylinder chamber 2.2 via a supply passage 33.

The valve spool 34t of the valve 27 connects the rear cylinder chamber λ3 to the pressure fluid source in the illustrated position, and connects the front cylinder chamber,
Connect the two to the tank. Cylindrical end 3 of valve spool 34I-! , 36 have a piston surface which is connected to the control passage 37 . ≠2, these passages are each branched into da branch passages, so that the control passages 37.4!2 are each divided into da boats 31r.
, 3ri, po, gu/and! j, 4+! ≠、Reference 3. It leads to Cylinder/2 via Hiro 6. A total of t branch passages are provided with cylindrical holes 7 intersecting with each other, and a cylindrical pin≠t is slidably provided in this cylindrical hole 4/-7 in a fluid-tight manner. Pin #l has two small diameter parts, no.
M. Pin 4! The IK control piston 11 is integrally provided, and this piston! J divides one cylinder into two cylinder chambers It, 17, and 'tt% Kame Bin IK is integrally provided with a dashpot piston Jl.

Compressed air is a pressure regulator! 2 passages through de 40.4/
A restriction portion 42 is provided in the zero passage 41 which is supplied to the two cylinder chambers It, 17, respectively.

The cylinder chamber j7 is communicated with the cylinder chamber 4# between the outer casing 11 and the land 4j on the buffer piston 17 by a passage 43. The front end surface 64 of the land 4j abuts against the shoulder 47 inside the outer case to limit the impact position of the anvil element l. The land 4jK is provided with seven or more passages 11 passing through it in the axial direction, and the buffer piston 17 is pressed forward to the normal position as shown in FIG. 1. Even though the passage 11 is closed, However, when the buffer piston 17 leaves the shoulder ≦7, it is communicated with the atmosphere via the passage 42.

Next, the operation of the impact device shown in FIG. 1 will be explained.

The hammer piston 13 moves forward (to the left in FIG. 1) during its working stroke as shown in FIG. 1, so that the valve spool 3 is in the position shown. When the boat of the control passage λ is opened to the rear cylinder chamber 3, the control passage ≠ applies pressure to the control piston 3t, causing the valve suction 34& to move to the right (as shown in Figure 1). Moving. Preferably, at the moment when the hammer piston 13 hits the anvil/hiro, the valve suction 3≠ has finished its movement. Therefore, the pressure existing in the front cylinder chamber λλ from the moment of collision is
1J rearward to open the branch passageway Hiro O of the control passageway 37 to the front pressure chamber here. As a result, the pressure passage 37 applies a control piston/3jVcEfl force to return the valve spool 3V to the illustrated position, whereby the rear cylinder chamber λ3 is pressurized. The pressure in the rear cylinder chamber 23 retards the movement of the hammer piston 11 and accelerates it forward again, so that the hammer piston/3 performs another working stroke t'.

Valve spool 3 has an annular surface j2. ! 3 and internal passage si,
z4L, which allows both active IJ pistons 3jt,
34 holds the loaf spool in place while the piston is not held stationary. Circular table [jJ.

! 3 is piston 3! , 34 ends.

Except for the bin≠l being in the position shown, the boat 〇 in the control passage 37 and the boat μj in the control passage 4A2 are the boats that make the valve stool shift position tjjtt-. In other positions of the pins ti-t, the other boats do not act, the three pairs of boats 31. A pair of boats from each of ≠3; 3, Hiro≠ and ≠/, Hiro4 are selected to cooperate to control the valve.

During the return stroke of the hammer piston, the boat 31~≠io@first one opened to the front cylinder chamber 22 begins to move the valve spool 3hiro to the shift position. Thus, by adjusting the axial position value of the bin, the operator preselects the stroke length of the printer. The axial distance between boats 3 and 4 is smaller than the corresponding axial distance between boats Jl and F/.

By appropriately selecting the axial position of the boat 3~≠4 in the cylinder for each stroke length, the selected boat 3~≠4 is closed at a predetermined distance before the impact position of the hammer piston. Alternatively, the valve spool can be moved to a position where it pressurizes the front pressure chamber when the hammer piston/J impacts the anvil element. By suitably selecting the distances between the boat bays 3-14, it is possible to ensure that a selected companion boat out of the N boats is opened independently for a period of time before the collision.

If there is no compression shock wave due to reflection, the traversing piston 1
7 is not repelled and the 1 passage 43 is constantly closed. Therefore, the pressure acting on the piston JJtlC is balanced. Piston: yjjq) Due to the area difference, the piston 1
1 moves to the left Ks in FIG. 1, so that the stroke length of the hammer piston decreases until the damping piston 17 begins to spring back 6 Due to the periodic springing movement, air leaks through the passage 1643, This allows room j
The pressure at 7 yen decreases and the piston stops moving to the left in FIG. The piston needs to be balanced at a position where the buffer piston 17 makes almost no rebound movement, which means that the amount of energy reflected as a pressure wave is significant. The balance of the piston is the difference in area,
Restrictions 4-1 are limited by the supply air pressure and, of course, by the damping piston 17. The dashpot piston it retards the movement of the buffer piston 17 and controls t*
stabilized at

If the jackhammer bit is new or has been newly resharpened, the stroke length will be automatically reduced and the stroke length will be automatically reduced due to this) The machine bit does not wear unnecessarily quickly, so the stroke length increases as the drill bit wears. The stroke lever is also automatically probed against the length of the jackhammer stem depending on the nature of the rock and the extension of the rod.

FIG. 2 shows another embodiment of the device for controlling the pin 4ILl. A plunger piston 71 is fixed to the pin at, a check valve 7J is installed, and the cylinder chamber/I of the buffer piston/7 is connected to the cylinder chamber/I of the buffer piston/7 through nine passages 7. Cylinder chamber 7 of plunger piston 71
# is directly connected. The reverse valve 73 is bypassed by a bypass passage 7j, and a restriction part 7 is provided in this passage 7j.
There are 6. Pin 4At and plunger piston 71
The wide cylinder is divided into two 7-ring chambers 71, 7 by an annular land 77 between them. The cylinder chamber 7t is constantly connected to the drain via the passage 10, and the cylinder chamber 7t is constantly pressurized via the passage 1/. In order to avoid sensitivity to the pressure level of the fluid main system, the annular area in the cylinder chamber 7 must be equal to the plunger area. The spring 1 is configured to press the bottle 1 to the left in FIG.

During the rock drilling operation, the pressure inside the chamber It reaches a peak value due to the rebound of the Il technique piston 17. The check valve 7J, which is closed at the normal pressure level, opens at each peak pressure to supply a small amount of fluid to the plunger cylinder 7#, and the plunger piston 7J resists the action of the spring to close the pin at is moved to the right in the drawing, so that the length of the stroke of the nominal piston IJ increases as described with reference to FIG. Rebounding motion is reduced11
! .

The spring t forces the plunger 71 and pin t to the left in FIG. 2 until the rebound increases again. In this way, as in the example of Fig. 1 (,
The pin at is controlled in response to the pressure S* strike wave.

In the impact motor shown in Figures 1 and 2, the buffer piston 17 is pushed forward to the limited normal position, and the feed force applied to the outer casing is less than the force applied to the piston surface of the buffer piston. Provided that the damping piston 17 returns to or nearly returns to the limited normal position before each impact.

FIG. Floating 1iK as shown in Figure 3
be. Pin reference 1 controls only valve control passage J7 and does not control valve control passage J7, pin at is controlled by compressed air at control pressure as shown in FIG. II1, but as shown in FIG. The ventilation method is different from the example in that 1 passage ≦ 3. Compressed air at a control pressure is supplied to the chamber It from the supply passage II through the check valve It, and as a result, the air in the chamber At is is configured to form a ridge. The massive piston surface tt#i of the counter piston 17 is located within the cylinder chamber 17, and when in use, the cylinder chamber 17 is connected to the supply passage l! It is constantly pressurized by the joints and shafts connected to it.

It is necessary that the piston surface it of the counter piston 17 is substantially smaller than the piston surface of the buffer piston 17.

When starting rock drilling, compressed air is first supplied to the supply passage 4o, At
, IIK are supplied, and the buffer piston 17 moves to the left in FIG. Except for supplying the feed force to the outer casing // to start the impact motor, the outer casing // moves forward, i.e.
The buffer piston /17 moves inwardly into the outer casing //, thereby.

The air in the chamber lt is compressed until the resultant force of the air splash force acting on the surface 2 and the force acting on the surface it balances the resultant force of the thrust force and the internal reaction force.

When the buffer piston rebounds, the counter piston t7 follows, but since the acceleration of the rebound 9 is extremely high, a gap O is temporarily created between the buffer piston 17 and the counter piston t7. This temporary gap creates a leakage path through which the path t3 connects to the anvil l.
It is vented to the atmosphere through the gap 2/ between the piston and the counter piston t7. By venting the passage t3 in this manner, the position of the pin hole t is controlled in the same manner as described with respect to FIG.

In the embodiments described above, only motion related to reflected compressive shock waves is sensed. - Neither the secondary compression shock wave nor the reflected tensile shock wave causes the bouncing of the loose piston/7, which allows the device to have a very simple construction.

Alternatively, the motion of the rock drill stem can be sensed by one, for example, a light emitter, an optical fiber bundle, and a photocell. The electrical signal from the photocell can be analyzed and processed to obtain a control signal for controlling a control pin of the type illustrated above or other SRS device for adjusting the striking speed of the hammer piston. . It is thus advantageous to compare the movements associated with one reflected shock wave with the primary shock wave and to adjust the strike velocity in response to the ratio of the lengths of these movements.

When the impact device shown in Fig. 1, Fig. 3 or Fig. 3 is used as a rock drill, the front end' is shown in Fig. 8g. One part of the non-circular expanding part of the adapter L, which is the ridge end surface /j, engages the chuck bushing λ, and this bushing is provided with an insertion bushing J, so that the insertion bushing is connected to the chuck bushing. The gear busher λ is rotated once by a rotary motor (not shown) via a drive shaft j and a gear device P4c.

For turning, there are only l bauds) 71-, each with μ passages intersecting the hole u7, and only l bauds) 4Cj~, each with μ passages intersecting the hole $7.
14 shows that W control was performed virtually steplessly. For this purpose, it is advantageous and desirable to have the separate boats and their passageways axially superimposed on each other, so that the boats and their respective passageways may be arranged so that they are axially superimposed on each other but remain separate. One example can be arranged axially in two or three rows.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of an impact motor according to the present invention, such as an equilibrated motor for a rock drill, FIG. A vertical cross-sectional view of an impact motor according to a third embodiment of the present invention, the reference figure is a longitudinal view of the front end of the rock drill equipped with the impact motor shown in Figure m1, Figure 1 or Figure 3, facing in the vertical direction. be. l3...Hammer piston, /41!・・・・・・
...Anvil. 17...Buffer piston, Hirol...Cylindrical pin. jj...Piston, 7/...Plunger piston.

Claims (1)

[Claims] t. Controlling an impact motor having a reciprocating hammer piston α1 to convert kinetic energy into shock wave energy when applying an impact onto an anvil I. In an impact motor control method that transmits this shock wave energy to a long and slender tool such as a rock drill stem or chisel, the reflected shock wave is sensed and the reflected shock wave is responded to so as to minimize the reflected shock wave energy. An impact motor control method characterized in that the impact speed of the hammer piston α is adjusted by 2 The stroke length of the hammer piston α-ken is #11
2. A method as claimed in claim 1, characterized in that the impact speed of the hammer piston is adjusted by adjusting the impact velocity of the hammer piston. 3. The method according to claim 1 or 2, characterized in that the impact velocity of the hammer piston 03 is adjusted so that the reflected shock wave energy is reduced and is preferably in the form of compression wave energy. . A method according to any one of claims ii-i, characterized in that the motion coupled to the reflected shock wave is sensed. Sensing the motion coupled to the reflected shock wave and the Wb motion coupled to the primary shock wave, and adjusting the shock velocity k in response to the ratio of the lengths of the motion.
The method described in Section 3. (v) a reciprocating hammer piston Q3 configured to convert kinetic energy into shock wave energy in a gland that impacts on anvil A4 and transmits this shock wave energy to an elongated tool such as a jackhammer stem or a chisel; This Hough 1 - a Nk device that increases the velocity of the piston OII to v4 - senses the movement coupled to the reflected shock wave and responds to the amount of the reflected AS wave to minimize the reflected shock wave energy. 7. A ninjaku seven-tater characterized by comprising a device (55, 71) for controlling the mu-gi outfit. 7 Elastically the father shape uJ to transmit the feed blade to the front tool
The sensing device is provided with a strand σn, and detects the rebound of the deformable strand 0η and controls the g4 adjusting device so that the rebound of the deformable strand aη is reduced. (55) is constructed by t++
An impact motor according to claim 4 of the patent claim.