JPS58155180A - Synchronous vibration striking hammer - Google Patents

Abstract

A vibratory impact hammer (1) including a hammer body assemblage (9) suspended by rubber mounts (11) for reciprocal axial movement in a support frame (3), the rubber mounts providing guiding and damping action of the assemblage in either direction of axial movement without extraneous friction forces acting thereupon, and a pair of synchronously driven eccentric weights (19,21) which are arranged to provide vibratory movement of the assemblage.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a synchronous vibratory hammer employing a driving and driven eccentric weight arranged to produce a vibrational action that can be used to impact a tool against a work surface.

Vibratory hand technology of the type to which this invention relates is well developed, and various designs have been proposed and used successfully. Bernard Ei Centielli
d A century) in 1975 2
One representative example of this conventional vibratory hammer is described in U.S. Pat.

The superheavy invention has a significant number of elements in common with the Sennaeri patent, but the Sennaeri patent's Guide (186) and (1
There are few differences in important respects, such as the absence of mechanical damping that could absorb energy, such as occurs in 88). The mechanical brake in the Centieri patent is used to control the non-linear movement of a hammer member driven by a single eccentric, whereas the device of the present invention uses two eccentrics. , eliminating the need for this type of mechanical brake.

The device of the present invention requires less maintenance than vibratory hammers which have non-linear shock vibrations that not only vibrate the hammer support mechanism but also cause significant wear and tear.

The principal object of the invention is to provide a drive hammer with good operating efficiency and low maintenance costs.'' These and other objects and features of the invention are illustrated in the respective figures. 5. Referring now to FIGS. 111 and 8112, reference numeral (
1) shows a vibratory hammer with a support frame consisting of a pair of side plates, the latter comprising a tubular spacing rod (5) welded to the side plates and a tool support member (7) also welded thereto.
are kept parallel by. The hammer structure (9) (Fig. 6) is located between the side plate (3) and the hole between the side plate and the hammer structure.
The mounts are suspended by an elastic member consisting of four rubber mounts (11) fi fixed at (13) and (15). Acts as a single guide and damping member for the structure.

The hammer structure (9) is supported by a roller bearing (25) located at the end cap (27) and is an eccentric housing a pair of eccentric weight bodies (19) and (21) mounted on the nine shafts (23). It has a weight body chamber (17), and the end cap is attached to the eccentric weight body chamber (17) with a pole (32) and fixed with nine plate members (31) (29). Fixed to the eccentric weight single body chamber (17) and protruding from its upper surface is the upper arm member (53) fixed to the rubber mounting base (11X) at the pole (15).

A reinforcing member (37) is fixed to the eccentric weight body chamber (17) and protrudes from the bottom thereof, which is a lower arm member (35) attached to the rubber mounting base (11) at (15). ) are fixed to both sides of the lower arm member (35) and to the heshim structure (9) in the stabilizing rounding of the arm member. Eccentric weight body (19) t - Shaft (
Fixed to one end of 23) is a nine hydraulic motor (59). shirt) (23) A pair of teeth 4 attached to
1) is arranged at the ninth point transmitting rotational motion from the shaft supporting the eccentric weight body (19) to the shaft supporting the eccentric weight body (21), so that both types of masses rotate at the same speed in opposite directions K11. do. A hose member (43) supplies pressurized fluid from a power source (not shown) to the motor (39) as needed.

At the lower end of the arm member (35) there is a striking plate (45) fixed thereto by a pin (47), the striking plate is attached to the tool support member (7) K as best seen in FIG. It is arranged so as to apply a K1ft blow to the top of the bell-shaped tool (49). A reciprocating movement of the tool is enabled by a holding device comprising a key (51) projecting into a groove (53) formed in the tool (49). The tool is supported in the bushing housing (57). 1fi), but the bushing housing is attached to the head screw (61
) is fixed to one end of the tool support member at the tool stop plate ( ).
59), the position is held so as not to move in the axial direction.

The support device for the vibratory hammer (1) comprises a link structure (63
).

A vibrating hand made according to the invention disclosed herein! The design specifications will obviously vary depending on the desired impact work output.

It is well known that when the forced frequency is a mass vibrating at the solid frequency, the mass of the forced frequency oscillator is 90 degrees in phase with the mass being vibrated. If the forced frequency is much higher than the natural frequency, one forced frequency mass can lead the mass being vibrated by 180 degrees.

Therefore, for a 135 degree advance, the vertical component of the centrifugal force of the vibrating mass combined with the stored energy of the rubber mount will generate the maximum impact force on the tool (49).

The best phase angle of 135 degrees (0) is determined by the following equation.

Where: # = Phase angle ζ - Damping rate f - Forced frequency CPM, Lacaun/Second natural frequency Plotting the frequency ratio against # under various damping rates K Therefore, below the critical damping system (as shown to produce a phase angle of about 180 degrees at frequency ratios greater than 1), therefore critical damping of the system is essential to obtain the best operating results. Critical damping, by definition, means that when a mass is moved from its rest position and returned to the same rest position, it does not oscillate excessively. Critical damping is achieved in this vibratory hammer by preloading using a rubber work stand (11).

For best behavior, ahem! It is important that the stroke of is equal to the displacement "in the air"(S#), and this compliment (
S") is given by the following equation.

Where: W - Unimpinged weight r = Unbalanced weight Radius away from the center of rotation W - Total vibration weight Applying these formulas, the vibratory hammer of the present invention has an impact work output of 120 Orpm and a 2007-to-bond (216
If #−m) is required, it will have the following numerical value.

Stroke (L4144 inches (1,052 m) Weight of hammer structure (9) 485.52 lbs (22α
23-) W = 60.69 bond (# to 27,71)
r = 1.6576 inte(4,21am) wr=
10639 inch bond (192kt-aIA) manager =
166.76 inches 3 pounds (76α8-proverb) K =
3400 $A7chi (2!19 mma7fx*
)

[Brief explanation of the drawing]

FIG. 1 is a side view of a vibrating hammer implementing the principle of the present invention;
Figure 2 is an enlarged sectional view taken from line 2-2 in Figure 1, and Figures 3, 4 and g5 are taken from lines 3-3, 4-4 and 5-5 in Figure 2, respectively. The sectional view, FIG. 6, is an external view of the hammer main body parts used in the apparatus of FIG. 1... Vibration shock hammer, 3... Vibration frame, 11
...Elastic member, rubber I11/iL base, 17...-
19... Drive eccentric weight body, 21... Driven eccentric weight body, 39... Prime mover device, 41... Gear device, 19.21, 39.41... Vibration drive device, 49
...Tool, 51,55.59-...Tool supporter, 6
1... Tool removal member. Agent Patent Attorney Sanro KimuraFIG, 1 FIG, 3 FIG, 4 FIG, 6

Claims (1)

Scope of Claims: (1) In a vibration impact hammer having seven supporting frames, the supporting seven frames are arranged by elastic members arranged so as to provide guidance and damping in both directions of axial movement of the hammer structure.
A hammer structure suspended in a frame, a vibration drive device arranged so that the hammer structure vibrates in the axial direction, and a vibration drive device installed in a supporting frame so that it can reciprocate, when the vibration drive device moves it back and forth. and a tool located so as to receive the impact force of the hammer structure, and the elastic member is the only member that engages with the hammer structure so that external friction force is avoided. i. (2) The vibration impact hammer according to claim 1, wherein the elastic member is a rubber mount. (3) A plurality of pairs of the rubber stud mounting bases are arranged, one of which is located at the upper part of the hammer structure, and the other is located at the lower part of the hammer structure. Vibration impact hanger 10 (4) The vibration drive device has a driving eccentric device, a driven eccentric weight body, and a prime mover device that rotates both types of weight bodies in synchronization. The vibratory impact hammer described in Section. (5# 1 of claims 1 to 4, characterized in that the electrocardiogram mass bodies are connected by a gear system.
Vibration and shock described in ! . (63) The vibratory impact hammer according to claim 1, characterized in that a tool support member is provided for the work odor, and the tool support member has a member for removing the tool from the hammer. (7) Forced The phase angle of the vibration frequency is 1 from the frequency of the heavy object being vibrated.
The vibration impact hammer according to claim 1, characterized in that it is advanced by 35 degrees. (8) The stroke of the hammer structure is equal to 2WK, where W is the unimpinged weight, the radius at which the r-spring balance is away from the center of rotation, and W is the total oscillating weight. ! 16 (9) Shock work output is 27.2 at 1200 rpm #-
m (200ft-tba) hammer has a stroke of 1.
052a1 ((L4144 inch)) and has the following design parameters, the vibration impact hammer according to claim 1 to claim 8,
KW-22 (123kg (4B5B2 g y )
”), w −27,71 to #(6 (169 bond), r
-4213IC1,6576 inches). VR-123 #-31 (106,59 inch-bond), WR” = 488 m-aj (166,67 lb-in?”) K Spring rate (11th term) Tomi 2391
晦/aa (3400 cm/inch).