U.S. patent number 3,827,507 [Application Number 05/289,787] was granted by the patent office on 1974-08-06 for hydraulically powered demolition device.
This patent grant is currently assigned to Construction Technology, Inc.. Invention is credited to Raymond E. Lance.
United States Patent |
3,827,507 |
Lance |
August 6, 1974 |
**Please see images for:
( Certificate of Correction ) ** |
HYDRAULICALLY POWERED DEMOLITION DEVICE
Abstract
A hydraulic hammer for driving a demolition tool is disclosed.
The hammer carries a piston which reciprocates in a cylinder. High
pressure fluid drives the hammer to a retracted position to
compress an air spring. The piston is momentarily held in the
retracted position while an annular valve sleeve disposed about the
piston is automatically moved downwardly by differential fluid
pressure to open an annular passageway around the piston to permit
the fluid to freely bypass the piston. The piston is then released
so that the stored energy rapidly accelerates the hammer through an
impact stroke without significant impedance from fluid and without
displacing fluid from the cylinder. Since high pressure fluid is
required only on the retraction stroke, the volume of fluid
necessary to operate the hammer is essentially reduced by 50
percent, thus permitting either the force or frequency to be
doubled for a given high pressure fluid source. A safety shuttle
valve is also included which is cooperable with the tool member to
bypass pressure fluid to reservoir until a predetermined load is
imposed on the tool.
Inventors: |
Lance; Raymond E. (Fort Worth,
TX) |
Assignee: |
Construction Technology, Inc.
(Grand Prairie, TX)
|
Family
ID: |
23113094 |
Appl.
No.: |
05/289,787 |
Filed: |
September 18, 1972 |
Current U.S.
Class: |
173/15; 91/276;
173/DIG.4; 173/127; 92/130R; 173/204 |
Current CPC
Class: |
B25D
9/12 (20130101); B25D 9/145 (20130101); E02F
3/966 (20130101); Y10S 173/04 (20130101) |
Current International
Class: |
B25D
9/12 (20060101); B25D 9/14 (20060101); B25D
9/00 (20060101); B25d 009/02 () |
Field of
Search: |
;173/119,134,16,17,15
;91/276,300,328,173,423,165 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Abbott; Frank L.
Assistant Examiner: Pate; William F.
Attorney, Agent or Firm: Hubbard, Thurman, Turner &
Tucker
Claims
What is claimed is:
1. A hydraulic impact device for applying impact forces to a tool
assembly comprising:
a housing having an axial bore,
a hammer member slidable in the housing and defining with said bore
a cylinder chamber,
energy storage means adapted when compressed to accelerate the
hammer in a first direction to deliver an impacting blow to the
tool assembly when the hammer is released,
piston means carried on the hammer dividing the cylinder chamber
into first and second pressure chambers and movable between first
and second positions, the first chamber being that which when
pressurized causes the piston to move the hammer in a second
direction to the second position to compress the energy storage
device,
a high pressure inlet port in the housing communicating with the
first chamber,
a first outlet port communicating with the second chamber, and
valve means in slidable contact with the bore and in sealing
contact with the piston to cooperate with the piston and
selectively isolate the first chamber from the first outlet port
whereby the piston and valve are moved in the second direction, the
valve being shiftable in the first direction when the piston
reaches the second position to provide open communication between
the first chamber and the second chamber and thus the first outlet
port to permit the storage device to accelerate the hammer by
permitting relatively unrestricted return of said piston in said
first direction without significant displacement of fluid from the
housing.
2. The device of claim 1 wherein said energy storage device
comprises a compliant chamber containing a compressible fluid.
3. The device of claim 1 wherein said energy storage device is an
air spring.
4. The device of claim 1 further including second valve means for
bypassing fluid from said first chamber until at least a
predetermined load is applied to said hammer.
5. The impact device comprising:
a housing defining a cylindrical chamber,
a compressible energy storage means attached to the housing at one
end of the cylindrical chamber,
a hammer reciprocally disposed in the cylindrical chamber to leave
an annular cavity therein and positioned to compress the energy
storage device when moved in a first direction and to impact a tool
assembly disposed at the other end of the housing when moved in a
second direction,
a piston mounted on the hammer and disposed within the annular
cavity, the piston being sized to leave a substantial annular
opening between the piston and the housing,
a low pressure exhaust port in fluid communication with the end of
the annular cavity near the energy storage means,
a high pressure inlet port in fluid communication with the other
end of the annular cavity, and
a valve sleeve reciprocally disposed in the housing and sealingly
engaging the piston and the housing to divide the annular cavity
into first and second expansible fluid chambers when in contact
with the piston whereby the piston will move the hammer through a
compression stroke to compress the energy storage means, and,
alternatively, to freely pass fluid around the piston when
separated from the piston to permit the energy storage means to
freely accelerate the hammer through an impact stroke to impact the
tool assembly,
both ends of the valve sleeve being entirely exposed to hydraulic
fluid and pressure shiftable in the direction of the impact stroke
when the valve sleeve is separated from the piston as a result of
only the supply and return hydraulic pressures.
6. A hydraulic impact device for applying impact forces to a body
comprising:
a housing having first, second and third housing sections,
a hammer member having a head in said first housing section and
having an axial shaft section extending into a bore in said second
section, said hammer shaft and said bore defining an annular
cylinder chamber,
said third section housing an anvil and chisel, said chisel adapted
to be impacted by said hammer through said anvil,
energy storage means contained in said first section and engagable
with said hammer head and adapted when activated to transmit stored
energy to said hammer to move said hammer in a first direction to
deliver an impacting blow,
piston means carried on said hammer dividing said cylinder chamber
into first and second pressure chambers, said first chamber when
pressurized causing said piston to move said hammer in a second
direction against said energy storage device to activate same,
a first outlet port housing communicating with said second
chamber,
a second outlet port in communication with said first chamber,
a supply port in communication with said first chamber, and
sequencing valve means in slidable contact with said bore and said
piston, said valve movable in the second direction to isolate said
first chamber from said second outlet port and from said second
chamber whereby said hammer is moved in said second direction to
activate said energy storage means, said valve shiftable in the
first direction upon predetermined movement of said piston to
separate the valve from the piston and openly communicate said
first chamber with said second outlet
across said valve thereby initiating transfer of energy from the
storage means to the hammer by permitting relatively unrestricted
return of said piston in said first direction.
7. A hydraulic impact device for applying impact force to a body
comprising:
a housing having upper, intermediate and lower sections,
said upper section including a frame having an upper bearing plate
and a lower bearing plate,
a hammer member having an enlarged head in said upper section and
an axial shaft portion extending through said lower bearing plate
into a bore in said intermediate section,
an anvil and blade member reciprocable in said lower section
adapted to be impacted by said hammer,
air bag means contained in said upper section and engagable with
said hammer and adapted when compressed to expand transmitting
stored energy to said hammer to move said hammer in said first
direction,
said bore in said intermediate section having an axial section of a
first increased diameter and a second section of reduced diameter,
said bore defining with said hammer shaft a cylinder chamber
enclosed at the ends by bearing members,
piston means carried on said hammer shaft dividing said cylinder
chamber into first and second pressure chambers, said first chamber
when pressurized causing said piston to move said hammer in a
second direction against said air bag to compress same,
a first outlet port communicating with said second chamber,
a second outlet port communicating with major diametral bore
section adjacent said reduced diametral section,
an inlet port communicating with said first chamber, and
sequencing valve means having a generally annular body having an
inner surface adapted to slidably contact said piston and with a
first outer end portion in slidable contact with said minor bore
and a second outer portion in slidable contact with said major
bore, said valve means slidable from a first position abutting said
lower bearing to a second piston abutting said upper bearing, said
valve caused to reciprocate from said first position to said second
by inlet pressure and caused to move from said second position to
said first by fluid pressure at said second spool end when said
piston reaches a predetermined position thereby venting said first
chamber through said second outlet permitting expansion of said air
bag and relatively unrestricted return of said piston.
8. The device of claim 7 further including second inlet means and
third outlet means adjacent said second inlet means and shuttle
valve means having a groove therein, said shuttle valve being
biased to a position communicating said second inlet and third
outlet across said groove to bypass fluid from said first chamber
and movable to terminate communication therebetween by
predetermined movement of said anvil in said second direction.
9. The impact device comprising:
a housing defining a cylindrical chamber,
a compressible energy storage means attached to the housing at one
end of the cylindrical chamber,
a hammer reciprocally disposed in the cylindrical chamber to leave
an annular cavity therein and positioned to compress the energy
storage device when moved in a first direction and to impact a tool
assembly disposed at the other end of the housing when moved in a
second direction,
a piston mounted on the hammer and disposed within the annular
cavity, the piston being sized to leave a substantial annular
opening between the piston and the housing,
a low pressure exhaust port in fluid communication with the end of
the annular cavity near the energy storage means,
a high pressure inlet port in fluid communication with the other
end of the annular cavity, ane
a valve sleeve reciprocally disposed in the housing and sealingly
engaging the piston and the housing to divide the annular cavity
into first and second expansible fluid chambers when in contact
with the piston whereby the piston will move the hammer through a
compression stroke to compress the energy storage means, and,
alternatively, to freely pass fluid around the piston when
separated from the piston to permit the energy storage means to
freely accelerate the hammer through an impact stroke to impact the
tool assembly,
The valve sleeve having area such as to be being pressure shiftable
in response to high hydraulic pressure on each end thereof as a
result of being separated from the piston, and being mechanically
separated from the piston when the piston has reached a
predetermined position in the annular cavity.
10. The impact device comprising:
a housing defining a cylindrical chamber,
a compressible energy storage means attached to the housing at one
end of the cylindrical chamber,
a hammer reciprocally disposed in the cylindrical chamber to leave
an annular cavity therein and positioned to compress the energy
storage device when moved in a first direction and to impact a tool
assembly disposed at the other end of the housing when moved in a
second direction,
a piston mounted on the hammer and disposed within the annular
cavity, the piston being sized to leave a substantial annular
opening between the piston and the housing,
a low pressure exhaust port in fluid communication with the end of
the annular cavity near the energy storage means,
a high pressure inlet port in fluid communication with the other
end of the annular cavity,
a valve sleeve reciprocally disposed in the housing and sealingly
engaging the piston and the housing to divide the annular cavity
into first and second expansible fluid chambers when in contact
with the piston whereby the piston will move the hammer through a
compression stroke to compress the energy storage means, and,
alternatively, to freely pass fluid around the piston when
separated from the piston to permit the energy storage means to
freely accelerate the hammer through an impact stroke to impact the
tool assembly,
the valve sleeve being pressure shiftable in response to high
pressure on each end thereof as a result of being separated from
the piston, an being mechanically separated from the piston when
the piston has reached a predetermined in the annular cavity,
means forming an annular seal with the piston when the piston has
reached the predetermined position in the annular cavity to hold
the piston at the end of the compression stroke, and
a second low pressure exhaust port placed in fluid communication
with the first fluid chamber only when the sleeve valve is in a
predetermined position near the tool assembly end of the housing to
release the piston to start the impact stroke.
11. A hydraulic impact device for applying impact forces to a body
comprising:
a housing having first, second and third housing sections,
a hammer member having a head in said first housing section and
having an axial shaft section extending into a bore in said second
section, said hammer shaft and said bore defining an annular
cylinder chamber,
said third section housing an anvil and chisel, said chisel adapted
to be impacted by said hammer through said anvil,
energy storage means contained in said first section and engagable
with said hammer head and adapted when activated to transmit stored
energy to said hammer to move said hammer in a first direction to
deliver an impacting blow,
piston means carried on said hammer dividing said cylinder chamber
into first and second pressure chambers, said first chamber when
pressurized causing said piston to move said hammer in a second
direction against said energy storage device to activate same,
a first outlet port housing communicating with said second
chamber,
a second outlet port in communication with said first chamber,
a supply port in communication with said first chamber,
sequencing valve means in slidable sealing contact with said bore
and said piston, said valve movable in the second direction to
isolate said first chamber from said second outlet port and from
said second chamber whereby said hammer is moved in said second
direction to activate said energy storage means, said valve
shiftable in the first direction upon predetermined movement of
said piston to openly communicate said first chamber with said
second outlet across said valve thereby initiating transfer of
energy from the storage means to the hammer by permitting
relatively unrestricted return of said piston in said first
direction, and
said sequencing valve having a first surface disposed in said first
chamber and an opposite second surface, said second surface having
greater cross-section area than said first and cooperable with said
piston whereby upon said piston reaching said predetermined
position fluid pressure acting at said second surface will shift
said valve.
12. The device of claim 11 further including shuttle valve means
having a first position bypassing fluid from said first chamber to
a low pressure reservoir and a second flow blocking position, said
shuttle valve being biased to said first position and adapted to be
moved to said second position by a predetermined force being
applied to move said hammer in said second direction.
13. The impact device for applying repetitive impact forces to a
tool assembly comprising:
a housing having a bore,
an axially slidable hammer member in the bore for impacting the
tool assembly,
energy storage means adapted to transmit energy to accelerate the
hammer to impact the tool assembly,
piston means carried on the hammer in the bore defining opposite
first and second fluid chambers, and
valving means for limiting high pressure fluid to the first chamber
to move the hammer against the energy storage device, and for
placing the first chamber in fluid communication with the second
chamber when the piston has reached a predetermined position to
thereby permit the energy storage device to accelerate the hammer
to impact the tool assembly as the fluid moves from the first
chamber to the second chamber, and for again limiting high pressure
fluid to the first chamber when the piston has reached a
predetermined second position to repeat the cycle,
the valving means including a sleeve forming a peripheral fluid
seal between the piston and the cylinder, the sleeve being shifted
away from the piston to place the first chamber in fluid
communication with the second chamber, the opposite ends of the
valving means being exposed entirely to hydraulic fluid in either
the first or second fluid chambers and being pressure shiftable
toward the second position of the piston when separated from the
piston and being maintained in sealing engagement with the piston
by fluid pressure as the piston moves from the second position to
the first position.
14. The impact device for applying repetitive impact forces to a
tool assembly comprising:
a housing having a bore,
an axially slidable hammer member in the bore for impacting the
tool assembly,
energy storage means adapted to transmit energy to accelerate the
hammer to impact the tool assembly,
piston means carried on the hammer in the bore defining opposite
first and second fluid chambers,
valving means for limiting high pressure fluid to the first chamber
to move the hammer against the energy storage device, and for
placing the first chamber in fluid communication with the second
chamber when the piston has reached a predetermined position to
thereby permit the energy storage device to accelerate the hammer
to impact the tool assembly as the fluid moves from the first
chamber to the second chamber, and for again limiting high pressure
fluid to the first chamber when the piston has reached a
predetermined second position to repeat the cycle,
the valving means including a sleeve forming a peripheral fluid
seal between the piston and the cylinder, the sleeve being shifted
away from the piston in the direction of the impact stroke to place
the first chamber in fluid communication with the second chamber,
and
means for momentarily retaining the piston against the force of the
storage means until the sleeve has separated from the piston a
distance sufficient to prevent the piston from overtaking the
sleeve until the hammer has closely approached the point of impact
with the tool assembly.
Description
The present invention relates generally to a fluid powered
repetitive impact device, and more specifically relates to a
hydraulic demolition hammer.
Reciprocating tools for delivering high impact blows to demolish
pavement, rock, and the like are well known. These impact tools
have heretofore been predominately driven by air pressure and are
characterized by the well-known jackhammer. Large versions of the
jackhammer have heretofore been mounted on the boom of a backhoe.
These devices are characterized by being able to deliver relatively
high frequency, but relatively low impact forces. As a result, even
the larger of these devices tends to powder the harder materials
due to the relatively low force. However, the high frequency to
some extent compensates for this deficiency. Additionally, air
driven hammers of this type produce a very high noise level as a
result of the rapid venting of the air from the cylinder. This is
particularly objectionable in metropolitan areas where a major
portion of this type of activity is carried out, and the resulting
noise pollution is coming under increasingly severe criticism.
A hydraulically driven hydraulic hammer has offered for a long time
the potential of increased forces required to fracture concrete,
rock and similar materials. Additionally, hydraulically driven
devices tend to be much quieter as a result of eliminating the
venting noise from an air hammer. However, no hydraulic hammer has
heretofore been introduced to the market having sufficient
reliability to gain wide acceptance. Additionally, hydraulic
hammers of this type have heretofore been relatively inefficient
because of the problem of venting the hydraulic fluid from the low
pressure side of the piston during the impact stroke. One approach
which has heretofore been taken to overcome this deficiency is to
drive a hammer against an air spring during a retraction or
compression stroke by means of a hydraulic linear actuator
including a piston and cylinder, and then by disconnecting the
hydraulic actuator from the hammer to allow the energy stored in
the spring to accelerate the hammer against the demolition tool.
These devices have not only proven to be unreliable, but are also
relatively slow in that hydraulic power fluid must return the
linear actuator to effect mechanical reengagement with the hammer
after each impact stroke in preparation for the next compression
stroke.
The present invention is concerned with an impact device of this
type which is hydraulically driven and relatively quiet, is capable
of delivering an impact stroke of high efficiency because it is
substantially unimpeded by fluid an does not require a mechanical
disconnect and reconnect during each cycle, and which uses high
pressure fluid only during the compression stroke to provide, for a
given hydraulic power supply, either twice the impact force, or
twice the frequency of a device employing a double acting
piston.
More specifically, the present invention is concerned with an
impact device in which the shaft of a hydraulic linear actuator is
a reciprocating hammer. Hydraulic fluid is applied to one face of
the piston of the actuator to drive the hammer through a retraction
stroke to compress an air spring. Fluid pressure is then
efficiently bypassed from one side of the piston to the other to
permit the air spring to accelerate the hammer without the
hydraulic fluid materially impeding its motion. Since no hydraulic
fluid is displaced from the cylinder during the impact stroke, the
volume of hydraulic fluid required is reduced substantially in
half. The hammer thus freely impacts an anvil of a tool assembly
which transfers the energy to the material to be demolished.
In the preferred form of the invention, the piston and a sleeve
valve effectively divide the cylinder into two fluid expansible
chambers during the retraction stroke. However, at the end of the
retraction stroke, the sleeve is separated from the piston while
the piston is retained at the top of the retraction stroke during
the downward stroke to permit the hydraulic fluid to bypass the
piston.
Still more specifically, the piston moves into a retaining cavity
at the top of the retraction stroke as the valve sleeve is
mechanically separated from the piston. The valve sleeve is then
shifted to the end of the impact stroke by differential pressure at
which time an exhaust port is opened to release the piston from the
retaining cavity to start the impact stroke.
Additional details and features of the preferred embodiments of the
invention are set forth in the appended claims. The invention
itself, however, as well as other objects and advantages thereof,
may best be understood by reference to the following detailed
description of illustrative embodiments, when read in conjunction
with the accompanying drawings, wherein:
FIG. 1 shows a side view of the hammer of the present invention
mounted on the end of a conventional backhoe boom;
FIG. 2 is a longitudinal sectional view illustrating the details of
the present invention;
FIG. 2A is an enlarged view of the center portion of the sectional
view of FIG. 2;
FIG. 3 is a sectional view taken along lines 3--3 of FIG. 2;
and
FIGS. 4 through 7, in simplified schematic form, illustrate the
operation of the hammer.
Referring now to the drawings, a demolition device in accordance
with the present invention is indicated generally by the numeral 10
in FIG. 1. The demolition device 10 is mounted on a pair of bracket
plates 14 which are connected to the end of boom 11 of a typical
construction machinery unit such as a backhoe, not shown. As is
conventional with such machinery, boom 11 may be swung horizontally
or raised vertically to hold the device 10 against any desired
object with considerable force. A hydraulic cylinder 15 is
associated with the boom 11 and is employed to pivot the hammer
structure 10 about pinned construction 12. Hydraulic lines 84 and
64 connect the hammer to a source of fluid pressure and to a
reservoir. The demolition or breaking of hard objects such as
pavement, roadbeds, rocks and other materials is accomplished by
chisel tool 20 which engages the material.
In operation the device will generally assume a position as seen in
FIG. 1 and therefore throughout the specification the relative
terms "upper" and "lower" refer to a unit positioned as in FIG. 1.
The device is shown in FIG. 2 in a horizontal position with the
upper end to the left-hand side of the drawing for purposes of
illustration. The hammer 10 includes upper end chamber 22 which
houses the air spring or other similar energy storage device.
Chamber 22 is generally rectangular and is defined by a frame
including upper cover plate 23 and side members 25 which are joined
at their lower ends to base plate 24. Base plate 24 is provided
with a central circular opening 26 which receives the axial shaft
portion 27 of hammer member 28. Hammer 28 diverges at the upper end
to enlarged head 29 which is disposed within chamber 22. A cushion
plate 30 is interposed between tapered head 29 of the hammer and
base plate 24. Cushion plate 30 has a conical bore 32 which
receives generally frusto conical dampening member 34. A similarly
shaped hardened steel ring 35 is provided at the upper surface of
the dampening member 34 to abut the tapered underside of head 29
when the hammer is in the extended position. Typically, cushion
plate 30 would be formed of steel and cushion ring or dampening
member 34 of a suitable resilient material such as an elastomer or
rubber. Bearing plate 38 is secured to the upper end of hammer head
29 and approximately corresponds in diameter to the cushion plate
30. The upper surface of bearing plate 38 has circular cavity 39
which receives metal bumper pad 40. Pad 40 is an integral part of
air spring device 45 comprised of a compliant air chamber 42 having
a central retaining ring 43. Another bearing pad 44 is provided
between the surface of upper end of air chamber 42 and the inside
of cover plate 23 of the chamber 22.
The chamber 42 of air spring 45 is formed of a compliant material
such as fabric and rubber and iis inflatable to a predetermined
pressure with a compressible fluid such as air by means of a
suitable valve, not shown. As hammer 28 is restricted, the air
spring will be compressed, storing energy which is utilized to
drive the hammer downwardly on the impact stroke. The bearing pads
40 and 44 serve to distribute the thrust load of the hammer over
the area of the chamber and the cushion plate 30 absorbs energy if
for any reason the tool 20 is not in position to stop the travel of
the hammer before the head 29 reaches the plate 30. It will be
obvious to those skilled in the art that energy storing devices,
other than the air spring device shown could also be utilized. For
example, pneumatic air spring assembly 45 could be replaced with a
conventional compression spring and give similar results.
The main shaft portion 27 of hammer 28 extends axially within
intermediate cylindrical housing section 50. Housing section 50 is
provided with a stepped axial bore having upper major diametral
section 52 and reduced diametral section 53 at the lower end which
define annular expansible chambers 60 and 90, respectively, around
hammer section 27. The upper chamber 60 is closed by bearing member
55 which is generally annular and held in place by engagement at
interior shoulder 56 and abutting exterior snap ring 57. Concentric
bore 59 in member 55 bears against hammer shaft 27 and, along with
appropriate packing or sealing members 58, prevents fluid leakage
from annular cylinder chamber 60. An extension 62 of bearing 55
extends axially into chamber 60 and serves as an abutment for the
reciprocating internal valve sleeve. Exhaust port 61 communicates
with chamber 60 through bearing portion 62. Lower chamber 90 is
closed by bearing member 65 which similarly engages the housing
bore at shoulder 66 and is held in place against axial movement by
snap ring 67 engaging the bore and the end face of bearing member
65. Similar sealing members 68 engage the surface of shaft 27 at
concentric bore 69 to prevent leakage along the hammer shaft 27.
The inner end of member 65 is provided with interior circular
groove 92 extending adjacent bore 53.
Piston 70 in the form of a generally annular ring is affixed to
hammer shaft 27 by snap rings 72 and 73 which abut opposite faces
of the piston. The piston is provided with a frustro conical
surface 71 exposed to chamber 90 tapering from peripheral sealing
surface 74.
Reciprocation of the hammer is automatically effected by sequencing
valve 75. The valve 75 is in the form of a differential area
cylindrical sleeve 76 which is in sliding, sealed with bores 52 and
53. The differential area is provided by the difference in
diameters of the cylinder bores 52 and 53, the latter being the
smaller. Annular metal piston rings 88 and 78 provide sliding fluid
seals with the bores 52 and 53, respectively. In the position shown
in FIG. 1, valve sleeve 75 seals off outlet port 79 which is
connected to the low pressure reservoir. The upper end 80 of sleeve
76 is provided with a slight taper 81 to admit the piston 70 more
easily on the downstroke. An annular recess 82 extends around the
exterior of sleeve 76 at upper end 80 and one or more radial
notches 87 (see FIG. 3) provide fluid communication with the recess
82 when the sleeve abuts the lower end of bearing 55. As mentioned,
end 80 of valve 75 has a larger effective area than the opposite
end as a result in the difference in diameters of the bores 52 and
53, and thus will be rapidly shifted downwardly when high pressure
is applied to both ends of the sleeve as the piston 70 leaves the
sleeve on the upstroke.
Inlet port 91 communicates with chamber 90 at undercut groove 92 in
bearing member 65. The inner end 93 of the bearing serves as an
abutment to engage the end of sleeve valve 75 when the sleeve
assumes its lowermost position adjacent the tool end.
An anvil 120 is reciprocable in sleeve 95 below the terminal end of
the hammer. The anvil has an enlarged shoulder portion 121 which
slides within sleeve 95. Stub shaft 122 is impacted by the lower
end of hammer member 28.
Hammer 10 also incorporates a shuttle valve 100, which makes the
hammer inoperative by diverting high pressure fluid to a reservoir
until at least a predetermined load has been placed on the unit at
chisel 20. By virtue of the safety feature, the hammer cannot be
inadvertently actuated until the hammer is positioned in an
operative position. Shuttle valve 100, having a body member in the
form of a generally cylindrical sleeve 101, is positioned in
chamber 102 defined in sleeve 95. Chamber 102 has cylindrical
exterior walls 103 which enlarge at shoulder 108 to bore portion
104. High pressure port 106 and low pressure port 112 intersect the
chamber wall adjacent opposite sides of shoulder 108.
The outer surface of the valve sleeve 101 has a peripheral sliding
seal 109 within bore 104. In FIG. 2, valve 100 is shown in its
uppermost position with the lower end 116 of sleeve 101 engaging
shoulder 121 of anvil 120. Peripheral groove 105 extends in sleeve
101 defined by opposite ends 114 and 115. It will be observed that
end 115 is of greater cross-sectional area than end 114 due to the
increased bore diameter at 103.
Chisel or tool member 20 is reciprocable within lower bearing
member 126 and has an appropriately shaped blade end 130. Chisel 20
is formed having a flat face 127 extending longitudinally within
bearing 126. A removable pin 129 in bearing 126 engages the flat
face 127 to hold the chisel 20 in predetermined rotational position
and to retain the chisel 20 within the bearing but is permitted
axial movement as determined by the length of flat face 127. The
upper end 132 of chisel 130 abuts the lower end 131 of anvil
120.
The hammer 10 is held together by tie rods 145 which extend
longitudinally between recesses 144 in plate 24 at upper chamber 22
and recesses 141 in lower bearing member 126. It will be obvious
that the hammer can be easily disassembled by simply removing the
tie rods to permit bearing 126 to be removed, thus releasing
intermediate body section 50. Anvil 120 can then be removed and
removal of appropriate snap rings 57 and 67 will permit access to
the valving and piston components.
Bracket plates 14 are provided with inwardly depending plates 137
which receive bolts 139 to secure the brackets to the underside of
hammer plate 24. Bottom plate 150 secured between the bottom of the
brackets defines a socket 151 which receives a portion of tool
bearing member 126. The hammer 10 can be separated as a unit from
bracket plates 14 by removing bolts 139.
Ideally, the combined mass of hammer 28 and plate 38 is
approximately equal to the combined mass of anvil section 120 and
chisel 20. In this way, the unit is dynamically balanced and when
the compacting blows are dellivered by the hammer 28, undue
vibration and rebound of the unit is avoided and maximum energy
transfer is achieved.
The construction and operation of the hydraulic hammer of the
present invention will be better understood from the following
description of operation as shown schematically in FIGS. 4 to 7.
The unit initially is in an inactive mode as shown in FIG. 4 with
hammer 10 positioned by boom 11 so that chisel 20 engages the
material to be broken. The hammer is connected having inlet port 91
in communication with a source of fluid pressure 83 via line 84. A
bypass line 107 connects line 84 to inlet port 106. Port 112 is
connected to a low pressure reservoir 63 by line 113. Outlet or
exhaust ports 61 and 79 are similarly connected to a low pressure
reservoir 63 by line 64.
Referring to FIG. 4, when high pressure fluid is introduced into
chamber 105, the differential area between ends 114 and 115 results
in a net pressure force acting to urge valve 100 and the anvil 120
downwardly. As valve 100 moves downwardly, chamber 105 is placed in
communication with low pressure port 112, causing high pressure
fluid to be directed to reservoir 63. In this position the unit is
inoperable as high pressure fluid is bypassed directly to
reservoir, and accordingly, chamber 90 will not be pressurized to
actuate the hammer. When valve 100 is moved upwardly by virtue of
upward movement of anvil 120, due to the force exerted at chisel
20, chamber 105 will again be moved out of communication with
outlet port 112 with peripheral land 109 closing off port 112.
Supply fluid will again be directed via port 91 permitting
discharge pressure to build up in chamber 90. For typically
operating pressures, approximately 600 pounds of force will be
required at chisel 20 to overcome the differential hydraulic bias
forcing the sleeve valve 100 downwardly. Thus, the hammer cannot be
inadvertently actuated until a sufficient load is placed on the
hammer to insure that operation of the hammer is intended and that
the anvil is in position to prevent the hammer from striking plate
30.
As pressure builds up in chamber 90, valve 75 will be caused to
move rapidly upward into engagement with the inner end of upper
bearing member 55 as seen in FIG. 5. Intermediate exhaust port 79
will be sealed from communication with chamber 90 at groove 77 by
sealing ring 78. Fluid pressure in chamber 90 acting against the
area of piston 70, will cause piston 70 to move upwardly,
displacing the hammer. As hammer 28 moves upwardly, bearing plate
38 will compress air spring 45, storing energy in the spring.
During upward movement of the piston and hammer, cylinder chamber
90 expands in volume with pressure fluid being admitted at port 91.
Opposite cylinder chamber 60 contracts in volume with fluid being
exhausted through port 61 to reservoir.
When the piston 70 has reached the fully retracted position shown
in FIG. 6, the piston is within the interior surface of the inner
extension 62 of bearing 55. High pressure fluid behind piston 70
will then pass through radial notches 87 to act on the upper end 80
of valve 75. Since the end 80 of valve 75 has a larger effective
surface area than does the opposite end, the differential force
will rapidly move valve 75 downwardly into engagement with lower
bearing member 65. The piston 70 will be retained in the end of
bearing sleeve 62 until seal 88 passes discharge port 79 as is seen
in FIG. 7, chamber 90 is placed in communication with exhaust port
79 via recess 85 in the upper end of sleeve 76 and chamber 90 will
rapidly depressurize. Once pressure in chamber 90 is vented, the
piston 70 leaves the end of bearing 62 and the energy stored in air
spring 45 is released, forcing hammer 28 rapidly downwardly to
impact the anvil and in turn chisel 20.
It should be noted that once the piston 70 leaves the end of the
bearing 62, it is free to move almost unimpeded by the fluid in the
cylinder chamber until it again enters the valve sleeve 75. Thus,
the energy of the air spring is not dissipated in moving fluid. It
is also important to note that no fluid is displaced during the
downstroke, i.e., impact stroke of the hammer.
The hammer 28 normally impacts the anvil just before it reaches the
downward limit of the stroke where the hammer head engages the
cushion plate 30. In this position, the piston 70 is within the
upper end of sleeve valve 78 so tha the lower expansible chamber is
again sealed as shown in FIG. 4. Thus, as long as sufficient force
is applied at chisel 20, the hammer will cycle at a rate determined
by the fluid flow rate from the power source.
The hydraulic hammer of the present invention provides a high
impact device which can cycle at a relatively high, but
controllable rate. Previous hydraulically actuated hammers which
are double acting, that is, driven hydraulically in both the
retraction and actuation strokes, can cycle at only approximately
half the rate at which the hammer of the present invention can
cycle for the same fluid supply flow rates annd pressures. This is
because the speed of operation of a hydraulic linear device is
limited by the rate of flow to the device, the double acting unit
requiring pressure flow to be directed to both sides of the piston.
Further, the hammer operates at a relatively low noise level with
no high frequency sounds due to exhausting or venting of air
pressure. The simple valving is highly efficient as most of the
energy stored in the air spring is transferred to the hammer to
impact and cause the demolition of materials.
It will be obvious that the hammer device of the present invention
has broad application to other types of impact tools. For example,
the reciprocating hammer could be used for drilling, hand held
demolition hammer, as a nail gun, cutting or stamping device and
the like. Also, modifications and changes will suggest themselves
to those skilled in the art. It is intended that the scope of the
present invention be limited only by a fair interpretation of the
appended claims.
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