Note: Descriptions are shown in the official language in which they were submitted.
8840
A MYRA WORKING MACHINE
the invention relates to a material working
machine, such as an excavator., loader, break ,
compactor, planer, pave. or dredge., to which is, in
operation, attached a working tool for working on or
in a material, such as earth, while both vibratory
and non-vibratory forces are applied thereto.
Known machines of this kind have various
disadvantages. Replacement or substitution of a
working tool on such a machine is laborious and time-
consuming. Known machines are not designed, and
consequently not suitable, lo. continuous working of
the tool-carrying part of the machine undo. wale,,
neither aye they designed for universal use, and can
therefore usually work with only one type of tool.
The aim of the present invention is to
avoid, or at least to mitigate, these and other
disadvantages of known machines.
this is achieved according to the invention
- 20 by a material working machine comprising vibratory
means, applying vibratory forces and d Ivan by
driving means, and non-vib.atory means, applying non-
vibratory forces, the machine having vibratory tool
carrier means for removable attachment of a working
tool, the tool carrier means incorporating first
mounting means for its connection to the vibratory
means, and second mounting means for its connection
to the non-vibratory means, the second mounting means
enabling reciprocation of the tool carries means at
the point of it attachment to the second mounting
means when the vibratory means is in operation, the
fist and second mounting means being spaced from
each other in, or substantially in, the direction of
said reciprocation.
In a preferred embodiment the driving means
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includes a motor sensing, via -the vibratory means.
load applied by the working tool to the tool carrier
means at any instant of its operation and
automatically responding by correspondingly adjusting
its torque and, in inverse proportion the eta, its
speed, which are then transmitted, via the vibratory
means, as variable-torque vibratory forces to the
tool carrier means which transmits them to the
working tool.
In a further preferred embodiment, the tool
carrier means incorporates at least one oil nose void
situated between the first and second mounting means
for supplying oil to the first and second mounting
means.
It is particularly advantageous to produce
the tool carrier means by casting.
The advantages of` a machine according to
the invention include easy replacement and
substitution of tools and also universality, i.e. the
possibility to attach to the same tool carrier means
divers tools.
cause the tool carrier means incorporates
at least one oil reservoir, i.e. has a self-contained
lubrication system, the machine can work with the
whole tool carrier means under water, and the
provision of the oil reservoir or reservoirs ensures
good thermal stability for the bearings in the tool
carrier means.
It has many further advantages to have a
tool carrier means to which a tool it attached
compared to the known machines without any tool
carrier means, particularly if the tool carrier means
is made by casting. Some ox -the advantages have
already been mentioned, other include the possibility
of precision machining and assembly of the tool
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carrier means in high volume production, the tool
carrier means is attached to the machine and the
single tool carrier means can be used for any tool,
and all the tools used with the machine can be made ,
without any tool attachment means of their own
permanently fixed thereto, so that they are lighter
and cheaper.
The invention will now be described, by way
of example, with reference to the accompanying
diagrammatic drawings, in which:
Figure l is a side view of a relevant part
of a material working machine according to the
invention provided with a bucket;
Figure 2 is a front view to Figure 1;
: 15 Figure 3 is a section of the drive shown in
Figures l and 2;
Figure 4 is a front view, partly in
section, of the drive shown in Figures 1, 2 and 3;
Figure 5 is a plan, partly in section, of a
tool carrier shown in Figures l and 2;
Figure 6 is a side view of a material
working machine according to the inventions
Figure 7 shows a detail from Figure 6:
Figure 8 is a side view of a further
embodiment of a machine according to the invention
provided with a breaker;
Figure 9 is a front view to Figure 8;
Figure lo is a side view of the relevant
part of a material working machine including a front
loader, which forms a further embodiment of the
present invention
Figure 11 is a partial plan to figure lo
Figure 12 shows a combined rotary and
sliding bearing used in the machine illustrated in
Figures lo and 11. and
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Figure 13 (on the sheet of Figure 6) shows the
hydraulic circuit of the vibration mechanism.
Figures 1 and 2 show an implement arm 12 of an
excavator. The arm 12 carries a vibratory tool carrier 52
to which is firmly fixed a working tool, here a bucket 14
provided with teeth 15. The arm 12 is pivotal connected
to a dipper arm 18 about a pivot 20 and to a dipper ram 24
about a pivot 22. The dipper ram 24 is operable to lift
and lower the implement arm 12.
A vibratory means or mechanism, indicated
generally at 26, is mounted on the implement arm 12. An
implement ram 28, operable to impose arcuate movement to
the tool carrier 52, is connected at a pivot 31 to pivotal
links 32. The links 32 are pivotal connected at pivots
33 to the implement arm 12. Pivotal links 30, connected
to the vibratory tool carrier 52 at a pivot 34 (also
referred to as "second mounting means"), are connected to
links 32 at a pivot 35. The links 30 and 32 are operable
by the implement ram 28 to control the position of the
tool carrier 52 relative to the implement arm 12 while
permitting it to vibrate, as links 30 swing to and fro
about the pivot 35. It can be appreciated from the above
that the elements 24, 28, 30, 31, 32 and 35 can also be
referred to as "non-vibratory means".
Referring now to Figures 1 to 5, the vibratory
mechanism 26 is driven by driving means including a
hydraulic motor 36 to which is connected by its upper end
a shaft 38 mounted in bearings 37 and 39. The lower end
of the shaft 38 carries a first bevel gear 40 situated in
a first housing 41 partially filled with oil. Transversely
through the first housing 41 passes a transverse shaft 42
carrying a second bevel gear 43 meshing with the first
bevel gear 40. The transverse shaft 42 is mounted in
bearings 44 each of which is situated between an outer
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retaining collar 45 and an inner retaining collar 46.
Both the shafts 38 and 42 pass through seals 47 in the
first housing 41 to prevent oil from escaping from the
first housing 41. Both ends of the shaft 42 extend
laterally from the first housing 41. The elements 36-47
thus form the driving means.
At each end of the shaft 42 is an eccentric 50.
Both eccentrics 50 are sealed in the vibratory tool
carrier 52. The illustrated tool carrier 52 is made as a
single sturdy casting which comprises for each eccentric
50 first mounting means of the type of a bearing 53,
situated between two retaining collars 54 provided with
seals 55. For large working tools the tool carrier 52 may
be formed by two or more castings bolted together. Spaced
from the bearings 53 are bearings (not shown) for the
pivot 34. The tool carrier 52 has two lateral oil
reservoirs 56 (Fig. 5), each situated between one of the
bearings 53 and one of the bearings for the pivot 34, from
which oil is fed to these bearings through passageways 57
and 58-
The bucket 14 is firmly fixed to the tool courier by a retaining pin 59 and four fixing members 60. When
the fixing members 60 are removed, the bucket 14 can be
swiveled on the retaining pin 59, e.g. through 180 as
shown in dashed lines in Fig. 1, and again firmly fixed to
the tool carrier 52, whereby the machine is converted from
a back hoe to a front loader.
The hydraulic motor 36 drives the shaft 38 and
this rotation is transmitted, via the bevel gears 40 and
43, to the transverse shaft 42 causing the eccentrics 50
to describe a circular orbit (having a radius of less than
1 cm. for example about 1 mm) around the axis of the shaft
42 thereby vibrating the tool carrier 52 in a manner which
is controlled by the links 30 connected via the links 32
to the ram 28. With this arrangement, the eccentrics 50
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cause the teeth 15 on the bucket 14 to describe a close
curve of a generally elliptical shape during each cycle of
vibration.
Figure 6 shows a machine having an implement arm
12, as described in connection with Figures 1 and 2,
connected to a dipper arm 18 and dipper ram 24, which in
turn is slid ably carried in a boom slide 62. The boom
slide 62 is pivotal connected to a boom arm 64,
displaceable by a boom ram 63, and to a first end of a
turn buckle 65 which actuates automatic start-stop means
shown in greater detail in Fig. 7. This means includes a
lever 67 hinged by a pivot 68 in the boom arm 64. The
second end of the turn buckle 65 is by a pivot 66 connected
to a short arm AYE of the lever 67. The long arm 67B of
the lever 67 extends between two stops 69 and two
micro switches 70.
The movement of the long arm 67B is controlled by
control means 71 which, in the illustrated example,
comprises two opposed pairs of compression springs 72,
each situated between a central movable abutment 73 fixed
to the long arm 67B and a stationary abutment 74 fixed to
the boom arm 64. It will be understood that other
elements than compression springs can be used to control
the preselected actuation pressure. The force of the
springs 72 is adjustable. Any forces acting on the arms
12, 18, 64 are transmitted, via the turn buckle 65, to the
lever 67 and try to deflect its long arm 67B towards one
of the micro switches 70, but the long arm 67B can actuate
the relevant micro switch 70 only if these forces are so
high that they overcome the control means 71. The
function of the micro switches 70 will be described later
in connection with Figure 13.
Figures 8 and 9 show an embodiment having
elements 12 to 52 substantially identical with those
described in connection with Figures 1 and 2. The shaft
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42 has at each end a non-eccentric sub 75 carrying a spur
wheel 76. In an alternative arrangement (not shown) other
driving elements may be used instead of the stub 75 and
wheel 76, for instance a further eccentric or crank.
To the tool carrier 52 is attached, e.g. by bolts
or ~uick-release couplings, a working tool unit of the
type of a breaker unit 80 comprising a housing 81 which
forms an oil sup and through which extends a shaft 82
mounted in bearings 83. The shaft 82 carries at each end
a spur wheel 84 meshing with the adjacent spur wheel 76 of
the tool carrier 52. The center of the shaft 82 is formed
into an eccentric 85 coupled with a rod 86 pivotal
connected to a rocker arm 87 which converts the rotary
motion of the shaft 82 into a reciprocating motion
imparted to a working tool _ (here a spike) guided in
slides 89. The wheels 76 and 82 on each side of the tool
carrier 52 and housing 81 are protected by a common sealed
cover (not shown). The oil from the sup in the housing
By lubricates both the bearings 83 and the wheels 76 and
84.
Other working tool units may be attached to the
tool carrier 52, in which the tool may be driven by a
drive independent on the drive for the eccentrics 50.
In operation the rocker arm 87 causes the working
tool 88 to perform a rectilinear reciprocating motion on
which is superimposed the motion of the tool carrier 52
generated by the eccentrics 50 of the vibratory mechanism
25. The amplitude (length) of the rectilinear
reciprocating motion of the tool 88 is greater than the
amplitude (throw) of the eccentrics 50, the ratio of the
said amplitudes being 10:1 in the illustrated example.
As is apparent from the drawing, the spur wheels
76 and 84 are of a different diameter so that the
frequencies of the two superimposed motions are
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different. As a consequence of this arrangement, the
working tool 88 operates without seizure.
The oscillatory forces generated by the
eccentrics 50 and the eccentric 85 increase and decrease
in direct proportion to each other.
To protect the machine from shocks when the tool
88 impinges on a very hard material, e.g. when breaking
concrete or rock, a shock absorber 90 is connected to the
hydraulic system of the implement ram 28. A suitable
shock absorber comprises a pressure vessel containing
hydraulic liquid of the system and also containing an
inflatable bag which is lit Ed with gas and is
consequently compressible. The gas pressure in the bag is
set to be higher than the maximum pressure for operating
the implement ram 28. A shock absorber may also be used
in the hydraulic system of the other described embodiments.
Figures 10 and 11 show a front loader mechanism
of a material working machine which comprises a front
loader bucket 114 provided with teeth 115 and attached to
two vibratory tool carriers 152. The front loader
mechanism includes non-vibratory means including an arm
112 to which is pivotal connected by pivots 134 a
substantially U-shaped link member 130 which is in turn
pivotal connected to rams 128 by pivots 131, the rams
128 being operable to effect movement of the link member
130 about the pivots 134 relative to the arm 112. The
machine comprises a vibratory means or mechanism,
indicated generally at 126 which, when driven by a
hydraulic motor 136, imparts vibratory motion to two
vibratory tool carriers 152, and thereby to the tool (here
bucket 114) attached thereto.
The vibratory mechanism 126 comprises driving
means including said motor 136 to which is connected a
shaft trot shown) mounted in bearings 137 and carrying a
first bevel gear 140 situated in a first sealed housing
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141 partially filled with oil. Transversely through the
first housing 141 passes a transverse shaft 142 carrying a
second bevel gear 143 meshing with the first bevel gear
140. The transverse shaft 142 is mounted in first
bearings 144 situated in the first housing 141, and in
second bearings 145, each of which is contained in a
separate second sealed housing 146 which is fixed to the
top of the link member 130, to which also the first
housing 141 is fixed.
At each end of the shaft 142 is a vibratory means
of the type of an eccentric 150. Each eccentric lS0 is
mounted in first mounting means, in this embodiment a
bearing l , and both the eccentric 150 and the bearing
153 are sealed in one of the tool carriers 152. Both the
housings 146 and the tool carriers 152 have a respective
separate oil reservoir (not shown). The bucket 114 is
connected to the two tool carriers 152. The bucket 114 is
therefore via the two tool carriers 152, bearings 153,
eccentrics 150, shaft 142, bearings 145 and housings 146
pivotal connected to the top of the link member 130.
The bottom of the link member 130 is pivotal
attached to the bottoms of the two tool carriers 152 by
means of pivots 160 (also referred to as "second mounting
means"). As is apparent from Figure 12, each pivot 160 is
rotatable mounted by means of a bearing 161 in a bearing
block 164 which is slid ably retained between rigid plates
166 and 16~ so that it can slide up and down in the two
tool carriers 152. Spaces 162, 163 are provided for this
motion in the two tool carriers 152 and this enables the
two tool carriers 152 to perform the desired motion.
There is an oil duct 169 in each of the tool carriers 152
to facilitate lubrication of the bearing 161 and of the
bearing block 164. The end of each ram 12B remote from
the pivots 131 is pivotal connected to a lever 167 of an
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automatic start-stop means described in connection with
FIG. 7.
The resultant movement of the bucket teeth 115 is
an elongate, very slim figure of eight having its major
dimension almost perpendicular Jo the direction in which
the teeth 115 of the bucket 114 extend forwardly, which is
substantially the same as the direction in which the
bucket 114 is pushed by translator inactive movement into
the material to be loaded. The loosening effect of this
vibration upon the material results in that smaller
inactive force is needed to drive a given bucket into a
given type of material.
Figure 13 shows a hydraulic circuit of the
vibratory mechanism. The circuit comprises a pump 170,
relief valve 171, a shock absorber 172, a solenoid valve
173, a priority flow control valve 174 and a motor 175
(such as the motor 36 in Figs. 1 and 2 or Figs. 8 and 9,
or the motor 136 in Figs. 10 and 11). The shock absorber
172 serves to protect the hydraulic system from a
so-called hydraulic line shock and may be a pressure
vessel containing together with hydraulic liquid of the
system also an inflatable bag which is filled with gas and
is consequently compressible.
The oil in the hydraulic system is constantly
pumped by the pump 170. When none of the micro switches 70
(Fig. 7) is actuated by the pump 170 to the relief valve
171 to the valve 173 from which it flows back to the tank
176 of the system. When one of the micro switches 70 is
actuated it causes the solenoid valve 173 to direct the
flow through the valve 174 to the motor 175 which is thus
operated and drives the vibratory mechanism.
As will be apparent from the description, the
system of Figure 7 automatically controls the system of
Fig. 13, the two systems forming an automatic start-stop
control device of the vibratory mechanism. This device
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automatic start-stop means described in connection with
FIG. 7.
The resultant movement of the bucket teeth 115 is
an elongate, very slim figure of eight having its major
dimension almost perpendicular to the direction in which
the teeth 115 of the bucket 114 extend forwardly, which is
substantially the same as the direction in which the
bucket 114 is pushed by translator inactive movement into
the material to be loaded. The loosening effect of this
vibration upon the material results in that smaller
inactive force is needed to drive a given bucket into a
given type of material.
Figure 13 shows a hydraulic circuit of the
vibratory mechanism. The circuit comprises a pump 170,
relief valve 171, a shock absorber 172, a solenoid valve
173, a priority flow control valve 174 and a motor 175
(such as the motor 36 in Figs. 1 and 2 or Figs. 8 and 9,
or the motor 136 in Figs. 10 and 11). The shock absorber
172 serves to protect the hydraulic system from a
so-called hydraulic line shock and may be a pressure
vessel containing together with hydraulic liquid of the
system also an inflatable bag which is filled with gas and
is consequently compressible.
The oil in the hydraulic system is constantly
pumped by the pump 170. When none of the micro switches 70
(Fig. 7) is actuated by the pump 170 to the relief valve
171 to the valve 173 from which it flows back to the tank
176 of the system. When one of the micro switches 70 is
actuated it causes the solenoid valve 173 to direct the
flow through the valve 174 to the motor 175 which is thus
operated and drives the vibratory mechanism.
As will be apparent from the description, the
system of Figure 7 automatically controls the system of
Fig. 13, the two systems forming an automatic start-stop
control device of the vibratory mechanism. This device
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can have a manual override controlled by the operator from
the cab.
The hydraulic circuit for the vibratory mechanism
is provided with a flow transducer (not shown) which sends
signals representative of the volume flow rate through the
flow transducer, to a torque monitor (not shown)
calibrated in units of torque, whereby information about
instantaneous torque of the hydraulic motor 36 or 13
(motor 175 in Fig. 13) is provided.
The hydraulic motor 36 or 136 is a pressure
compensated motor of a type obtainable from RHO Hydraulics
of Planet Place, Killing worth, Newcastle-upon-Tyne,
England, in which, as the output torque rises, the output
speed (rotational frequency) falls, thus giving
substantially constant power output.
In all the embodiments described above, the
eccentrics may be driven by any appropriate means, for
example, an electric motor, in which case an electric
circuit will be substituted for the hydraulic circuit.
Many variations are possible. The motor may
drive the transverse shaft 42, 142 directly. Other types
of implement than a bucket or a breaker unit e.g. a spike,
an impact drill, a chisel, a screen, a blade, a clam shell
or a compacting implement with a flat base or a roller,
25 may be attached to the same tool carrier 52,152 as has
been described.
Pneumatic rams may be used instead of the
hydraulic rams described.
The tool carrier 52, 152 may be made of two main
parts one of which is rotatable, displaceable and/or
adjustable relative to the other.
In each ease, but on a lesser scale, the
invention may also be applied to machines which are
manually maneuvered instead of mounted on a "prime mover".
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It will be apparent from Figures l and 2 that
because the eccentrics 50 are nearer to the pivot 34 than
are the teeth 15, the amplitude of the vibration at the
teeth 15 is greater than that of the vibration of the
eccentrics 50. The same applies, mutates mutandis, to
Figures 8, 9 and lo if.
The vibratory forces are greater than the
non-vibratory forces. It will be apparent from Figures l,
2, 6, B and 9 that major part of the non-vibratory
(translator) forces is applied along a path 28, 31, 32,
35, 30, 34 which differs from the path 50 along which are
applied the vibratory forces, but that these two paths
converge at the teeth 15 of the bucket 14 figs. 1, 2, 6)
or the tip of the spike 88 (Figs. 8, 9). In the
embodiment shown in Figures 10, 11 major part of the
non-vibratory (inactive) forces proceeds along a path 112,
134, 160 which differs from the path 150 along which are
applied the vibratory forces, and these two paths converge
at the teeth 115. In all the embodiments (Figs. 1, 2, 6,
8, 9, 10, 11) not only the two force paths are separate
and independent but also the operating hydraulic circuits
for these forces are separate and independent.
In the embodiments shown in Figs. 1, 2 and 6 a
sliding bearing, such as that illustrated in Fig. 12, can
be used for the pivot 34. It will be understood that the
bearing of Fig. 12 will be so positioned that it will
slide in, or substantially in, the direction towards and
away from the eccentrics 50.
Instead of the pivot 160 shown in Figs. lo and
if, mounted by means of the bearing shown in Fig. 12, an
arrangement similar to the arrangement including the link
30 and the pivots 35 and 34 may be used in the embodiment
according to Figs. lo and if.
In the claims the term "vibratory means" is
intended to mean "means applying vibratory forces" and the
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term "non-vibratory means" is intended to mean "means for
applying non-vibratory forces".
I.
