Note: Descriptions are shown in the official language in which they were submitted.
A motor assembly for carrying on the back
The present invention relates to a motor assembly portable on the back
which puts a substantially reduced load on the operator compared to conventionalassemblies carried on the back. The novel motor assembly of the invention rnay
advantageously be used for driving shearing and cutting tools in, for example,
5 forestry and gardening, but may also be used for other purposes for which back-
carried motor assemblies are or may be used.
In ~orestry motor assemblies carried on the back are used inter alia in
sawing equipment ~or clearance work. A conventional clearing saw consists of an
elongate supporting member, usually a power transmission tube, which at one
10 end thereo~ supports an in~ernal combustion engine and a saw blade at $he other
end. The clearing saw is supported in a harness attached to the rear portion of
the supporting member to hang on one side of the carrier with the driving motor
behind the carrier, and is operated via handle bars on the supporting member
which are fixed in front of the point of attachment of the harness. Tools for bush
15 pruning and the like are constructed in a corresponding manner. In addition to the
fact that such a tool is relatively heavy in itself (a modern clearing saw weighs
about 1~12 kg), the carrier is, despite specially constructed harnesses, subjected
to a considerably biased load caused by the tool hanging on one side of the
carrier. Since the driving motor, which is mounted to one end of the supporting
20 member, also is considerably heavier than the cuttlng tool at the opposl~e end,
the operator must counteract non-insignificant forces of inertia when swinging
the tool sideways. Such twisting loads to the back are particularly harmful and
additionally prevent a quick and accurate operation of the tool which reduces the
safety. Another disadvantage of this type of motor driven tools is the fact that25 they are normally balanced with their centre of gravity located somewhat before
their connection to the harness, which forces the operator to continuously lift
the fore supporting member with the cutting tool, which is tiring to the arms.
Naturally, such an apparatus is very trying to work with and reduces the workingcapacity. Through the uneven loacl or bias the risk of industrial injuries is also
30 high on a long view. There is therefore a need of a back-portable motor assembly
for clearing saws and the like which puts a reduced load on the body and therebywill be easier to operate. Attempts have been made to achieve this, on one hand,by reducing the weight of the tool and primarily the weight of the driving motoritself which is heaviest part, and, on the other hand, by redistributing and
35 balancing the tool load between the arms and the back in various ways. So far,
however, no satisfactory, practicable construction has been produced. This wouldrmainly be due ~o the necessary power output setting a lower limit to the weight
oI the driving motor. A result of the efforts to reduce the motor weight has been
that the cooling ~an system of the motor has become undersized for operation in
intense heat.
The object of the present invention is to provide a motor assembly
5 carried on the back which,despite having a drivin~ motor, preferably an internal
combustion engine, of at least the same power as the hitherto used motors,puts asubstantially reduced weight load on the carrier and does not subject the latterto any bias. Applied to~ for example, an equipment for a clearing saw or the like
the motor assembly of the invention provides an easily operable and safe tool
10 which also lacks the other disadvantages of the known and hitherto used sawing
equipments.
The invention is based upon the concept that a part of the motor
assembly power is utilized for "lifting itself", thereby reducing the weight to be
carried. This is accomplished by making the motor assembly, simultaneously with
15 driving the desired implement or tool, driYe at least one propeller means in the
form of a propeller, an impeller or the like, to provide a lifting force
counteracting the weight of the assembly and sufficient to balance the latter atIeast ~o a major part. Although it may in many cases be a more complicated and
rnore expensive alternative, it is within the scope of the inven~ion to use two
20 separate driving -motors in the motor assembly, Vi2. one (usually smaller) motor
to provide the lifting force and one (usually bigger) motor for driving the tool.
Since the air ~low from the propeller means may be utilized for cooling the
motor, no special cooling fan for the motor (or motors) will be needed. Usually
the cooling obtained hereby will also be considerably better than that of a
25 conventional cooling fan. Due ~to this arrangement with lifting force producing
propeller means driven by the motor assemblyJa back-portable motor assembly
will thus be provided which puts a substantially reduced weight load on the
carrier. While the fuel consumtion will be somewhat higher, it will be outweighed
by the increase of the operator's workin~ capacity and comfort that is achieved.30 In the bargain one also obtains, as mentioned above, an excellent cooling
capacity providing an efficient cooling of the motor even in operation at high
temperatures.
The propeller means may be arranged in various ways to provide the
desired lifting force. Preferably9 the propeller means are positioned in the upper
35 or lower part of the motor assembly. In the ~ormer case, which may be
preferable, the air flow generated by the propeller means will cool the motor,
while in the latter case the intake air to the propeller means may be utilized ~or
the coolin~.
~z~
Although the lifting force may be adjusted such that the motor assembly
will be substantially weightless ln its operative condition, it is for certain reasons
convenient to let the assembly, even at maximum speed of the motor, load the
operator with a certain weight, e.g. 2-4 kg, as will be described in more detail5 ~urther below. ~epending on the load on the working tool, e.g. a clearing saw
tool, coupled to the motor assembly, the motor speed will (provided that the
same motor is used for driving the propeller means and the tool) vary to some
extent, which in turn means that the weight of the assembly which is experiencedby the operator will also vary a little~ Such a variation would well be tolerated
10 by the carrier, but according to a preferred embodiment of the invention means
are arranged for maintaining the lifting force substantially constant. This may,for e~ample, be achieved by controlling the intake flow to the propeller means,
e.g. by having the intake flow pass through an opening with a controllable intake
area. Alternatively, the motor speed may be kept constant9 e.g. by electronic
15 control of the f~el flow to the engine. Preferably means are also provided for
controlling the lifting force, such that a suitable individual adjustment may be- made by the operator.
The propeller means may be designed in various ways in accordance with
~er se known technology. While the inventive concept may be realized with one
20 single impeller in the form of a propeller or a fan wheel, pre~erably two, orpossibly more, such impellers will be used in combination. Two impellers mountedto the same drive sha~t with intermediate guide vanes give a substantially
twofold increase of the li~ting force in comparison with the use of one single
impeller Correspondingly three impellers will give a threefold increase of the
~5 llfting force. Instead of mounting two impellers on the same drive shaft they may
be arranged to rotate at the same speed but in opposite directions through
driving by separate drive shafts, whereby the need of ~uide vanes is eliminated~The more detailed design of fan ~vheels, propellers, ~uide vanes etc. to achievethe desired lifting force may be made in accordance with known technology in
30 aircraft and fan engineering and will not be further discussed herein.
In the preferred embodiment wherein one and the same internal
combustion engine drives both the propeller means and the tool, etc. to be
powered by the engine, the power transmission bet~veen the engine and the
propeller means may be arranged in various ways. Thus, it may be completely
35 mechanical by connection of the propeller means ~rive shaft or sha~ts to ~he
~ngine output shaft through gear transmissions, driving belts or the like. Alterna-
tiYely, hydraulics or pneumatics may be utilized, optionally in combination, so
that a hydraulic motor or a prleumatic motor will drive the propeller means~ In
~2~ b38~
such a case also the desired tool driving is suitably effected by a hydraulic orpneumatic motor. ~Iso electric drivin~ of the propeller means, as well as oE ~heconnected tool, may be contemplated, in which case the internal combustion
engine vill drive a generator providing the necessary current to electric motors5 arranged to drive the propeller means and tool, respectively. While the use oEhydraulic, pneumatic and/or electric driving would make the motor assembly
heavier and more lumberin~, a ~reater flexibility in the utilization of the
assembly for various purposes is achieved. The weight increase may, of course,
be compensated by increasing the lifting force o~ the propeller means (and
10 thereby also the power consumption).
While the inventi~e principle could per se be applied to a conventional
clearing saw e~uipment of the initially described kind, ~he invention is most
advantageously utilized if the "weight relieved" motor assembly is carried in a
harness which, similarly to the harness of, for èxample, a rucksack, loads the
15 operator's back and shoulders equally on both sides. Depending on the intended
use of the motor assembly it may be mounted ri~idly to the harness or to be
laterally pivotal therein, in both cases via vibration damping members.
According to a preferred embodiment of such a devibrated suspension in the
harness the motor assembly is connected to the harness through one single
20 suspension point~ which is devibrated both vertically and horlzontally. A pivotal
vlbration-damped suspension poin~ may be accomplished by means of a vertically,
conically tapering joint portion ex~endin~ ~rom the actual n~otor assembly and
which is pivotally received in a sleeve corresponding to the cone-shaped portion,
the outside of which sleeve is connected to a surrounding holder via a layer of a
25 vibration damping material, said holder being fixed to the harness in any suita~le
manner.
As mentioned above the transmission of the motor assembly power for
driving various tools or implements may be effected either purely mechanically
or in a hydraulic, pneumatic or electric uay, or possibly with combinations
30 thereof. In the case of a purely mechanical power transmission the motor
assembly is provided with at least one output drive shaft, to which the desire~
implement or tool may be connected. When utilizin~ the invention for, for
example, a clearing saw or similar shear or cutting tools the power transmissionmay be effected by means of a power transmission shaft or tube, whi~h is
35 pivotally mounted to the motor assembly to permi~ upward and downward
swinging thereof. Since the motor assembly can be turned to the sides in the
harness an excellent mobility of the power transmission ~ub~ will thus be
~z~
obtained. In such a case a drive shaft is rotatably journalled in the power
transmission tube in conventional manner, and a pivotal coupling thereof to the
output drive shaft from the motor assembly may be accomplished by a suitable
bevel gear or the like. In a preferred embodiment of the motor assembly of the
invention combined with such pivotally mounted power transmission tube the
latter is spring biased to the motor assembly to be held up in a suitable position
by the spring means. The operator does therefore not have to continuously
support the power transmission tube with the connected tool with his arms but
instead, when necessary, presses the power transmission tube downwards (and, of
course, also upwards) against the spring force. The biasing force is preferably
adjustable to permit a balancing depending on the connected tool and the desiredoperating position. In a further preferred embodiment the power transmission
tube is telescoplcally arranged so that it may be continuously extended or
compressed as necessary.
In case of a hydraulic, pneumatic or electric power transmission no such
power transmission tube will usually be necessary, but the working tool will form
a separate unit together with a small hydraulic motor, pneumatic motor or
electric motor in connection with the tool, the power transmission being effected
through hydraulic ur pneumatic tubes or an electric lead.
lhe weight-relieved motor assembly of the invention for carrying on the
back may find use in many fields. Thus, it may be used in forestry for various
sawing equiprnents, e.g. for clearing sawing and thinning of young forests;
cutting and shearing equipment for cutting grass and underwood; as well as for
spraying assemblies. For the latter use a relatively greater power would be
re~uired to balance the, at least at the beginning of the spraying process9
substantial weight of the spray liquid. In gardenlng the motor assembly of the
Invention may be used for driving tools for cultivation, hed8e cutting, spraying,
etc. Furthermore, it may be used in building sites for driving portable tools for,
for example, vibrating concrete castings. The above enumeration is, of course,
only an example of different uses of the invention, and many other applications
are possible.
In the following the invention will be illustrated in more detail ~vith
reference to a particular embodiment in connection with the accompaning
drawings, wherein
3~ Fig. 1 schematically illustrates the use of an embodiment of the motor
assembly of the invention in the form of a sawing equipment for clearing and
thinning young forests,
~2~?$~8~
Fig. 2 is a schematic rear view, with parts broken away, of an
em bodim ent of the proper motor assembly of Fig. I supported by an operator,
~ig. 3 is a schematic side elevation of the supported motor assembly of
Fig. 2,
Fig. 4 is a schematic side elevation, partially in section and having parts
broken away, of a modified embodiment of the motor assembly of Fig. 2 and 3,
Fig. 5 is a hori~ontal view, partially in section, of the driving and power
transmission part of the motor assembly of Fig. 4,
Fig. ~ is a sectional view of the rear part of an embodiment of the power
transmission tube of Fig. 1,
Fig. 7 is a sectional view of the fore part of the power transmission tube
of Fig. 6,
Fig. 8 is a sectional view along A-A in Fig. 7, and
Fig. 9 is a schematic plan view of a chain saw cutting bar mounted to the
power transmission tube1
The clearing saw equipment of ~:ig. 1 comprises a motor unit 1 carried in
a harness 2 by an operator 3. The m otor unit I drives a cutting bar 4 attached to
one end of a power transmission or drive shaft tube 5, which is operatively
connected to the motor unit 1 through a cardan joint 6 to be vertically pivotal
~0 and rotatable about its longitudinal axis. The motor unit I is movably suspended
in the harness ~, so that it may be turned sideways about a vertical axis, as will
be further described below. The operator 3 o~erates the sawing equipment via a
handle or handle bars 7 fixed to the drive shaft tube 5.
The more detailed construction of the motor unit 1 and the suspension
thereof in the harness ~ appears from ~ig. 2-5. The power source of the motor
unit 1 is an internal combustion engine 8 having a fuel ~ank g. The engine ~ m ay
be of the type usually used in chain and clearing saws with a power of, for
example, 4-6 horse power and will not be further described herein A propeiler
gear housing 10 is mounted on the side of the engine output drive shaft. From the
30 upper part 11 of said gear housing a vertical drive shaft 12 protrudes which is
coupled to the propeller means 13 and 14 designed to act upon the motor
assembly wit`h an upward lifting force and simultaneously cool the engine 8 witha downward airflow. Via the gear box 10 the output drive shaft of the engine 8 is
coupled to the cardan joint 6 for driving the cutting bar 4 through a power
35 transmission shaft rotatably journalled in the drive shaIt tube 5. The cardan joint
6 is vertically pivotally connected to the gear housing 10 via a spring biased
balancing joint 15, the spring force of which may ~ ontrolled by a control knob
~2~8~
16. The propeller section oE the motor assembly is enclosed by a casing 17, the
rear part of which extends downwards sver the en~ine 8 and the gear housing 10
(Fig. 3). The intake air to the propeller means 13, 14 is admitted through an
opening 18 in the casing top which is covered by a ~rating 19 attached to a
5 stiffened portion 20 of the casing. The casing 17, which, for example, may be of
aluminium, is in the illustrated case ~ixed to the upper part 11 of the gear
housing 10 via cross bars 21 and~optionally~not illustrated bars connecting the
lower part of the casing to a suitable portion of the engine 8 and/or the ~ear
housin~ 10 or the means for suspending the motor assembly in the harness 2.
The suspension in the harness 2 appears from Fig. 2-5. Two brackets 22,
23 are in the rear part thereof attached to the base porti~n ~4 of the ~ear
housing 10 and in the fore part thereof to a vertical journal member 25 having alower cone-shaped part 26. Said cone-shaped part is rriounted to be rotatable
about its vertical axis in a bearing sleeve 27, which preferably is of a self-
15 lubricating type. The bearing sleeve 27 is in turn fixed ~o a holder cup 2B via a
layer 29 of a vibration damping material~ e.g., such rubber ma~erials as are
usually used for vibration damping. The cone-shaped portion 26 is extended Wittla thin cylindric portion 30 extending through an opening in ~he lower part of the
holder cup 28. A nut 31 on a threaded end portion of the projecting cylinder pin20 30 retains a helical spring 32 between the nut and the bottom of the holder cup.
With the nut 31 the bias of the spring 32 can be adjusted to a suitable contact
pressure between the cone-shaped ~ournal ~6 and the bearing s~eeve 270 The
holder cup 28 is in turn attached by means of mounting brackets 33 to a plate 34to be ~astened to the harness 2. The harness 2 may, as shown in the Figures,
25 consist o~ a rigid supporting frame 35 for bearing against the baclc and to which
the mounting plate 34 is fixed in the lower part of the frame. The supporting
frame 35 is fastened to the carrier by means of a waist belt 36 fixed to the lower
part of the frame and two shoulder straps 37 fixed to the upper part o~ the
frame. Due to the above described devibrated one point suspension substantially
30 no vibrations are transmitted from the motor assembly to the operator since the
cone-shaped design of the bearing journal and the vibration damping sleeve
absorb vibrations in all direc~ions.
In Fig. 2 the propeller means 13, 14 are intended to be mounted to the
same drive shaft 12, and thereby ro~ate in the same direction. In this case guide
35 ~anes 38 are arranged between the two propeller means, whereby the provided
fan pressure, and thereby the lifting force, will be doubled. In the embodiment of
Fig. 4, on the other hand, which shows, in more detail, an example of how the
power transmission between the engine and the propelJer means 13, 14 may be
provided, the latter are arranged to rotate in opposite directions. The need of the
guide vanes 38 is thereby eliminated since a correspon~ing pressure increase will
still be obtained. ~n the illustrated case the propeller means 13, 14 consist of two
fan whee~s or impellers of a per se conventional type. The two impellers each
comprise a central disc portion 39 and 40, respectively, and a suitable number of
fan blades (e.g. six to thirty) 41 and 42, respectively, fixed to the central disc. A
suitable material for the fan blades is aluminium or possibly a fibre-reinforcedcomposite. The upper impeller 13 is fixed to a vertical drive shaft 43, which via
bearing means, e.g. a ball bearing 44, is rotatably journalled within an outer drive
- shaft 4S, to which the lower impeller 14 is fixed. The outer drive shaft 45 is in
turn rotatably journalled, in relation to the upper part 11 of the gear housing 10,
in upper and lo~ver bearing means, e.g. ball bearin~s, 46 and 47, respectively. The
Iower end of the drive shaft 43 Is rotatably journalled in the bottom portion ofthe gear housing 10 in a ball bearing 48 designed to stand a high axial load. The
power transmission between the output drive shaft, designated by the reference
numeral 49 (Fig. 5~, of the internal combustion engine 8 and the impellers 13,14is effected through a gearing, generally designated by 50. The gearing 50
comprises a bevel gear 51 which is fixed to the engine shaft 49 and engages a
bevel gear 52 having a rotation axis substantially perpendicular to the drive shaft
49. The gear 52 is fixed to an oppositely arran~ed bevel gear 53, which in turn
engages, on one hand, a bevel gear 54 fixed to the inner drive shaft 43 for the
upper impeller 13, and, on the other hand, a bevel gear 55 fixed to the outer
drive shaft 45 for the lower impeller 14 and through which the inner drive shaft2S 43 extends. Through the described ~ear artan8ement the rotation of the engine
drive shaft 49 is transmitted to the two impellers 13, 14, so that they rotate at
the same speed but in opposite directions. In Fig. 4 and 5 the bevel gears 51-5Sare of equal size, but, of course, the size and number of teeth may be varied togive the impellers a different rate of ro~ation from that of the motor drive shaft.
The motor drive shaft 49 is rotatably journalled in a holder portion 56 in
the bottom part of the gear housing and projects through an opening in a fore~
removable sidewall 57 of ~he gear housing. The power transmission from the
drive shaft 49 to the power transmission shaft in the drive shaft tube 5 is
effected by the above mentioned cardan joint or beve~ gear 6. The latter is
arranged in a housing 58, which is pivotally mounted in relation ~o the gear
housing ~0 (and thereby the res~ of the motor assembly). To this end the gear
housing 58 is connected to the gear housing 10 via t~vo rotatably journalled
~l2~ 38~
cylinder sleeves S9, 60, the inner one 59 of which is fixed to the sidewall 57 of
the gear housing 10 and the outer one is fixed to the gear housing 58. A helicalspring 61 is mounted on the outside of the outer cylinder sleeve 50 with one endthereof fixed to a worm gear 62 and the other end fixed to the gear housing 58.
5 The worm gear is rotatably journalled in the gear housing 10 and may be rotated
by means of the previously mentioned control knob 16. The helical spring 61 is
arranged such that it will maintain the gear housing S8 and the drive shaft tube 5
with the cuttin~ bar 4 at a certain level in relation to the stationary part of the
motor assembly. By rotating the contro1 knob 16 the tension of the helical spring
10 61 can be adjusted ~o position the drive shaft tube 5 at a desired level. The more
the spring is stretched, the higher moment load can the spring absorb, and the
more raised will consequently the end of the drive shaft tube be according to the
increased effective length of the lever. The drive shaf~ ~u~e with the associated
sawing unit will thereby be supported completely by the motor assembly and thus
15 only load the operator's back. In order to restrict the moment action in the
suspension point 26, 27 as far as possible the weight distribution of the motor
assembly, including the drive shaf~ tube and cutting tool, is adapted to permit
the centre of gravity to coincide with the point of suspension.
In the gear housing 58 the output drive shaft 49 of the engine is rotatably
2D journalled in a ball bearing 63 before the gearing3 and a packing 64 after the
gearing. The gearing consists of a bevel gear 65 which ;s fixed to the drive shaft
49 and engages a bevel gear 66 fixed to a power transmission shaft 67 rotatably
journalled in the drive shaft tube 5 in ball bearings9 one of which, 68, in the
figurc is mounted in the gear housing 58. The power transmission shaft 67 with
2S its associated gear 66 is mounted substantially transversely to the engine drive
shaft 49 with the gear 6S. The power transmission shaft 67 in turn drives the
chain saw bar 4 (Fig~ 1), through a suitable bevel gear, as will be further
described below.
The drive shaft tube 5 with the chain saw bar 4 is operated, as mentioned
30 above, by means of the handle or handle bars 7, which are attached ~o the drive
shaft tube S via a suitable vibration damping material, so that the vibrations of
the tool will not be transmitted to hands and arms. SuitablyJ a throttle control is
mounted to the handle bars 7 for controlling the engine speed. The engine 8 is
suitably started by a starting strap (not shown), which runs in one shoulder
35 portion of the harness and is easlly accessible to the operator. When the engine 8
operates, the engine output drive shaft 49 drives the two impellers 13, 14, via the
gearing S0 and the drive shafts 43, 45, as well as the chain saw bar 4, via ~he
~l2~
gearing 65, 66 and the power transmission shaft 67~ When the impellers 13, 14
rotate, air is sucked in through the grating 19 and is given a speed and pressure
increase by the impeller blades 41, 42 to provide a lifting force acting upwardsupon the motor assembly simultaneously with an excellent cooling of the internal5 combustion engine 8. The lifting force, which i.a. depends on the number of
impellers and the design thereof as well as the rotary speedJis adjusted such that
the operator still experiences a certain weight, e.g. of the order of magnitude of
2-4 kg, since too great a lifting force which tends to lift the assembly out of the
harness would be inconvenient to the operatorO The more detailed choice of the
10 number of impellers and the design thereof is wlthin the skill a person skilled in
the art and will not be further discussed herein. As an example may be mentionedtnat if the whole clearing saw equipment, including the motor assembly, weighs
about 12 kg, a suitable lifting force at .he normal operating speed of the engine,
e.g. 5000 rpm9 is about 8 kp. The operator will then experience the weight of the
15 sawing equipment as about 4 3cg. The necessary ef~ect to drive the impellers 13,
14 and provide the desired lifting force, of course, also depends on the total
weight of the sawing equipment and the desired maximum weight reduction as
well as on how well the efficiency s~f the impeller arrangement has been
optimized. For a 4 horse power driving motor 8, which would be sufficient ~or a
20 clearing saw of the described type, an 8 kp lifting force may be effected with a
power supply of about 0,8 kW.
A conventional driving motor for the described clearing saw equipment
normally has an operating range between about 3000 rpm and 6000 rpm, the
speed control being performed by the throttle control on the hanàle bars 7. Since9
25 in the illustrated case, ~he lifting force will be completely dependent upon the
motor speed, the operator will experience the sawing equipment as heavier the
lower the speed is. Since the operator will be capable of adjusting the motor
speed rather quickly with the throttle control, he can prevent too high a lifting
force, which according to the above could be inconvenient, in case of a possible30 overspeeding of the engine. Preferably, however, means are provided which
restricts the lifting force such that it cannot exceed the weight of ~he
equipment. This may, for example, be accomplished by electronic control means,
which affect the fuel flow to prevent a predetermined maximum speed from
being exceeded, e.g. 6000 rpm. Alternatively, the control means may be cDupled
35 to the ignition system to switch of f the ignition current when the predetermined
speed is exceeded. Of course, the control means may also be arranged to
continuously maintaln the motor speed at a predeterrnined value, whereby the
same lifting force will always be obtained. An alternative arrangement is to
control the intake area for the intake air to the impellers to maintain the lifting
force substantially constant. This may, for example~ be accomplished by some
form of motor speed controlled "diaphragm" or damper in the aperture 18 of ~he
5 casing or cover 17. Another arrangement is to provide the central disc of the
impeller with spring-actuated side plates, which are folded out by the centrifu~al
force to increase the area of the central disc - and thereby decrease the
effective part of the impeller blades - dependin~ on the speed of rotation
(the motor speed).
When operating the above described clearing saw equipment the operator
will consequently experience a very moderate part of the total equipment
weight. Neither will, due to the devibrated one point suspension~ any vibrationsbe transmitted from the motor via the harness. Further9 the drive shaft tube 5
with the sawing tool 4 will, as mentioned above, be supported by the motor
assembly in the desired, pre-adjustable posi~ion and can easily be moved
vertically with as well as agaînst the force of the helical sprin~ 66. Thereby the
operator will be loaded only when he needs to change the inclination of the drive
shaft tube. Swinging of the drive shaft tube to the sides is effected by rotation of
the whole motor assembly in the suspension joint 26-28. FinallyI the sawing tool 4
may be turned by rotating the drive shaft tube 5 about its longitudinal axis. The
above described clearing saw equipment is thus excellently convenien~ to operateand will substantially increase the operator's working capacity and comfort.
Fig. 6 and 7 show an example of a suitable design of the power trans-
mission or drive shaf~ tube 5. In this embodiment the drive shaft tube is
extensible, and it will be appreciated through the following description that the
above described design of the gear housing 6 can not be used in this case. The end
of the drive shaft 49, which in the previously described embodiment optionally
also may be used as an additional power output, is excJuded here, so that the
drive shaft ends just after the bevel gear 65. The modified bevel gear housing,
here designated by the re~erence numeral 58', has an extension 69 (illustrated
shortened) arranged to permit accommodation of the end of a sliding drive shaft
70 tcorreSponding to the shaft 67 of Fig. 5), which is rotatably mounted in the
drive shaft tube 5 in two ball bearings 71 in the gear housing 58' as well as in a
ball bearing 72 in a lower gear housing 73 at the other end of the drive shaft tube
5. The housing 58' is attached to an inner tube cylinder 74, in which the upper
part of the power transmission shaft 70 extends. The tube c:ylinder 74 is slidably
mounted in the upper part of the drive shaft tube 5 via sliding means 75 at each
12
end thereoI. The handle bars 7, to one handle of which a not illustrated throttle
control is attached, are rigidly, but preferably in a vibration damped manner,
mounted to the drive shaft tube 5, and a compressible protective ~aiter or
bellows 76 (only hinted in the figure) is arranged over the drive shaft tùbe 5
between ~he gear housing 58' and the mounting portion of the handle bars 7 on
the drive shaft tube. The power transmission shaft 70 is displaceable in its
longitudinal direction in the ball bearings 71 as well as in a bevel gear 77
(corresponding to the gear 66 in Fig. 5) on the shaft. The shaft 70 is, however,not rotary in relation to the ball bearings 71 and the ~ear 77, which is
accomplished through suitable guide means. The bevel gear 77 is driven in the
same way as above by the gear 65 on the motor drive shaf~ 49 (Fig. 5). A draw
spring 78 acting within the drive shaft tube between the end of the inner tube
sleeve 74 and the lower gear housing 73 tends to maintain the drive shaft tube 5completely drawn over the inner tube cylinder 74? such that the end thereof
contacts the gear housing 58'. By brin~ing the handle bars forwards the operatormay displace the outer tube of the drive shaft tube on the inner tu~ cylinder
against the force of the draw spring 78 to extend the drive shaft tube. This maybe valuable, for example3 for sawing work where ~here are obstructing branches.
A suitable possible extension of the drive shaft tube may beg e.g., 2-3 dm. Whenthe drive shaft tube is extended the power transmissi~n shaft 70 slides in the ball
bearings 7i and the gear 77 as above.
The chain saw bar 4 is attached to the gear housing ~3. An endless saw
chain (not shown) is movable around the chain saw bar in conventional manner
and runs over a pulley 79 on a driYe shaft;~0 at a portion thereof protruding from
the gear housing 739 in which it is rotatably journalled in two ball bearings 81, 82.
The power transmission from the drive shaft 70 in the drive shaft tube 5 is
effected via a bevel gearing consisting of a bevel gear 83 fixed to the end of the
drive shaft 70 and in en~agement with a bevel gear 84 fixed to the saw drive
shaft 80. The pulley 79 is attached to the drive shaft 80 via a conventional safety
cJutch 85, based upon centrifugal action, so that the driving of the saw chain will
rapidly be disengaged if the chain gets s~uck. These disengagement means may
optionally be placed at another site along the dri~ing means, e.g. in the upper
gear housing or the cardan housing 58.
Lubrication of the saw chain is effected with oil from a container (not
illustrated) in the lower part of the drive shaft tube ~ adjacent to the gear
housing 73. Through suitable clucts ~he interior of the gear housing 73 is kept
filled wi~h oil from ~his con~ainer. An oil duct 86 (Fig. 8~ connects the inside of
8~
the gear housing with a port which opens into the interior of the chain saw bar
and therefrom, in conventional manner, leads out ~o the guide channel Eor the
saw chain. An adjusting needle 87 is provided for controlling the oil quantity. The
oil in the gear housing 73 is metered to the oil channel 86 via a cone-shaped
pulley 88 fixed to the saw driving shaft 80. The metering pulley 38 is on part of
its envelope surface provided with a recess 89, which during a part oI each
revolution connects the channel 86 with the interior of the gear housing 73.
Fi~. 9 schematically shows the saw bar end of the clearing tool brought
against a tree 90. The reference numeral 91 signifies a support to counteract the
action of the chain saw force upon the clearing saw. A transversely mounted saw
bar similar to the one illustrated would definitely be the most advantageous forclearing operations. Optionally the direction of the saw bar could be made
adjustable to permit a desired positioning between a transverse position, as
illustrated, and a position with the saw bar arranged in the longitudinal direc~ion
of the drive shaft tube. The latter position would permit use in pruning
operations. Suitably the saw bar is made sufficiently long for the clearin~ saw
also to be used for thinning young forests. It is, of course, als~ within the scope
of the Invention to dimension the saw bar such that the sawing equipment may be
used for conventional tirnber cutting and replace the usual hand-carried chain
saws.
The devibrated one point suspension as described above, as well as the
spring balanced pivotal suspension of the drive shaft tube to the motor assembly,
are, of course~ also ad~rantageous in a conventional motor assembly without
lifting force producin~g devices, and the invention therefore also comprises these
devices as such.
While the use of a chain saw bar is preferred in a clearing saw equip-
ment, a circular saw blade could just as well be used. It is to be understood that
various other modifications and changes may be made in the embodiment
described above and illustrated in the drawings without deviating from the scopeof the invention.
As stated above the motor assembly according to the invention is, o~
course; not restric~ed to the use in sawing and cutting equipments, but may alsojust as we~l be utilized in units for cutting grass and underwood, hedge cutting,
cultivation, vibration of concrete castings, in spray units, etc. Optionally themotor assembly may be provided with some type of quick-coupling for simple
connection of various implements, such as a drive shaft tube provided with a tool
(similar to the one described above) or for the connection of a flexible drive
14
shaft, for example, in hed~e shears. As previs usly mentioned ~he power
transmission may also be effected via hydraulic, pneumatic or electric means,
optionally in combination. Other applications and mod;fications are, of course,
also within the scope of the inventive principle, as it is stated in the subsequent
5- claims.
