Note: Descriptions are shown in the official language in which they were submitted.
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TITLE OF THE INVENTION
PRESSURE-DRIVEN ENGINE
BACKGROUND OF THE INVENTION
As a conventional reciprocating engine, an internal
combustion engine represented by a gasoline engine is known.
However, the drive of a gasoline engine accompanies noise,
exhaust gas and vibration. In addition, a gasoline engine
is difficult to carry and the use thereof is limited from
the point of view of fire prevention. Therefore, the
reciprocating motion of a pressure-driving source such as an
air cylinder is utilized, as, for example, a power for a
power-driven nipper, a power-driven scissors or a
combustible treating apparatus.
For example, in nippers for shearing lead wires and
metal plates by the power of compression air, the blades are
opened and closed by the reciprocating motion of an ordinary
air cylinder, and in the air cylinder, the inflow and
outflow of the compression air, in other ~ords, the intake
and the exhaust of air is controlled by a manual valve or a
solenoid.
That is, a conventional pressure-driven engine for
obtaining reciprocating motion or rotational motion
necessarily requires a switch valve, and a power and an
electric equipment for controlling and driving the switch
valve, so that the equipment cost and the management of the
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equipment are also required. In certain cases of limiting
the equipment, the use of the driving source other than
compression air is difficult. ;
Especially, in the case in which great importance is
attached on the portability and the handling property as in
the case of tools held by hand, the power source, the
connecting cord and the solenoid regulate the moving range ~- -
and increase the weight of the tools, thereby deteriorating
the operability.
SUMMARY OF THE INVENTION
Accordingly, it is a first object of the present
invention to eliminate the above-described problems in the
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prior art and to provide a pressure-driven engine which is
dispensed with separate switch valve and control unit.
It is a second object of the present invention to
provide a pressure-driven engine for which the type of a
pressure-driving source is freely selected.
It is a third object of the present invention to
provide a pressure-driven engine which is dispensed with
another driving source such as a power source so as not to
be ignitable. ;
To achieve this aim, the present invention provides a ;
pressure driven engine which is composed of an engine body
comprising: a cylinder provided with an air hole at one end ; ;~
thereof, and an intake hole and an exhaust hole connected to
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a pressure-driving source on the other end thereof; a piston
slidably inserted into the cylinder and having a return
spring around the shaft or the connecting rod thereof, an
intake vale and an exhaust valve for opening and closing the
intake hole and the exhaust hole, respectively, each of the
valves having a valve rod slidably inserted into the
corresponding pair of sliding portions provided at one end
of the piston and a pair of springs which are provided
around the valve rod on both sides of the sliding portion;
an intake magnet opposed to the intake valve so as to open
the intake hole by attracting the intake valve; and an
exhaust magnet opposed to the exhaust valve so as to open
the exhaust hole by attracting the exhaust valve.
A plurality of engine bodies may preferably be arranged
in parallel with each other. In this case, the engine can
be a multi-cylinder engine like an internal combustion
engine.
A plurality of engine bodies may also preferably be
arranged in opposition to each other. In this case, the
engine can be utilized for the work which requires both
advancing motion and backing motion.
It is also preferable that a plurality of engine bodies
are arranged with the respective pistons connected to each
other by a crank mechanism. In this case, the reciprocating
motion can be utilized as a smooth rotational motion.
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It is also preferable to provide a plurality of engine
bodies by connecting the respective pistons with each other
by a crank mechanism and to omit the return springs of the
respective pistons. In this case, the working efficiency is
further improved.
The above and other objects, features and advantages of
the present invention will become clear from the following ~ ;
description of the preferred embodiments thereof, taken in
conjunction with the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
Figs. 1 and 2 show an embodiment of a pressure-driven
engine according to the present invention, wherein
Fig. 1 is a vertical sectional view of the main part
thereof in the state in which the piston is accommodated (at ;
the bottom dead point), and
Fig. 2 is a vertical sectional view of the main part
thereof in the state in which the piston is projecting (at ;
the top dead point);
Fig. 3 a vertical sectional view of the main part of
another embodiment; ;~
j Figs. 4 and 5 are partially cutaway elevational view of
the main parts of further embodiments. ;
DESCRIPTION OF THE PREFERRED EMBODIMENTS '
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An embodiment of the present invention will be ,
explained with reference to Figs. 1 and 2. A cylinder 1 is i -
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made of a synthetic resin and a piston is slidably inserted
in the cylinder 1. The cylinder is divided into a
pressurizing chamber and a back pressure chamber 23 by the
piston 2. In the back pressure chamber 23, an air hole 13
is provided and a return spring 26 for constantly urging the
piston 2 toward the pressurizing chamber 22.
To the pressurizing chamber 22 of the cylinder 1, a lid
14 made of a synthetic resin is attached, and the lid 14 is
provided with a passage 15 connected to a compressor or the
like so as to introduce pressurized air set at a desired
supply pressure therethrough and an exhaust hole.
An intake valve 3 and an exhaust valve 4 have
reqpective valve rods 33, 34 slidably inserted into sliding
portions 12 provided on the side of the pressurizing chamber
22, and the intake valve rod 33 have springs Sa, 5b
therearound on both sides of the sliding portion 12. The
intake valve 3 can be freely brought into contact with an
intake valve seat 16 of an intake bearing body 20 so as to
open and close the intake hole 9 thereof. A pair of
permanent magnets 7 are secured to the lid 14 so that when
the intake valve 3 is attracted by the permanent magnets 7,
the intake hole 9 is opened.
An exhaust valve rod 34 have springs 6a, 6b therearound
on both sides of the sliding portion 12. ~he exhaust valve
does not close a communication hole 18 of an exhaust bearing
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body 21 and can be freely brought into contact with an
exhaust valve seat 17 of the exhaust bearing body 21 so as
to open and close an exhaust hole 10. A pair of permanent
magnets 8 are secured to the exhaust bearing body 21 so that
when the exhaust valve 4 is attracted by the permanent
magnets 8, the exhaust hole lO is opened.
The reference numeral 19 represents a packing for
keeping the airtightness of the piston 2, 24 a fixing
fitment, and 25 a receiving fitment.
The operation of this embodiment will now be explained.
In Fig. 1, when pressurized air is introduced through the
passage 15, the pressurized air passes through the intake
hole 9 and fills the pressurizing chamber 22.
At this time, although the pressurized air passes
through the communication hole 18, since the exhaust hole 10 ~
is closed by the exhaust valve 10, the pressure is risen 80 , .
that the piston 2 begins to slide so as to project. ~ ;
The sliding operation of the piston 2 contracts the
spring 5b of the intake valve 3 and extends the spring 5a ;
thereof. Although the intake valve rod 33 of the intake
valve 3 is about to slide so as to close the intake hole 9
by the intake valve 3, the attractive force of the magnets 7
is so strong as to allow the intake valve 3 to move.
The spring 6b of the exhaust valve is contracted and
the spring 6a thereof is extended. Although the exhaust
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valve rod 34 of the exhaust valve 4 is about to slide so as
t~ open the exhaust hole 10, the urging force of the spring
6a and the air pressure applied to the exhaust valve 4 do
not allow the exhaust valve 4 to move.
When the piston 2 has reached the top dead point at
last, the intake valve 3 moves against the attractive force
of the magnets 7, and closes the intake hole 9 in
cooperation with the urging force of the spring 5b, as shown
in Fig. 2.
At this time, the exhaust valve 4 also moves against
the air pressure and the movement is accelerated both by the
urging force of the spring 6b and the attractive force of
the magnets 8. Thus, the exhaust hole 10 is opened in a
moment, and the pressure of the pressurizing chamber is
gradually reduced to atmospheric pressure.
The piston 2 then begins to slide toward the bottom
dead point by the urging force of the return spring 26.
During this time, the exhaust valve 4 is not moved due
to the urging force of the spring 6b and the attractive
force of the magnets 8 nor does the intake valve 3 move due
! to the urging force of the spring 5b and the pressure of the
pressurized air applied to the intake valve 3. When the
piston 2 has reached the bottom dead point at last, the
exhaust valve 4 moves again against the attractive force of
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the magnets 8 by virtue of the urging force of the spring
6a, and closes the exhaust hole 9, as shown in Fig. i.
Although the intake valve 4 begins to move so as to
open the intake hole 9, the movement is accelerated by the
attractive force of the magnets 7, the intake hole 9 is r ''~
opened in a moment.
The urging forces of the springs 5b and 6a are ;
ordinarily stronger than those of the springs 5a and 6b,
respectively.
If the amount of pressurized air introduced through the
passage 15 and the amount of exhaust from the exhaust hole ~ ;
10 are adjusted, the piston sliding speed is variable. ;
The above-described relationship between the urging
force and the attractive force is shown in Table 1. The ~ ;
ordinate represents the driving force a, which is the urging
force or the attractive force, and the abscissa represents
the working distance X. The attractive force of the magnet
is represented by the line A and the urging force of the
spring is represented by the line B.
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Table 1
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B, B B2
O 1 2 3 4
X
The attractive force of the magnet is calculated from
the following formula:
a = K 2
wherein K represents the intensity of the line of magnetic
force,
and the valve switching point is obtained by the
intersection between the line A and the line B.
If the urging force is changed into another force such
as those indicated by the lines Bl and B2, the intersection
is also varied. Thus, a desired intersection can be
produced. It is naturally possible to produce a desired
intersection by varying the line of magnetic force of the
magnet. ;
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Table 2
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Applied pressing force
~- 80 _ / "~
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/ ,~ Effective pressing force
~ 50 _ ~
'40 _ / "~'
30 _ ~ ,~' :
20 _ / ""
1 0 _ ~" '
0 " 1 2 3 4 5 6
Pressing force ~ /cmZ
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produced
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The influence of the return spring of the piston on the :~
pressing force of the piston (working efficiency) is ; .:
represented in Table 2. In this case, the diameter of the ~;
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piston is set at 50 mm and the stretching force of the
return spring is set at 5 kg.
Although the actual pressing force of the piston is the
value calculated by subtracting 5 kg from the value shown in
Table 2, in consideration of a practical numerical value
range, for example, if the supply pressure is 5 kg/cm2, the
effective pressing force which is practically usable with
respect to 100 kg, which is the pressing force produced. In
other words, the efficiency is 95%.
If a plurality of engine bodies are used by means of a
crank mechanism, since the backing motion is actuated by the
advancing motion between each other, the return spring may
be dispensed with, as desired.
Fig. 3 shows another embodiment of the present
invention. A plurality of engine bodies 11 are provided in
opposition to each other.
The magnet 7 is an integral discal rare earth magnet
and the magnet 8 is an integral annular rare earth magnet. -~
The piston 2 has a connecting rod 29 rotatably connected to
the piston 2 by a pin 27.
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The connecting rod 29 is attached to an adapter plate ; ~;
28 on which a blade or the like is mounted. To the adapter ;
plate 28, another connecting rod 30 is attached so as to be
opposed to the connecting rod 29.
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That is, a plurality of opposing pairs of pistons 2
with the top and the bottom dead points reversed in each
pair are combined. This embodiment is effective when a
large force is required not only at the time of advancing
motion but also at the time of backing motion. In this
case, the return spring 26 may be dispensed with, or
sufficed with a small urging force, so that the working
eficiency is enhanced.
Fig. 4 shows still another embodiment of the present
invention. A plurality of engine bodies 11 are provided in
opposition to each other through a crank mechanism 31. The
crank mechanism 31 converts the reciprocating motion of the
piston 2 into rotational motion.
The cylinder 1 is rockably fixed to a fixing portion
32.
Fig. 5 shows a further embodiment of the present
invention. A plurality of engine bodies 11 are integrally
provided in parallel with each other while being connected
by the crank mechanism 31.
As described above, according to the present invention,
sincelit is possible to produce reciprocating motion only by
the supply from a pressure-driving source, no power source,
electromagnetic valve, nor controlling unit therefor is ;
required. Thus, the engine is light in weight and low in
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cost and has a good handling property and, especially,
enables the portability of tools held by hand to enhance.
Since the valve structure is accommodated in the
engine, the noise is reduced, and since the engine is not at
all ignitable, it is usable in the workshop containing a
combustible material. In addition, since the type of a
supply pressure source is not restricted, the engine of the
present invention can be widely used in any place.
Furthermore, it is possible to produce a large force
~pressing force) required by varying the diameter of the
cylinder and the pressure supplied without any shock and, in
addition, the speed thereof is also easily controllable.
While there has been described what is at present
considered to be a preferred embodiment of the invention, it
will be understood that various modifications may be made ~;~
thereto. For example, a plurality of engine bodies may be
arranged radially around the crank mechanism. It is
intended that the appended claims cover all such
modifications as fall within the true spirit and scope of
the invention.
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