JPS5949150B2 - driving machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is an electric driving machine (Electric Impac).
tTool).

Low-energy, electrically powered driving tools are commonplace and are used to drive small nails and clasps, as well as to tighten and loosen nuts. It is also used to attach deformable fasteners such as small brass or copper rivets.

However, to date, high-energy driving tools, at least of the hand-held type, have been powered by compressed air.

This compressed air type driving machine has a number of drawbacks.

That is, large hoses are required and also a large volume air source that is not practically movable.

Further, the equipment required for this type of pneumatic equipment, such as a pressure control system, a lubricating oil system, and a filter, makes the system complex, difficult to handle, and expensive.

Although high-energy, hand-held, electrically powered driving tools are certainly desired, there are still many unresolved problems.

For example, a 16 penny nail (length 8.3.crIi (3,2
It takes approximately 453.6 mm to drive a 5-inch nail) into medium-hard wood so that the nail head does not protrude from the surface of the wood.
The peak force requirement of kg (1000 boats) can be easily determined using an arbor press and instrumentation.

Since the nail applies an equal reaction force to the screwdriver, and the worker would not be able to counteract the force of approximately 4.53.6 kg at its peak, a low-speed screwdriver would not have enough force. But it probably won't work, because the nail will be pushed back from the piece of work rather than being pushed into the wood.

Therefore, the time required to drive the nail and the volume of the driver are of paramount importance.

design parameter
This is especially true when there is a high demand for reactionless work.

For example, the amount of potential energy that must be stored in mechanisms and systems of the type that are required to transfer energy to a workpiece within a short period of time is required to perform essentially recoilless work. For calculation purposes, other actual parameters such as tool capacity and contact speed can be chosen for the tool.

Once this is done, the above calculations reveal the following.

That is, combined with a very fast and sufficient force transmission mechanism,
This means that a considerable amount of energy storage capacity is absolutely necessary.

Moreover, this calculation shows that it is totally useless to use conventional things like electromagnets to solve the problem.

This is because the electromagnetic unit that can generate the average required power in the short time required to perform the recoilless work described above is too large and heavy to be practical. This is because it cannot be quantified (even if we ignore the price point).

The idea of a flywheel comes to mind as a small, lightweight mechanism that can store high energy, but unfortunately, a flywheel is a high-speed rotating system that generates undesirable moments due to rotation. It is large and unsuitable for hand-held tools, making it difficult to put it into practical use.

Moreover, the tools held in this hand must have a certain degree of precision.

The problem presented to workers in managing these forces is that a single flywheel tool is a very dangerous, if not fatal, machine.

This danger occurs when the machine has fasteners, such as nails, that can be fired at high velocity.

This is because there are considerable difficulties in trying to control this firing.

According to the present invention, a high-energy engine capable of producing a force of about 75 horsepower within a short period of several seconds sufficient to drive a 1'LLf, 8.3 cTL (3.25 inch) nail.
We have actually created an electrically driven, hand-held type driving machine.

In fact, a small, low horsepower electric motor is sufficient to provide the power at more than one cycle per second.

Not one, but a pair (two) of substantially similar flywheels that rotate in opposite directions can store the required energy, and the pair of flywheels can properly interact with each other. They are compatible and are designed to eliminate the harsh rotational moments that occur when the flywheel rotates at high speeds.

These identical flywheels are rotated in relation to the other flywheel so that one of them engages a friction ram located between the pair of flywheels, which forces the ram to engage within a short period of time on the order of a few tenths of a second. This constitutes an efficient high-speed power application mechanism capable of applying considerable driving force.

Thus, clutches made in this manner do not require synchronous engagement and, when well designed, will not slip.

A mechanical interlock is provided, i.e., holds the tool firmly against the work piece (the object into which the nail is being driven) when the trigger is pulled to engage the clutch. The protruding part of the tool makes it safe for work, and even if there is an accident in which the tool is dropped, the nail will not explode.

Although a motor speed controller may not necessarily be an accurate safety device, it does provide the operator with the ability to reduce ram energy to an appropriate level commensurate with the workpiece. It provides a means to enable this.

Ordinary household electrical current is sufficient to power the tool, and in fact the power requirement is such that it can easily be supplied by batteries or a small self-contained generator. This is especially true for cycles with low power demands.

The problem is not so much the waste of energy during the drive cycle, which is as minimal as a small, low-horsepower motor, but rather the energy wasted in order to speed up a single-drive motor to the required speed. The time required is the issue.

The driving machine of the present invention, when designed as a nailing machine, is suitable as is to receive commercial nail strips or belts without any modifications.

This also applies to fasteners (other than nails) such as rivets or similarly packaged fasteners.

Generally, this type is housed in a magazine supplying a trap of conventional design.

The first object of the invention is thus to provide a new, high-energy, hand-held, electric driving tool.

The second object of the present invention is to utilize the principle of a high-speed flywheel,
Moreover, the object is to obtain a device of the type mentioned above, in which the energy storage medium is made to be effectively free from any rotational moments.

Another object of the invention is to use a matched pair of counter-rotating flywheels as a medium of energy transfer;
The aim is thereby to obtain a driving machine in which the latent energy stored therein can be transmitted almost instantaneously to the ram.

Another object of the invention is that the ram is actuated by a self-locking, effectively non-slip, high power friction clutch, thereby eliminating the need for synchronous engagement between toothed clutches. I'm trying to get a loading machine.

An additional object of the invention is an electrically operated, hand-held tool based on the principle of dual counter-rotating flywheels, the tool being a nailer, riveter or latching machine. , punching machines, chisel machines and similar tools, the object being to obtain a tool whose work cycle is based on the high-speed striking of a retractable ram.

Other objects of the invention will become apparent to some extent from the description below.

Before giving a detailed description of the embodiment of the nail driving machine (indicated by the reference numeral 10) of the present invention, a brief description of the most important elements and parameters of the tool will be given with respect to the principle explanatory diagram of FIG.
Some of these are quite important.

It is first necessary to describe a simple experiment, combined with a detailed mathematical analysis, in order to obtain an idea of the force that must be produced by the instrument and the time required to exhaust this force. It would be good to help understanding.

Below is a description of the mathematical analysis and experiment.

What is the peak force required to drive a 16-penny nail 8.3 cm (3.25 inches) long into a piece of medium-hard wood so that the head of the nail does not protrude from the surface of the piece of wood? Approximately 453.
The weight is 6 kg (1000 lbs), which was determined by an experiment using a simple arbor press.

Furthermore, a graph showing the relationship between the rate of penetration of a nail into a piece of wood and the applied force can be found in 453.6 above! 9 (1000
(pounds) is approximately linear.

Therefore, the total energy consumed can be expressed by the following formula.

In a nail driving operation, the time required to drive the mass of the nail and driver is a major consideration since the nail exerts an equal reaction force on the nail gun or driver.

Assume the weight of the screwdriver is 4.536 kg (10 lb), which is a reasonable weight for a hand-held tool, and the speed of contact when driving the nail is 152.4 crn/sec (5 feet, //lf/J). ), the time for inserting the nail into the wood is defined by the following equation (2).

Here, FXt) is the force applied to the wood by the nail that changes over time.

However, M is the mass of the driver.

In equation (4), d is the time required to drive the nail.

Therefore, if we integrate this, Vi is the nail driving speed of the tool, and Vf is the final speed of the same bond as previously determined.) (453,6 kg) Calculating td from equations (4) and (6) Then, by substituting the value assuming the nail driving speed to be 152.4 cm/sec (5 feet, 4>), and assuming the final speed to be zero, from this formula, using a tool weighing 4.536 kg (10 pounds),
Assuming an initial speed of 152.4 cm/sec (5 feet/sec) and no recoil operation (therefore, Vf = 0), it can be seen that it takes 0.003 seconds to drive the nail.

The average power value required during the working time ta (time required to drive the nail) is determined by the following equation.

From the above calculation, the following can be found.

That is, the tool must have a considerable energy storage capacity and must also be capable of discharging this energy within a very short period of time, about one-tenth of a second.

Now, assuming that a flywheel is employed in this energy storage mechanism, with a diameter of 762 cTn (3 inches) and a rotational speed of ω, a meaningful comparison can be made between the peripheral speed of the flywheel and the driving speed of the nail; is obtained between the energy of and the required energy.

If a 7.62crI'L (3 inch) nail is driven in 0.003 seconds, this speed is 7.62 crI'L (3 inch) diameter flywheel driven at 2.54 m.
/sec (assuming that it is rotating at an offshore circumferential speed of 1000 inches/sec, its rotational angular velocity is 6366 r, p, m, which is an appropriate speed and can be increased as necessary. .

The energy of the flywheel is expressed by Equation (12) E=0.51ω2, where I is the rotational inertia value of the flywheel.

For a solid disk with a diameter of 7.62 cIrL (3 inches), its inertia value is given by:

Formula Q3)..." I = 0.5 mr "For example, if brass is used as the flywheel material, 2.546r1'L
(1 inch) thick, its mass M is calculated by substituting equation (13) = 5.34
X10-5kg -m-sec2) Here, using ω = 666 radians/sec, the energy is expressed as Equation (16)... E = 0.5 (5,34X10
') (666) 2 = 118.43 ft-lb (16,4 kj7- m ) (approximately 161 joules) Approximately 125 ft-lb (17,3 kg m ) of energy is 8.3 cr/L (3,25 in. ) was assumed to be required to drive a nail of medium hardness up to the nail head, but the diameter is 7.62 CrrL (3 inches).
7 with a brass flywheel 2.54 cTt (1 inch) thick.
The one that rotates at 00 Or, p, m has sufficient energy and peripheral speed to meet the requirements of the high energy nail driving machine mentioned above.

However, as long as such a tool is held in the hand, it has a significant rotational moment.

This rotational moment is due to rotation about an axis perpendicular to the spin axis of the flywheel.

The magnitude of this moment is calculated as follows.

Formula ση...Mp = IΩω Where, Mp is the rotation-based moment acting on the nail driving machine, ■ is the inertia of the flywheel of the nail driving machine, ω is the rotational angular velocity of the flywheel, Ω is the operator is the rotational angular velocity at which the nail driver attempts to rotate.

As an example, if a worker has a nail-driving machine with the flywheel parameters mentioned above and attempts to rotate the nail-driving machine 180 degrees in 0.1 seconds, the force based on the gyroscopic rotation will be The moment of the nail driving machine due to is calculated by the following formula.

Formula: Mp = (31,4 radian/e)
x (5,34 x 10-4 lb-ft-sec2) x (666 radians/sec) = 11.2 ft-lb (1,55 kg-m) This 1.55 kg-m is a large torque. This makes it extremely difficult for an operator to position the nailer in a desired direction.

Therefore, in order to eliminate possible rotation-based moments in the gripper tool, which must be carefully and accurately positioned relative to the workpiece, two It is necessary to provide a functionally identical flywheel.

In accordance with the teachings of the present invention, it has been realized that there are many other parameters, more or less critical, to be recombined.

One of its most important parameters is that the ram element 12 is sandwiched between a pair of counter-rotating flywheels 14 and 15, and that the work piece shown in FIG. The fact is that the entire working stroke of the ram, such as being driven forward, must be carried out within a very short time of a few thousandths of a second, in order to avoid any slippage or displacement of the tool.

In other words, if the tool is used to drive a 16 penny nail, the ram is engaged with the nail at 0,003
Approximately 453.6 kg (453.6 kg) is loaded onto the ram during a short period of seconds.
It is necessary to apply a tremendous amount of force (1,000 pounds).

Although drive communication between a pair of flywheels and the ram means could be accomplished in many ways, the only practical method employed requires synchronous engagement of racks and pinions, etc. This method uses frictional force that does not

Additionally, some type of clutch may be applied to momentarily engage the ram with a flywheel that is already rotating, but with no rotational movement of the flywheel as desired in order to keep the flywheel engaged with the ram. It is impossible to drive the ram once in a few thousandths of a second.

Such latches move both of a pair of flywheels toward and away from each other to engage and disengage them, or one movable flywheel engages a ram with the other fixed in position. The flywheel can be moved relative to the flywheel and pressed against the side of the other fixed flywheel.

Of these two modes of operation, the latter is preferred.

This is because, according to the previously described mode of operation, if the ram means floats between two relatively movable flywheels, then for each actuation both flywheels are activated rather than simultaneously. This is because one flywheel approaches the ram before the other flywheel.

When this happens, an excessively large acting force is created that exceeds equilibrium, causing one of the pair of flywheels to bend the other.

As is clear, the ram engagement force in this case is equal to the amount of force required to drive and actuate the nail, or approximately 453.6
3 times kg (1000 pounds), approximately 1360.8 kg
(3000 pounds).

Therefore, the installation of a deformable flywheel makes it extremely difficult to properly design and engineer the mechanism.

Moreover, the forward movement of the ram or the path in the working stroke can be on either side of the guideway and cannot be determined if one flywheel moves in advance of the other during a particular drive.

In order to solve this inconvenient problem, one flywheel is arranged to be rotatable about a fixed spin axis, and a clutch is attached to the other flywheel.
A preferred method is to be able to act to reduce the distance between the two flywheels during driving.

As mentioned above, it is certainly possible to displace one movable flywheel towards the other stationary flywheel along a line perpendicular to the direction of movement of the ram toward its extended position, but the ram engagement Disadvantageous problems are posed because the resultant force is approximately three times as large as the maximum working force of the ram.

However, it has been found that a sufficient amount of ram gripping force can be obtained by arcing one movable flywheel into engagement about a pivot axis located behind the spin axis.

The movable flywheel rotates rearwardly when the surface of the movable flywheel engages the surface of the ram means located in its vicinity, forcing the ram means against the surface of the stationary flywheel, thereby causing the movable flywheel to rotate against the ram. increase the pressure exerted by the

The action of such a flywheel when engaged with the ram surface generates a ram gripping force of the required magnitude, and even if the ram gripping force is so large that it exceeds three times the maximum driving force of the ram. can occur quickly and easily.

The theoretical arcuate path of the spin axis of the movable flywheel lies in a plane through the pivot axis perpendicular to the direction of movement of the ram toward the extended position.

Once the spin axis crosses behind this plane, the clutch acts to loosen its grip on the ram, thus breaking drive communication.

Therefore, in order to completely prevent wear on the engaging parts, the spin axis of the precisely movable flywheel should be kept in a position that does not reach a point beyond the said plane.

This is a significant problem that can be solved according to the teachings of the present invention.

As shown diagrammatically in FIG. 1, the acting force driving the ram element upward is expressed by the following equation:

Formula (2o) −・−・−pci = 2FnKf where,
Fn is the value of the normal acting force between the flywheel and the surface of the ram means, and Kf is the coefficient of friction between the ram element and the flywheel.

Further, as shown in FIG. 1, the downward acting force applied to the arcuately movable flywheel 16 is expressed by the following equation.

Equation (, zl) −...+・F u = F nK fThe following equation can be derived from the geometric theory.

where θ is the first plane defined by the spin and pivot axes of the arcuately movable flywheel and the rammo stage 1
It is the value of the acute angle formed by the intersection of the second plane perpendicular to the direction of movement toward the extended position of the second plane.

By substituting the above equation (2]) into equation (22) and simplifying it, the following equation is obtained.

Equation (23)...Tanθ-Kf From the two equations, slip is a critical phenomenon that must never be allowed for all practical purposes, and if Kf≧ It is understood that if the relationship ton θ exists, slippage can be avoided when the flywheel and ram means engage.

It is easy to select the values of the angle θ and the coefficient of friction Kf so that the critical relationship of Taiki holds true.

The flywheel should be cylindrical and the retaining surface of the ram means should be flat so that both parts come into contact with each other along a straight tangent parallel to the spin axis.

Other complementary surfaces are unnecessary since points on the surface at different distances from the spin axis have different magnitudes of circumferential velocity, which inevitably leads to the phenomenon of slip. be.

Before giving a detailed explanation of the embodiment as a nailer,
Some other features will be described below.

First, the size of the motor is considered to suit the desired work cycle.

As previously stated, the average power consumption required to drive a 16 penny nail until the head is flush with the surface of the work piece is approximately 75 horsepower.

Since energy is stored in the flywheel, the actual motor drive power required to drive the flywheel can be from 0 to 75 horsepower depending on the desired work cycle.

If the motor work cycle is selected at a rate of 5 operations per second and friction is ignored, the desired motor drive force is:

In other words, a motor drive power as large as 1.125 horsepower can maintain a suitable rate of motion of the flywheel at a rate of 5 activations per second.

As can be seen, the motors mentioned have excessive work cycles from a practical point of view, and even smaller horsepower electric motors are quite suitable.

Moreover, the amount of energy consumed for each task is such that the stored power is adequate to energize the motor, considering the amount of work done in a few hours.

Excessive ram biasing energy is disadvantageous, so it is preferable to adjust such energy accordingly.

One such energy adjustment method is shown schematically in FIG. 12.

Speed control means 18 for one or more motors
achieved by.

The various positions of control knob 20 may be determined by a scale 22 shown in FIG.

The scale 22 is set according to the size of the nail, for example.

A slight excess amount of energy is usually required, since a sufficient amount of energy should be applied to the ram means to ensure adequate consumption of work in the ram means.

However, in order to avoid damage to the workpiece due to the presence of this excessive amount of energy, the ram means is used to provide some degree of damage to the workpiece without denting, parting, drilling, etc. Preferably, means are provided to encourage the consumption of energy.

As such means, the energy absorbing cushion 24
It may be disposed on the protruding piece 26 at the front end of the nozzle 28 to serve to absorb excess energy remaining in the ram means near the end of the working stroke.

However, when the ram means is driven by a flywheel, the use of such a cushion is unnecessary.

Therefore, the length of the ram means is determined in relation to the position of the flywheel behind the lug so that the ram means is positioned prior to the end of the working stroke or the beginning of the working amount of the cushion 24.
Preferably, the driving engagement with the flywheel is severed (see FIG. 7).

Of course, this means that the cushion only needs to absorb the remaining energy without absorbing the energy directly applied to the ram means by the flywheel at the end of the working stroke.

Obviously, the lighter the ram means, the lower the amount of energy remaining at the end of the working stroke.

The ram means advances forward past the flywheel to disengage it, but the clutch re-opens the spacing between the pair of flywheels, at least when drive communication exists between the two members. , a tension spring 30 connected to the ram means.
can serve to send the ram means back past the pair of flywheels to complete its working stroke.

In the particular embodiment shown, the clutch drive means consists of a protruding piece 26 and a fixed link 32, the protruding piece 26 being mounted for retractable movement relative to the nozzle 28, and the fixed link 32 The projecting piece 26 is operatively connected to a shaft-mounted frame 34 that supports the flywheel 16 movable in an arc.

When the protruding piece 26 is moved backward toward the retracted position and pressed against the workpiece W as shown in FIG.
A fixed ring 32 is operative to swing rearwardly on an axially mounted frame 34 to bring the movable flywheel into driving relationship with the ram means.

Once the movable flywheel engages the ram means, the ram means is capable of returning the lug to the extended position within a few seconds of the hand required for the actuation stroke until it is released from the flywheel. cannot be released.

This may be accomplished automatically by clutch release means coupled to bias the frame 34, which is normally axle-mounted, in a direction that increases the spacing between the pair of flywheels.

In the illustrated embodiment, the clutch release means comprises a compression spring 36 which is connected to the retractable lug 26.
, which acts to bias the position toward the extended position.

Thus, before such clutch release means is activated, the biasing force applied to the protruding piece should be large enough to exceed the retraction force exerted on the protruding piece by the workpiece W.

In practice, as soon as the ram means has completed its working stroke, the operator disengages the projecting piece from the workpiece, thus activating the clutch release means to widen the spacing between the pair of flywheels and release the spring 30. Action can cause the ram means to retract.

FIG. 2 shows a perspective view of a tenth embodiment of the nailing machine, the case or housing part of which is formed by the nozzle 28 being designated by 40.

Immediately behind the nozzle 28 a so-called flywheel 42 is provided.

This flywheel chamber 42 accommodates a driving means consisting of a pair of identical electric motors 44, a movable shaft-mounted frame 34 for attaching one of the pair of electric motors, and a fixing member 46 for attaching the other one. ing.

An upper rim 48 of the bundle gripper 50 extends rearwardly of the flywheel as an integral part of the housing in longitudinal alignment with the nozzle.

The upper rim 48 of this bundle is hollow and suitable for accommodating the ram element 12 in the retracted position (see FIGS. 5 and 6).

In the illustrated embodiment, a control knob 20 of the speed control means 18 is arranged on the wall 52 behind the bundle 50 (located along a scale 22 arranged according to nail size, etc.).

Bundle 50 has a generally C-shaped configuration, as seen in many electrically driven, hand-held tools.

Bundle 50 also supports a trigger 54 and a line cord section 56 suitable for connection to a power source when the self-storing power source is not in use.

As shown, the case 40 is comprised of a pair of cast halves bolted together and has a removable movable cover 58.

Additionally, the illustrated embodiment is provided with an aperture 60 that allows a fastening device 62, such as a nail, to be fed into the path of the advancing ram means 12 (FIGS. 1, 8, and 9). reference).

A magazine or fastener housing 64 of conventional design is used to guide a commercially available bell-shaped nail into an opening 60 in the side of the nozzle.

As can be seen with reference to FIGS. 3 to 7, which show details of the internal structure of the tool according to the invention, a fixed end plate 66 is disposed at the bottom of the flywheel chamber 42, and this fixed end plate 66 is connected to the fixed electric motor 44F. It supports a bearing 68 for the axis γOF of.

An upright wall 72 connects the flywheel compartment to two electric motors 74 and 7.
It is divided into 6 parts.

A horizontal wall γ8 formed integrally with the wall 12 separates the two motor compartments 14 and 76 from the vehicle compartment 80 by a distance.

In the drawing, this horizontal wall 18 is shown supported on a scaffold 82 inside the flywheel compartment.

A pair of additional bearings 68 are placed in fixed positions in one half of the flywheel, one in a groove in the top of the horizontal wall and the other in a groove in the scaffolding.

The flywheel 14, which is fixed in position, is attached to a motor shaft 70F that projects from the motor compartment 14 into the flywheel compartment.

Thus, the stationary electric motor 44F and the flywheel 14 are housed within one half of the flywheel compartment located alongside the ram means 12.

Inside the other half of the flywheel compartment, a movable electric motor 44M,
The shaft 70M and the movable flywheel 16 are housed therein.

In place of the fixed end plate 66, a movable end plate 84 is provided, which supports a bearing 68 for the lower end of the shaft 70M of the movable electric motor 44M.

The movable end plate 84 also cooperates with a number of vertically spaced parallel arm rods 86 to increase the spacing therebetween for engagement with the rams to form driving communication. A pivoted frame 34 is defined which supports a movable flywheel and a movable electric motor 44M for pivotal movement.

The lower end of the pin 8° 8 is non-rotatably fixed to an integrally formed leg portion 90.

Legs 90 are disposed on the underside of movable end plate 84 that slides back and forth on the bottom of the housing.

The illustrated housing is provided with an enlarged portion 92 suitable for receiving a pivot pin whose upper end is rotatably mounted in a socket 94 of movable cover 58.

As shown, arm rod 86 joins web 96 to define a unitary structure that is non-rotatably attached to pin 88.

Each of these arm rods 86 and movable end plate 84 supports a bearing 68 for shaft 70M of movable electric motor 44M.

The gap 98 formed in the horizontal wall body 78 accommodates the shaft 70M of the movable electric motor, and allows the frame 34 mounted on the shaft to move between the engaged position and the disengaged position relative to the shaft 70M. It can be allowed to swing in an arc.

As shown in FIGS. 1 and 3, the pivot axis set by pin 88 is located behind the movable flywheel spin axis set by movable motor shaft 70M.

Thus, even when fully engaged as shown in FIG.
The spin axis remains in front of the pivot axis perpendicular to the path of movement of the ram means towards the extended position.

As shown, the ram means is longitudinally slidable and loosely fitted in a groove 100 in the fixed link 32 for driving the clutch, with the ram means being loosely fitted in a groove 100 of the fixed link 32 for driving the clutch, about 200 yen required for engagement with the fixed flywheel. It can move laterally by a distance of .54c/rL (1 inch).

However, once engaged, the ram means will move according to a straight path defined by the shoulder 102 which provides a guideway or track groove remote from the movable flywheel that forces the ram means against the fixed flywheel. .

To this end, the angle θ and the normal plane shown in FIG. 1 are defined during the forward movement of the ram means.

The return movement stroke of the ram need not take place along a straight path, but in fact proceeds along a slightly oblique path.

As can be seen with reference to FIGS. 3-11, a pair of rearwardly extending parallel arms 104 are attached to the rear surface of the lug 26 and are confined between a normally extended position and a retracted position. Nozzle 28 for reciprocating movement
located within.

These pairs of arms serve a dual function, the first of which is to guide the ram means according to the groove 100 between an extended position and a retracted position.

The second function is the frame 34 on which these pair of arms are mounted.
is operatively connected to the arm rod of the clutch, thus defining, in cooperation with the projecting piece, a fixed link 32 for driving the clutch.

Said pair of arms 104, which themselves provide a guideway for the ram means, are connected to the nozzle 28 and the upper rim 4 of the bundle.
8 and the underside of the movable cover 58 in a groove 106 which can be guided for a limited reciprocating sliding movement.

In contrast to the ram means 12, the arm 104 is confined within the groove 106 and its movement is limited to be substantially linear.

As shown in detail in FIGS. 10 and 11, a fixed limit stop 108 provided on the underside of the movable cover 58 is connected to a movable limit stop 1 supported by an arm 104.
10 and serve to limit the forward movement of the fixed link 32 for driving the clutch.

The rearward movement of the fixed link 32 is stopped when the protruding piece 26 engages the front end of the nozzle.

One or more springs 36 placed between the opposing faces of the nozzle and the lug typically act to bias the lug toward the extended position.

The compression spring 36 is automatically actuatable to disengage the clutch as soon as the fixed link 32 for driving the clutch is de-energized by the return movement of the lug towards the normal extended position, thereby providing a latch release means. It consists of

As shown in FIGS. 3 to 7, the end of the arm rod 86 of the frame 34, which is mounted on a shaft, is provided with a number of ears 112 arranged vertically at the end remote from the pin 88. A number of ears 112 are received in notches 114 in a boss 116 formed on one side of the arm 104.

Thus, the connection formed between the arm 104 and the fixed link 32 for driving the clutch, which is constituted by the protruding piece 26, connects the arm 104 to the flywheel and the frame 34 mounted on the shaft.
It is possible to achieve the effect of operatively connecting to the clutch means constituted by.

When the fixed link 32 for driving the clutch is biased by pressing the protruding piece against the work piece with a force greater than the biasing force applied thereto by the spring 36, the frame 34 is moved into an arcuate shape. As it is swung rearward, the distance between the pair of flywheels is narrowed, and engagement of the clutch is thus achieved by gripping the ram between the pair of flywheels.

As previously stated, once engaged, the clutch remains in the engaged position until the ram means is removed from the flywheel.

When the ram means leaves the flywheel as shown in FIG.
The clutch can be disengaged and, under the action of a compression spring 36 acting as a clutch release element, the fixed link 32 for the clutch drive can be automatically disengaged.

In other words, as long as the projecting piece remains pressed against the work piece, the spring 30 acting to retract the ram means will pull the ram means rearwardly into contact with the pair of flywheels. The pair of flywheels are maintained in an unseparable position to prevent the ram means from passing between them.

As soon as the pressure on the lug is relieved to the point where it can be extended by the biasing force of the clutch release spring 36, the spacing between the pair of flywheels widens again and the ram means performs a return stroke. It will end.

The flywheel engaging the surface of the ram means is provided with friction butts 11 made of some kind of wear-resistant material with a fairly high coefficient of friction, for example common brake lining material.
8 has been applied.

Limiting stop 120 (see FIG. 5) becomes operative when spring 80, acting to urge retraction of the ram means, biases the ram means rearwardly.

As best seen in FIGS. 5, 8 and 9, the forward end of the ram means is shaped to form a protrusion 122 defined at the top and bottom by shoulders 124.

This protrusion 122 passes through an aperture 126 provided in the protrusion piece 26 when the shoulder 124 engages the cushion 24.

If there is any energy remaining in the rad means at the end of the working stroke, either the cushion absorbs such residual energy or the protrusion of the ram means abuts against the work piece itself.

5, 6, 7, 11 and 12 show the construction of the trigger 54 and the secure interconnection between the trigger 54 and the fixed link 32 for driving the clutch. The format is shown in detail.

Trigger 54 is pivotally mounted within the handle opening in conventional manner and is normally biased forwardly by spring 128.

When the trigger 54 is manually moved to the retracted position,
It serves to close a normally open on-off switch 130 located within the lower rim 132 of the handle.

A vertically located T-shaped hole 134 is integrally formed in the inner web 136 of the handle above the trigger 54.

Said T-shaped hole 1 having the effect of limiting vertical sliding
Disposed within 34 is a limit stop 138 operatively connected to trigger 54 by link 140 .

When the trigger 54 is driven retracted toward the energized position, it serves, via the link 140, to lift the limit stop 138 and displace its forward projection 142 from the arm 104, thereby displacing the clutch drive means. The fixed link 32 moves rearward to achieve clutch engagement.

When the trigger is released, the forward projection 142 of the limit stop 138 serves to prevent the retraction movement of the projection 26 necessary for engagement of the clutch.

Thus, if the tool were to be dropped while it was in operation, the operator could actuate the trigger to intermediate the protrusion 142 to prevent engagement of the clutch and thus release the nail. The ram means can be activated.

As shown in FIGS. 6, 7, 8 and 9, the fastener receiving frame 64 is of more or less conventional construction, with upper and lower parallelogram plates 144 and 146. The pair of plates are interconnected at their leading edges by a wall 148.

Additionally, the wall 148 cooperates with the pair of plates to define an opening that opens rearward.

a pair of tracks 150 suitable for receiving therebetween the body of a fastener 62, such as a nail, and slidably retaining the fastener in alignment with the protrusion 122 of the ram element;
is located just inside the opening in the trailing edges of the pair of plates 144 and 146.

The head of the nail abuts against said track and is advanced into position driven by a follower 152 which is pulled under the action of a coiled tension spring 154.

As shown, a number of nails are connected in a belt by conventional paper tape 156.

The nail at the end of the belt chain abuts a stop 158 inside the nozzle across the appropriate opening 60 to hold it in alignment with the protrusion of the ram means.

The second nail is held behind the first nail by a track 150.

Therefore, when the ram means advances, the first nail is separated from the belt chain line and driven into the work piece W by the action of the ram, and subsequently the clutch drive means is disengaged and the clutch drive means is disengaged. As soon as the ram is opened and the ram means is returned to the retracted position away from the nozzle under the action of the spring, the follower becomes operative to move the second nail into the drive position.

To refill the tensioner receiving frame with the tensioner, the follower can be pulled in much the same way as in a wire sewing machine.

Since there is nothing new about the tension device storage frame itself, a detailed explanation of its structure will be omitted.

The same can be said of the motor speed control circuit shown in FIG. 12, which includes elements that are mechanically extremely important to the tool itself.

It should also be understood that tools having the parameters listed below are practical and can effectively accomplish the applications described above.

Flywheel diameter: approx. 7.62 crrL (3 inches) Flywheel speed: 7000r,p,m.

Ram element speed: approx. 25.4 rrv': seconds (1000
inches per second) Electric motor horse car: 1.125 horse power Total tool weight: approximately 4.54 kg (10 lbs) The illustrated embodiment detailed above is adapted for driving fasteners such as nails. It should be understood that the invention is not limited to such embodiments, but is susceptible to various modifications.

For example, the ram element could impinge directly on the workpiece, acting like a stamp, punch, or chisel.

Preferred embodiments of the present invention are listed below.

(1) A method for driving a tensioning tool, which comprises the steps of rotating a pair of flywheels in opposite directions, and transmitting energy from the flywheels to a ram for driving the tensioning tool. Tool drive method.

(2) A driving machine that applies a desired driving force to the object to be driven, the housing having a driving path as a parent and a child, and the driving path directed toward the driving object; and ram means adapted to reciprocate in the opposite direction;
a flywheel, a means for rotating the flywheel, and means for supporting at least one of the ram means and the flywheel, and at a position normally spaced relative to the other not supporting the ram means and the flywheel; moving the flywheel and ram means into driving engagement to move the ram means along the travel path to move the ram means toward the driving target. 1. A driving machine comprising control means for moving in the direction of the object to be driven so as to apply a desired driving force to the object.

(3) A driving machine that applies a desired driving force to an object to be driven, wherein a casing that defines a driving path and the inside of the driving path are directed toward the object to be driven. , and a flywheel adapted to reciprocate in the opposite direction, and means for rotating the flywheel, the flywheel being proximate but spaced apart from the ram means. means for supporting the flywheel in its normal position, the bearing means being movably mounted, and moving the bearing means to bring the flywheel into driving engagement with the ram means. , means for moving the ram means along the travel path and in the direction of the driving object so as to apply a desired driving force to the driving object. Characteristic driving machine.

(4) A fastener-driven driving machine, which includes a casing defining a travel route, a flywheel means, a power means for rotating the flywheel means, and a ram means movable within the travel route. , and a supply means including a magazine for supplying a tensioning device for sequentially supplying the tensioning device onto the travel path, and the flywheel means and the ram means are drivingly connected to each other,
a clutch means for propelling the ram means with a travel stroke along the travel path toward a tensioning device disposed within the travel path, thereby driving the tension device; A driving machine comprising a control means for controlling a clutch means.

(5) A fastener-driven driving machine, comprising: a housing defining a travel route; a ram means movable along the travel route with a travel stroke; and a ram means supported by the housing. a pair of flywheels rotating in opposite directions, and means for transferring energy from the flywheel to the ram means, thereby propelling the ram means in a travel stroke. A driving machine.

(6) A driving machine for applying a driving force to a driving object, comprising: a ram means adapted to move along a path and having a friction surface with a friction of a given coefficient of friction; a rotating body for storing the energy to be applied to the ram means; and a clutch means for bringing the rotating body into engagement with a friction surface of the ram means; A driving machine characterized in that the driving machine includes means for rotating the pivot, which is spaced apart from the ram means on the other side, toward the ram means.

(7) A tool held by hand, which includes a housing, a workpiece working means supported by the housing, and a movable crab knit connected to the workpiece working means located in the housing to work the workpiece working means. , and the moving crab unit includes at least one rotating body mass,
rotating in one direction with sufficient speed to cause a chiroscopic advance of the housing, and the housing has another rotating body rotating in a direction opposite to this direction of rotation, (8) A tool (8) characterized in that it has a speed and mass sufficient to counteract the chiroscopic leading of the housing. A casing that communicates with the flywheel compartment;
and ram means for longitudinal sliding movement within the housing;
a ram means whose range of motion is between the most retracted position within the flywheel chamber and the most advanced position protruding into the nozzle; a flywheel whose axis of rotation is a parallel axis perpendicular to the direction of travel; and a drive means connected to the flywheel for rotating the flywheels at substantially the same speed in mutually opposite directions; pivot bearing means for at least one axle of the pair of flywheels for relatively arcuate movement in a direction that changes the spacing between the two flywheels; act in conjunction with the ram means to frictionally grip the ram means therebetween to restrict the clutch and propel it to the point where no further driving contact is possible; a clutch actuation means connected to the pivot bearing means;
There is one that shifts the flywheel to a ram drive relationship,
and there is a clutch release means which cooperates with said pivot bearing means to cause the two flywheels to again widen the distance as soon as the flywheel is separated from the clutch actuating means and is no longer under the influence of the clutch actuation means, and in said ram means. ram return means connected thereto for automatically returning the ram means to its retracted position, the ram return means being adapted to be followed by subsequent forward movement of the ram means and movement of the clutch release means; A driving machine characterized by certain things.

(9) One flywheel 16 is movable in an arc around the pivot axis of the mounting means, the spin axis of the other flywheel 14 is fixed in position, and the flywheel movable in an arc swings backwards toward the locking position. The driving machine according to item (8), characterized in that it is movable.

(lq) The driving machine according to item 8), further comprising a stopper placed on the path of the ram means 12 to prevent the ram means from moving forward.

(11) The driving machine according to item (8) above, further comprising a stopper placed on the path of the ram means 12 to stop the coloring means at the retracted position.

(1) A clutch drive means is attached to the front end of the nozzle 28 and includes a protruding piece 26 which is movable relative to the nozzle between an extended position and a retracted position, and the protruding piece and the attachment means. and a link element operable to engage the clutch when the projecting piece is moved to the retracted position. Machine.

(13) The clutch release means includes a biasing member disposed to bias the attached means in the direction of disengaging the clutch. ) Driving machine described in item.

04) one of the flywheels is arranged to be rotatable about a fixed spin axis, and the ram means 12 is limited to the extent that it moves into a position suitable for frictional engagement with the fixed flywheel; The driving machine according to item (8), characterized in that the driving machine is arranged so as to be able to perform a lateral movement.

(L5) A retractable stop is disposed in operative engagement with the clutch to normally maintain the clutch in a disengaged position, and a manual trigger 54 is coupled to the stop for one actuation thereof. The driving machine according to the above-mentioned item 8, characterized in that the driving machine is operable to move the stopper to the retracted position and release the clutch to move it to the locking position.

(6) A second opening is provided in the nozzle 8 along the path of guided movement of the ram means 12 defining a breech of suitable size to receive the implant; The driving machine according to the above-mentioned article 8, characterized in that means are provided which are operable to receive and releasably hold the driving object in the vicinity of Cξ in the path of travel of the ram means.

(L7) characterized in that the drive means comprises at least one electric motor, and the speed control means 18 are electrically connected to said electric motor and are operable to vary the rotational speed of the flywheel when driven. The driving machine according to the above item (8).

(L8) The length of the ram means is related to the clutch position so that the ram means 12 can work forward toward a clutch-disengaged position before reaching the end of the nozzle 28. The driving machine according to item 8), characterized in that:

α9) The driving means includes a pair of electric motors coupled to individually drive the pair of flywheels in mutually opposite directions at substantially the same speed. ) The driving machine described in item 2.

(c) One flywheel is mounted so that it can rotate in an arc shape relative to the ram means 12, and the other flywheel is supported so that it can rotate around a fixed spin axis, and these pair of flywheels 14.16 and the opposing surfaces of the ram means 12 are shaped so that their spin axes are parallel and in contact with each other along straight tangents, and the spin axes of the arcuately movable flywheels are attached to the means. in cooperation with the pivot axis define a plane that intersects a second plane perpendicular to the direction of motion of the ram means, the intersection having a tangent value between the contact surfaces of the ram means and the arcuately movable flywheel; The driving machine according to No. 8, characterized in that the driving machine is formed at an acute angle that is equal to or smaller than the coefficient of friction.

(21) The opposing surfaces of the ram means 12 and the pair of flywheels 14.16 are in contact along a line parallel to the axis of rotation of the pair of flywheels, and the arcuately movable flywheel and the ram means are protected. The mounting is arranged between the pivot axis of the means and the arcuately movable flywheel mounted on the means so that when the spin axis of the flywheel remains in a position forward of the plane defined by the flywheel itself and the ram means. The driving machine according to the ninth aspect, characterized in that the spin axes are related to each other and to the line of contact between the flywheel and the ram means.

(c) Attachment means, a flywheel movable in an arc shape supported by the means, and the ram means are parallel to the direction of movement of the ram means toward the extended position when the flywheel and the ram means are engaged. The contact surfaces of the ram element and the arcuately movable flywheel are positioned relative to each other such that the surfaces intersect at an acute angle to the plane defined by the spin axis of the flywheel and the pivot axis of the mounting means. The driving machine according to the ninth order, characterized in that the coefficient of friction between the two is at least equal to the tangent value of the acute angle.

(c) A stopper for forward movement of the ram means consists of a cushioned member disposed at the tip of the nozzle, and the cushioned member stops the ram means before it contacts the workpiece placed at the front of the nozzle. The driving machine according to the above box, characterized in that the driving machine is adapted to absorb and dissipate most of the stored excess energy.

A stopper for rearward movement of the ram means is arranged to stop the ram means in a retracted position such that the clutch begins to engage the ram means at its forward end portion. (11) The driving machine described in l'J.

characterized in that the length of the ram means relative to the position of the clutch is determined such that the ram means disengages from the clutch when the front end of the ram means reaches the front end of the nozzle. The driving machine according to item bx above.

(c) The driving machine according to item (a) above, wherein the tangent value of the acute angle is smaller than the friction coefficient.

Paragraph 1, characterized in that the ram means and the pair of flywheels are shaped such that their opposing surfaces are in contact along a straight tangent parallel to the spin axis. driving machine.

(c) The driving machine according to item (c), wherein the friction coefficient is larger than the tadiene value of an acute angle.

(a) The spatial relationship between the elements is determined such that the ram means disengages from the clutch before reaching the front end of the nozzle. driving machine.

- characterized in that the direction of movement of the flywheel movable towards the ram means comprises a first component perpendicular to the direction of movement during the working stroke of the ram means and a second component in the opposite direction; The driving machine according to item 3) above.

(31) The support means includes a lever extending between the axis of rotation of the flywheel and a pivot line perpendicular to the travel path and spaced apart from a plane passing through the axis of rotation.
The driving machine described in (to).

(3) A driving machine characterized in that a second flywheel that rotates in the opposite direction to the flywheel described in the above-mentioned item is attached to the opposite side of the ram.

03) The driving machine according to item 1, wherein the second flywheel has a rotation axis fixed in position relative to the traveling route.

- Driving machine according to item (4), characterized in that it further comprises adjustable speed control means 18 connected to the power means and serving to control the rotational speed of the flywheel.

(g) The driving machine according to the above-mentioned Patent No. 4, wherein the control means includes an element responsive to the positioning of the housing in the vicinity of the work piece.

(g) The driving machine according to item (4), wherein the control means includes a manually operable element.

p. The driving device according to item (4) above, wherein the power means includes a rotatable electric motor, and the control means includes a manually operable electric switch for energizing the electric motor. Machine.

(G) The driving machine according to item (4) above, wherein the flywheel means comprises a pair of flywheels located along both sides of the ram means and rotating in opposite directions.

09) directing at least one flywheel from a first position in which the distance between the pair of flywheels is greater than the thickness of the ram means to a second position in which the distance is less than the thickness of the ram means; The driving machine according to the above item, characterized in that it includes a connecting means having an element for moving the driving machine.

- Driving machine according to item 29), characterized in that the ram means has a portion of thickness that is shorter than the spacing in the second position.

(b) A pair of flywheels are located on opposite sides of the ram, and the energy transfer means includes a gripping element for sandwiching the ram means between the pair of flywheels. The driving machine described.

(6) workpiece retaining means supported by the housing and movable in response to engagement with the workpiece; and coupled between the projecting piece and the gripping element, the workpiece retaining means being responsive to movement of the projecting piece; The driving machine according to item (41), further comprising link means for controlling the gripping element.

0→Energy transfer is achieved by interposing a ram means between a pair of flywheels.
) The method of driving the tensioning device described in section 2.

- rotating a pair of flywheels in mutually opposite directions, with one flywheel rotating around a relatively fixed axis of rotation and the other flywheel rotating around a relatively movable axis of rotation; The method for driving a tensioning device according to item U)IJ, characterized in that:

(iv) The ram means is sandwiched between the pair of flywheels by pivoting a relatively movable axis of rotation about an axis spaced apart from a plane containing the axis of rotation. The tension tool driving method described in hx.

←→ The tension tool drive according to item (1), further comprising the step of controlling the amount of energy transferred to the ram means by adjusting the rotational speed of the pair of flywheels. Method.

07) The above leprosy, characterized in that the predetermined coefficient of friction is approximately equal to the value of the tangent of an acute angle defined by a line approximately perpendicular to the passage and a line passing through the axis of rotation and the pivot point of the rotating body. 6. Driving machines listed in order.

(c) The tool according to item 7), wherein the moving crab knit rotating body includes a pair of rotating bodies that rotate in opposite directions.

- The tool according to the above item (f), characterized in that the moving crab knit further includes a pair of rotary motors respectively attached to each of the pair of flywheels.

- The tool according to item (7) above, characterized in that a pair of rotating bodies is coupled to a workpiece working means.

[Brief explanation of drawings]

Fig. 1 schematically shows the main operating parts of the tool according to the present invention, Fig. 2 is a perspective view of the tool shown in Fig. 1, seen from the upper left side of the rear end, and Fig. 3 clearly shows the internal structure. Fig. 4 is an enlarged cross-sectional view taken along line 4-4 in Fig. 3;
The figure is a vertical cross-sectional view taken along line 5-5 in figure 3 with the same magnification as figure 4, and figure 6 is a longitudinal cross-sectional view taken along line 6-6 in figure 5 to reveal the interior. In order to do this, we broke a part of the
Figure 7 is a similar cut-away view of Figure 6 showing the ram means in a fully extended position. Figure 8 is a further enlarged sectional view taken along line 8-8 in Figure 3, and Figure 9 is the same magnification as Figure 8, with a portion cut away to reveal the internal structure. FIG. 10 is a partial cross-sectional view at the same magnification as FIG. 5, showing details of the energized trigger and the protrusion remaining in the extended position; FIG. 11; 10 is a sectional view similar to FIG. 10 showing the protruding piece in the retracted position, and FIG. 12 is a diagram schematically showing the speed control circuit of the electric motor. In addition, W is a work piece, 10 is an embodiment as a nailer, 12
is a ram element (ram means), 14.16 is a flywheel, 18
20 is a speed control means, 20 is a control knob, 22 is a scale, 24 is a cushion, 26 is a protruding piece, 28 is a nozzle, 30 is a tension spring, 32 is a fixed link, 34 is a movable member (frame mounted on an axis), 36 is a compression spring, 40 is a case (casing), 42
44 is an electric motor, 44F is a fixed electric motor, 4
4M is a movable electric motor, 46 is a fixed member, 48 is an upper rim,
50 is a bundle, 52 is a wall, 54 is a trigger, 5
6 is a line cord part, 58 is a movable cover (lid), 60 is an opening, 62 is a fastener such as a nail, 64 is a fastener storage frame (magazine), 66 is a fixed end plate, 68 is a shaft bearing, 70 is a axis, 70
F, 70M is the shaft, 12 is the wall, 74.76 is the motor room, 7
8 is a horizontal wall body, 80 is a flywheel chamber, 82 is a scaffold, 84 is a movable end plate, 86 is an arm rod, 88 is a pin, 90 is an integrally formed leg portion, 92 is a large part, 94 is a socket, 96 is a web, 98 is a gap, 100 is a groove, 102 is a shoulder, 10
4 is an arm, 106 is a groove, 108 is a fixed limit stopper, 110 is a movable limit stopper, 112 is an ear portion, 114
is notsuchi, 116 is boss, 118 is friction bat, 120
122 is a protruding portion, 124 is a shoulder portion, 12
8 is a spring, 130 is an on-off switch, 132 is a rim, 134 is a T-shaped hole, 136 is a web, 138 is a limit stopper, 140 is a link, 142 is a protrusion, 144°1
46 is a board, 148 is a wall, 150 is a track, 152 is a follower, 154 is a tension spring, 156 is a paper tape, 15
8 is a stopper.

Claims (1)

[Scope of Claims] 1. There is a driving tool driving means supported in a housing, and a moving crab unit coupled to and actuating the driving tool driving means is provided in the housing, and the driving tool driving means is provided in the housing. The crab knit includes a first balance rotating body of the required mass, which rotates in one direction at a speed sufficient to exert a rotation-based force on the casing, and further includes a first balance rotating body having the required mass, which rotates in one direction at a speed sufficient to exert a rotation-based force on the housing, and further rotates in a direction opposite to the direction of this rotation. A rotating second balance rotating body is located in the housing, and has a speed sufficient to substantially cancel out the force based on the above-mentioned double rotation exerted on the housing. Insertion machine. 2. The driving machine according to claim 1, which applies a driving force to the object to be driven, wherein the housing has a travel path, and the driving tool driving means has a driving path. A ram means as a movable member is provided so as to reciprocate within the travel path toward and away from the object to be driven, and the first balance rotor support section and , the second balance rotor support part are arranged opposite to each other with the ram means in between, the first balance rotor support part is movable, and the first balance rotor support part is movable to support the first balance rotor. A driving machine, characterized in that it is driven into engagement with a ram means and further presses the ram means against the second balance rotating body. 3. The driving machine according to claim 1, which applies a driving force to the object to be driven, wherein the housing includes a nozzle extending forward, and the nozzle includes: having an opening at the forward end, the nozzle communicating with the rear flywheel, and ram means being provided within the housing;
The flywheel is guided to slide in the longitudinal direction between a most retracted position within the flywheel chamber and a most advanced position protruding into the nozzle, and the first balance rotating body and the second The balance rotating body is a pair of substantially similar flywheels, which are mounted on shafts so as to face each other with the ram means in between and rotate adjacently, and the balance rotating body is a pair of flywheels that are substantially the same, and are mounted on shafts so as to rotate adjacently to each other with the ram means in between. The axis of rotation of the rotating body is perpendicular to and substantially parallel to the method of movement, and a drive means is connected to the flywheel and rotates the flywheel in the opposite direction at substantially the same speed. The movable member supporting the flywheel is mounted on a shaft within a housing,
Moreover, the axle is configured to change the spacing between the flywheel and the ram means by the arch-shaped movement of the movable member to bring the ram into frictional gripping engagement or to disengage the engagement. A link for causing the movable member to move in the arch shape is provided in the housing so as to be slidable in engagement with the movable member. A clutch actuating means is constructed by connecting the link to a retractable protruding piece provided in the nozzle part, and a compression spring is interposed between the protruding piece and the nozzle part, so that the protruding piece is detached from the work piece. a clutch release means for moving the protruding piece away from the nozzle portion to cause the link to slide and the movable member to disengage the flywheel from the ram means; and the ram means, and a ram return means for returning the ram means to its original position when the flywheel is detached from the ram means. 4. A fastener-driven driving machine, comprising: a housing having a travel path; a ram means movable along the travel path during a driving stroke; and a pair of rams supported by the housing. a pair of flywheels rotating in opposite directions; and means for transferring energy from both of the pair of flywheels to the ram means to propel the ram means with a driving stroke. Machine 5 The driving machine according to claim 4, further comprising a work piece holding means provided in the housing so as to be movable in response to engagement with the work piece. , a protruding piece as part of the work piece engaging means is retractably provided in the nozzle portion of the housing, and the surface also moves one or both of the flywheels towards the ram means in response to movement of the protruding piece. A driving machine characterized in that a link means is provided connected between the means for controlling movement towards and away from the driving machine.