Regulator for a power tool .

The present invention relates to a regulator for fasteners, such as screws, bolts and rivets.

When arranging a screw or a bolt, provided with a thread into a hole with a corresponding thread, a tool, such an electric wrench may be used. The screw or bolt has to be tightened to a predetermined torque in order to achieve a rigid joint. In mass production e.g. automobile production, when a large number of screws or bolts are to be applied, it is important that the screws or bolts are tightened to a predetermined torque in a short period of time.

In order to achieve the predetermined torque within a short time period a regulator is connected to the tool regulates the tool .

A known regulator, which is used when tightening fasteners, is the PID regulator. Such a PID regulator gives an output signal u(t) according to:

u(t) = Kp » _e (t) + K ₁ \e{t)dt + K _D -e{t) (fl)

^e v ⁾ is the deviation in the output signal and is received from a reaction in the system. A large value of K _p leads to an increased rapidity of the regulator, but also to a decreased stability. The value of K ₁ eliminates stationary errors in the output signal, but will decrease the stability if too large. Derivation, by using a proper value of K _D will increase the stability. However, it is often connected to difficulties to find a proper value of K _D , especially when the noise level of the output signal is high. The values of K _p K ₁ and K _D is chosen from general theory and is known for the skilled person.

However, one drawback using a PID regulator is that it is difficult to reach an acceptable torque within such a short period of time, since there has to be enough time left for compensation by K ₁ and K _D . As a result, the efficiency will decrease and therefore heat develops in the tool. Also, the load or strain on the power tool will increase due to large acceleration forces and variations in the current to the motor, which leads to low endurance of the tool and poor ergonomics for an operator handling the tool.

An objective problem to be solved by the present invention is to achieve a regulator which increases the efficiency when tightening a fastener.

Another objective problem to be solved by the present invention is to provide a regulator for a power tool which accurate tightens a fastener to a predetermined torque or force at a minimum of time.

Yet another objective problem to be solved by the present invention is to improve the ergonomics for an operator handling a tool for tightening fasteners.

Another objective problem to be solved by the present invention is to decrease the load or strain on a power tool for tightening a fastener.

This is achieved by a regulator according to claim 1.

The above mentioned objectives are obtained by using the energy contributions within the system in order to regulate the instantaneous motor current, yielding a motor torque, to obtain the target torque value. By using the kinetic energy for tightening the fastener and to control the power tool using the current to the motor of the power tool, a specific amount of energy, corresponding to a predetermined

torque, is achieved in the fastener, thereby improving the tightening properties with respect to some of the parameters time, efficiency, load or ergonomics.

Ti me .

To achieve a correct target torque value the motor has to be braked to zero speed at the point of target torque . By allowing high speed as long as possible, i.e. brake as late as possible, the time to target torque is minimised.

Effi ciency .

By exploiting the kinetic energy of the motor 7 and gear 8, the motor energy is adjusted so that no excessive energy is used. As a result, a very small amount of energy is transformed into heat and combined with short time the total power consumption is decreased.

Tioad .

Since a substantially linear torque is developed when tightening the fastener and since the current regulated for braking the motor is smooth and at a low level, the acceleration forces and the torque on the power tool will not fluctuate in a range which is critical for endurance of the components, such as gears, in the tool. Also, in favourable conditions the torque from the motor on the gear's can be minimized.

Ergonomi cs .

Since a very small amount of energy is transformed into heat in the tool ergonomics for an operator handling the tool improves. A minimisation of the tightening time leads to a shorter torque build up time, and hence a smaller tool displacement . This results resulting in better ergonomics on hard joints.

Due to low energy losses and a low fluctuation of the output signal from the regulator small deviations from the

predetermined torque is achieved. This is due to using a regulator which is based on the laws of physics. The needed amount of motor torque for reaching the predetermined torque is calculated continuously during the tightening and as a result the accurate brake current will be used even though the characteristics of the fastener changes.

Other advantages and features of the invention can be derived from the following detailed description of exemplary embodiments of the invention, with reference to the drawings .

Fig. 1 is a schematic, partly sectioned view of a tool for tightening a fastener, which tool is connected to a regulator.

Fig. 2 shows a diagram of tightening a fastener using a PID regulator according to prior art,

Fig. 3 also shows a diagram of tightening a fastener using a PID regulator according to prior art,

Fig. 4 shows a diagram of tightening a fastener using a regulator according to the present invention,

Fig. 5 shows a diagram of tightening a fastener using a regulator according to the present invention,

Fig. 6 shows a diagram of tightening a fastener using the conventional PID regulator and a regulator according to the present invention,

Fig. 7 shows a diagram of alternative tightening scenarios for tightening a fastener using the inventive regulator,

Fig. 8 also shows a diagram of tightening a fastener using a regulator according to the present invention, and

Fig. 9 shows a block scheme of a regulator according to the present invention.

Referring first to fig. 1, there is illustrated a fastener 1, which may be a screw or a threaded bolt which is fastened into an internally threaded hole 2 or into a threaded nut (not shown) to unite two or more pieces 3, 4 into a typically rigid part called a joint 5. The fastener 1 is connected to a tool 6, such as an electric wrench, which is provided with an electrical motor 7 and gear 8. The tool 6 is connected to a regulator 9, which regulates the tool 6 when tightening the fastener 1 by turning the fastener 1 at an angle ? about its axis 10. In the figure the fastener 1 is a screw or bolt provided with a head 11, which in the tightened position is arranged on one of the two pieces 3, 4. The fastener 1 may also be a threaded nut which is tightened on a threaded pin (not shown) . The tool may also be a riveting tool, for which the target torque T _target is replace by target force F _target and the angle φ by travelled distance δ , respectively. The tool 6 may be arranged on a robot arm (not disclosed) or held by an operator 12.

Referring now to fig. 2, there is illustrated a diagram of tightening a fastener 1 using a PID regulator according to prior art. The PID regulator is well known by the skilled person. The curve 13 in fig. 2 represents the typical torque load which is developed during the continuous threading of the fastener 1 at an angle φ about the axis 10. In the torque load curve 13 there is a free running period A where only a small torque is required to advance the fastener 1. This is followed by a period B of clamping the head 11 of the fastener 1 against the piece 3 where the pieces 3 , 4 are being brought toward engagement and where

the torque increases substantially linear. The period B ends when a predetermined torque target is reached.

In fig. 2 also the current curve 14 is disclosed as i _q as a function of the angle ^ . In order to reach the target torque T _-arg/ the current i _q , to the electrical motor 7 is regulated according to the current curve 14 by using the known PID regulator. In period A only a small current i _q is required to run the motor. However, due to inertia in the electrical motor 7, the motor 7 must be provided with a control current in period B. According to fig. 2 the control current in period B is a brake current, which brakes the motor 7. The brake current regulated by the PID regulator may fluctuate as disclosed in fig. 2. The fluctuation and the high peak of the brake current leads to high loads or strain on the tool 6, especially the gear 8 of the tool 6, which in turn leads to low endurance of the tool and poor ergonomics for the operator 12 handling the tool .

In fig. 3 a torque load curve 15 exerted on the tool 6 is disclosed when using the known PID regulator. As is evident from fig. 3 the torque load exerted on the tool 6 fluctuates heavily during period B.

The above-mentioned drawbacks in relation to a PID regulator are reduced or eliminated if the PID regulator is further developed.

Fig. 4 shows a diagram of tightening a fastener using a regulator 9 according to the present invention. In fig. 4 the typically torque load curve 130 as described in connection to fig. 2 is disclosed. Also, the speed of

rotation ^ is disclosed as a function of the angle ^ in the diagram of fig. 4. In the beginning of period A the

speed of rotation ^ increases rapidly to a substantially constant level . When reaching the beginning of period B the

speed of rotation ^ decreases as a result of increased torque and braking current provided to the motor 7. When a predetermined target torque T _carget: is reached the rotation

of the motor 7 stops and thus the speed of rotation ψ is zero as indicated in fig. 4.

In fig. 4 also the current curve 140 is disclosed as a function of the angle ^ . In order to reach the target torque Ttarg, the current iq, to the electrical motor 7 is regulated according to the current curve 140 by using the inventive regulator 9. As described in connection to fig. 2 only a small current iq is required to run the motor in period A. However, due to inertia in the electrical motor

7, the motor 7 must be provided with a control current in period B. According to the embodiment disclosed in fig. 4 the control current in period B is a brake current, which brakes the motor 7. The brake current regulated by the inventive regulator follows the curve 140 as disclosed in fig. 4. The current regulated for braking the motor 7 is smooth and lower peak value relative to solutions described in prior art, the acceleration forces and the torque on the tool 7 will therefore not fluctuate in a range which is critical for endurance of the components, such as the gear

8, in the tool. This is evident from fig. 5 in which a torque load curve 150 exerted on the tool 6 is disclosed when using the inventive regulator 9. As is evident from fig. 5 the torque load exerted on the tool 6 fluctuates less and has a lower peak value during period B when comparing to the torque load exerted on the tool 6 using a known PID regulator.

In fig. 6 the current curve 14, 140 is disclosed as iq, ^ as a function of the angle φ and shows the difference between the conventional tightening using an PID regulator and the tightening method according to the invention. In order to reach the target torque Ttarget, the current iq, to the electrical motor 7 is regulated according to the current curve 140 by using the inventive regulator 9. As described in connection to fig. 2 only a small current iq is required to run the motor in period A. The amplitude of the brake current iq 140 is smaller when compared with the brake current 14 using the PID regulator for the same tightening speed counted from the start of the braking period B. Due to the fact that the braking can be initiated in at a later point, the time for tightening will be reduced. High current peaklevels generate high power consumption while a more smooth current profile with a lower amplitude gives a increased efficiency. The current regulated for braking the motor 7 using the inventive regulator 9 is smooth and at a lower level, the acceleration forces and the torque on the tool 7 will therefore not fluctuate in a range which is critical for endurance of the components, such as the gear 8, in the tool .

In fig. 7 the current curve 14, 140, 140' is disclosed as

i _q , ^φ as a function of the angle ^φ and shows a diagram of alternative tightening scenarios for tightening a fastener using the inventive regulator method. The inventive regulator gives the possibility to initiate the braking at different stages in the tightening period depending on how much brake current is accepted. In first alternative speed is maintained until braking is initiated in point B as described in fig. 6, obtaining a tightening time that is similar as for the PID regulator. However is the braking

current 140 more smooth and will consume less energy in total .

The second alternative describes a tightening where the tightening time is chosen as the most important property. By accepting a relative high braking current 140' it is possible to initiate the braking at a later point in time (compare brake points B versus C) , which shortens the time frame from snug level to the Torque target level . Since the correct braking current is calculated in each time step, even though not used before the brake point, it is a matter of configuration when braking should be initiated. The configuration occurs when the calculted braking current i _q exceeds a preset transition to braking threshold value, i _q > 1^ _x, where I _g1113x is a configuration parameter. During ideal conditions the brake current i _q will be at a constant level throughout the braking until target torque as shown in fig.7. That is i _q = i^ _^ . This is a consequence of the formulation of energy contributions in the system and the definition of i _q (f7) as described later on.

In fig. 8 discloses the brake current i _q and the torque load T acting on the gears as a function of time t and shows the properties of different tightening scenarios related to tightening speed which could be chosen by the operator using the inventive regulator. If the tightening time is non critical it is possible to choose a tightening process wherein the brake current is smooth and in which case the applied torque load T acting on the gears can be minimized during said braking. This will also spare the gearings in the system. The curves should be interpreted as follows :

The braking current i _q is relatively small and as a result, a substantial positive torque is acting on the gears during tightening D, while a large braking current results in situation where a substantial negative torque is acting on the gears during tightening F. Using a favourable

braking current as in tightening E the resulting torque on the gears can be minimized. In other words , the torque transferred to the gears from the motor is minimized using a correct brake current .

According to fig. 9 the regulator 9 calculates an output signal iq achieved from the calculation step icalc by taking in account the energy contributions within the system. These are the calculated or predetermined target energy E _target , the kinetic rotational energy E _rot in the motor 7 and in the gear 8, the potential joint energy E. _oint in the joint 5 and the operator energy E _operator from the operator 12.

From the relationships above and from the block scheme of fig. 9 it follows that:

"error ⁼ "target ⁺ "operator ~ "joint ~ "rot \L.4 )

The energy E _error is the amount of energy the motor 7 in the tool 6 should add in order to reach the torque target . According to f2 it is defined as the sum of the above- mentioned energy contributions.

^ _operator i ^{s tne} result of the mass of inertia of the operator using the tool but also the mass of inertia from the tool . The operator may also use an active reaction force. In a rigid or hard joint the influence of E _operator is smaller when comparing to more flexible or soft joints, since the time for clamping the joint up to the target torque is longer for soft joints than for hard joints. If the tool is mounted in a fixture in the form of a robot arm, E _operator can be interpreted as the energy transferred to the fixture.

& in fig. 9 defines the angel velocity with which the operators 12 hand and arm and also the tool 6 turn about the axis 10 when tightening the fastener 1.

The following relationships will be defined:

E _ ( VT * target /) ² target ( ^β )

2*k.

k _: is a measured value from joint characteristics achieved from a number of test runs or pilot samplings and depends on the stiffness of the joint, k. may also be achieved from measures during tightening of the fastener 1.

^JOItIt (f4)

2*k.

J is the inertia of the motor 7 and the gear 8 and ^ ^m is the motor angle velocity.

E "error = (>f ^LO 6)'

i _q is the current which regulates to the motor 7, k_, is a torque constant in the motor 7, ^ _carget is an estimated angel for which the fastener 1 should be tightened in the joint and ^ ₁ is the actual angel for which the fastener 1 is tightened in the joint. N is the gear ratio of the gear 8 of the tool 6. The product of i _q and km gives the motor torque. The relation (^ _target - ^φ _D ) * N gives the remaining motor angle ^. angle to reach the

ψ target ^•

Since i _q = and T = k, * φ _}

the fol lowing equat ion is achieved f rom the relationships above :

T is the actual torque in the joint

As a result the regulator 9 calculates an output signal i _q/ which is dependant on the energy E _error for braking the motor 7 of the tool 6.

Gsys in fig. 9 is the transfer function for the system.

The above-mentioned relationships are also applicable to rivet joints. However, in case of rivet joints, E _target; and E _DOinc above should be replaced by E _target and E _rivet , respectively according to:

k _r is a measured value from joint characteristics achieved from a number of test runs or pilot samplings and depends on the stiffness of the joint. k _r may also be achieved from measures during fastening of the rivet. Ftarget is a predetermined target force for the rivet joint.

Eπvet = -^- (f9)

2 * k

F is the actual force on the rivet joint.

F = k,*J (flO) δ is the distance for compress the rivet.

The energy E _error to brake the tool for riveting is the sum of the following energy contributions.

" Perror — P "target + ^τ P "operator - P "rivet P "rot ( > ^L f ~ ^± \ ~ ⁱ \