GB2063123A - Process and apparatus for producing helical springs - Google Patents
Process and apparatus for producing helical springs Download PDFInfo
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- GB2063123A GB2063123A GB8033761A GB8033761A GB2063123A GB 2063123 A GB2063123 A GB 2063123A GB 8033761 A GB8033761 A GB 8033761A GB 8033761 A GB8033761 A GB 8033761A GB 2063123 A GB2063123 A GB 2063123A
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- 238000005859 coupling reaction Methods 0.000 claims abstract description 28
- 238000006073 displacement reaction Methods 0.000 claims abstract description 25
- 238000007493 shaping process Methods 0.000 claims abstract description 20
- 230000003321 amplification Effects 0.000 claims abstract description 6
- 238000003199 nucleic acid amplification method Methods 0.000 claims abstract description 6
- 238000005520 cutting process Methods 0.000 claims description 13
- 238000004519 manufacturing process Methods 0.000 claims description 12
- 230000001105 regulatory effect Effects 0.000 claims description 10
- 230000001276 controlling effect Effects 0.000 claims description 2
- 230000001419 dependent effect Effects 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 4
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- ZXVONLUNISGICL-UHFFFAOYSA-N 4,6-dinitro-o-cresol Chemical compound CC1=CC([N+]([O-])=O)=CC([N+]([O-])=O)=C1O ZXVONLUNISGICL-UHFFFAOYSA-N 0.000 description 1
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21F—WORKING OR PROCESSING OF METAL WIRE
- B21F3/00—Coiling wire into particular forms
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21F—WORKING OR PROCESSING OF METAL WIRE
- B21F3/00—Coiling wire into particular forms
- B21F3/02—Coiling wire into particular forms helically
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Wire Processing (AREA)
Abstract
A helical spring winding machine (Figure 1) includes:- a pitch tool (140) and at least one shaping tool (138) displaceable mechanically by at least one displacement shaft, with a first drive (122) for the rollers (130) of a slip-free spring wire input (114) and a second drive for each independently displaceable pitch or shaping tool (138,140), each with an electrically controlled motor and with a programme control for one of the two drives.The first drive (122) has a continuously running motor (M1') and a coupling between the motor and the rollers (130). A tachogenerator (246) is connected between the coupling and the rollers. A proportional amplifier is connected between the tachogenerator and the motor of the second drive; a number of values of the amplification factor of the amplifier can be pre- selected by a programme control. To allow for running on of the wire feed after drive cut-off, due to inertia, the pitch and shaping drives continue to operate for a short time. <IMAGE>
Description
SPECIFICATION
Process and apparatus for producing helical springs
The invention relates to a process for producing helical springs, and in particular a spring winding process, wherein at least one rotatable displacement means for displacing a pitch tool and/or at least one shaping tool are or is programme-controlled and the wire is drawn in slip-free, wherein the speed of the wire intake is preselected and, if required, regulated in such a way that it is different, and in particular less, during production of the spring ends than it is during production of the spring body between the ends, wherein each displacement means is used as mechanical control means controlling at least one pitch and/or shaping tool, wherein the displacement and control is carried out continuously and wherein the rotary speed of the displacement and control means is preselected and, if required, regulated.The invention also relates to apparatus for producing helical springs, and particularly to a spring winding machine, with a pitch tool and at least one shaping tool which can be displaced mechanically by means of at least one displacement shaft, with a first electromotor drive for the rollers of a slip-free wire intake and a second drive for each independently displaceable pitch and shaping tool, with an electrically-controlled electromotor, and with programme control for one of the two drives, each displacement shaft being provided as a control shaft which introduces a torque, which is maintained during the control period, into at least one cam gear of a second drive, and wherein the drive of the wire intake rollers can be controlled and, if required, regulated.
In an earlier proposal by us the above-mentioned process is carried out without the use of coupling means and the wire intake in the above-mentioned apparatus is accordingly clutch-free, and in addition, each drive has an electrically-controlled electromotor, programme control is provided for the electromotor of each second drive, the electromotor of the first drive of the wire intake rollers can be programme-controlled, this being independently of the control of the electromotor of the possibly regulated second drive for each control shaft, and the programme control continuously controls the rotary speeds of the electromotors between the start and end of intake and displacement.
The process and apparatus disclosed in our copending Application No. 7921210 is based on the problem of devising a process and apparatus for producing helical springs by means of which helical springs of different shapes and sizes can be produced with constant high quality (precision of shaping) in larger numbers (productivity) and at a lower cost (manufacturing costs of the machine), with increased efficiency (working life of the machine) and reduced burdening of the environment (protection from noise).
The present invention is based on the same problem. However, its solution is intended also to fulfil the additional requirement that the process and the apparatus should be suitable in particular for processing thick wires.
This problem is solved according to the present invention in a process as referred to above by using means for the wire intake coupling which can be connected for operating the wire intake and disconnected for stopping it, with follow-through control, if required, and in that the rotation of the displacement and control means is proportionally controlled at preselectable ratios to the speed of the wire intake, and, to compensate for the running-on of the disconnected wire intake due to inertia, the displacement and control means are rotated further synchronously to correspond with this running-on.Also the problem is solved in apparatus as referred to above in that the first drive has a permanently-running electromotor and a remotely switchable coupling which can be controlled throughout, if required, provided between the said motor and the wire intake rollers, and that a tachogenerator is connected between the coupling and the intake rollers, and between this generator and the electromotor of the second drive a proportional amplifier is connected, for which a plurality of values for the amplification factor can be preselected and selected by means of the programme control.
By this means it is possible in an advantageous way to make use of the momentum of the moving masses of the first drive for the wire intake when processing thicker wires, without prejudicially affecting the advantages of our previous process and apparatus.
Due to the compensation, according to the present process, for the running-on of the disconnected wire intake by further rotation of the displacement and control means, the correct relationship between the moving apparatus parts is maintained even with various different interruptions in production, e.g.
due to switching off in an emergency or when producing a single test spring, so that production can be started up again without special preparation.
In a preferred embodiment of the apparatus according to the invention with an auxilliary control shaft which controls at least one cutting tool and actuates it, if required, and with a drive for the auxilliary shaft which has a constantly rotating electromotor and can be controlled, provision is advantageously made for the auxilliary control shaft to be connected to the electromotor of the first drive via a remotely switchable coupling which can be controlled throughout, if required, and for each second drive for a displacement and control shaft to have a torque amplifier where the electromotor of this drive is combined with a servo-valve and a hydro-motorto form one unitwhich is obtainable in various commercially available embodiments.
By this means the additional requirement set in conjunction with the problem of the invention is completely satisfied, as the operating performance of the cutting-off device and the servo unit can be adequately rated.
The invention is explained in detail in the following with reference to the preferred embodiment of the apparatus according to the invention shown in the Drawing by way of example.
Figure lisa partial front view of the embodiment.
Figure 2 is a partial side view of the same.
Figure 3 is a block circuit diagram of the embodiment, where the mechanical parts are shown schematically.
Figure 4 is a more explicit detail from Figure 3.
Figure 5 is a side view of a compression spring.
Figure 6 is a speed-time diagram for the wire intake of the embodiment, for the case when it is being used to produce the spring shown in Figure 5.
Figure 7 is a corresponding angular speed - time diagram for the main control shaft of the embodiment.
Figure 8 is a profile radius - rotary angle diagram for a control cam of the embodiment.
Figure 9 is a profile radius - time diagram for this cam according to Figures 7 and 8.
The parts of the embodiment which are similar or correspond to the parts of the first embodiment of the apparatus according to our said co-pending application are given reference numerals which are higher by 100 or reference symbols with an apostrophe.
The embodiment of which structural details are shown in Figures 1 to 4 consists mechanically essentially of a wire intake 114, a winding station 116, a control device 118 and an auxiliary control device 120 for processes in the winding station, a first drive 122 for the wire intake 114, a second drive 124forthe control device 118 and a third drive 126 for the auxiliary control device 120.
The wire intake 114which can be braked is formed by three pairs of wire intake rollers 130, making a total of six, which feed an endless wire D' straight horizontally into the winding station 116. All the rollers 130 are driven.
The drive 122 for the wire intake rollers 130 is composed of an electromotor M1', an equalizing gear 132 which directly drives the rollers 130 of all the pairs of rollers, a switching gear 222 and a toothed belt gear 134. The switching gear 222 has a pair 226 of stepping-down cogwheels which can connect the torque-transmitting drive shaft 224 of the toothed belt gear 134 to an auxiliary control shaft 200, if required, a pair 230 of stepping-down cogwheels which connect the larger cogwheel of the pair 226 rotationally with an intermediate shaft 228, a pair 234 of stepping-up cogwheels which connect the intermediate shaft 228 with a coupling shaft 232 of the equalizing gear 132, if required, forming a high-speed gear of the switching gear 222, and a corresponding parallel-connected pair 236 of stepping-down cogwheels as the low-speed gear, together with a switchable coupling 238 disposed between them with three parts seated on the shaft 232, the two outermost of which are connected rotationally fixed to the cogwheels of the pair 234 seated on the shaft 232 and the middle one of which can be brought from its central position which produces idling into contact alternatively with one of the two outer ones to connect up the high-speed or low-speed gear. In the embodiment example the larger cogwheels of the two pairs 230 and 234 are identical, and the larger cogwheel of the pair 226 and the smaller cogwheel of the pair 230 are seated rotatably on the shaft 200 and are connected to each other rotationally fixed. The reason for this arrangement will be clarified later.
In the winding station 116 there are two winding tools 138 which continuously deform the incoming wire D', together with a pitch tool 140 and a cutting tool 142. All the tools can be adjusted, exchanged and are movable. The pitch tool 140 and the cutting tool 142 are each mounted on a carriage 144 or 146 respectively, which are moved in a locationally-fixed slideway 148. The moving equipment for the holder 150 of the two winding tools 138 is not shown in its entirety. What is shown is described in more detal below. The cutting tool 142 co-acts with a projection 152 in the winding station 116.
The control device 118 has two parts which appertain to the winding tools 138 or the pitch tool 140 respectively, and have a common control shaft 154. The first part for winding is constructed as follows: On the control shaft 154 a shaping cam 156 is seated, the eccentricity of which depends on the spring shape required, and on this alone. A roller lever 160 is mounted pivotably on the machine frame 158 and a transmission lever 162 is also mounted rotatably thereon, being connected to the winding tool holder 150. The roller lever 160 runs via one roller 161 on the periphery of the shaping cam 156. Via another roller 163 on one arm of the transmission lever 162 the latter is braced against the roller lever 160. The shaping cam 156 consequently controls the movement of the winding tools 138 when the control shaft 154 is rotated.The second part of the control device 118, intended for the pitch adjustment, is constructed as follows: On the control shaft 154 four control cams 164 are seated, all axially displaceable, which are used alternatively during one rotation of the cam shaft.
These are a threefold cam 164.1, a twofold cam 164.2, a bridging cam 164.3, and a special cam 164.4, with which three or two identical springs are produced per revolution of the control shaft 154, orthe number of springs can be reduced by 2 or 1, or special springs with irregular pitch course overthe length of the spring body can be produced, respectively. The control cams 164 co-act alternately with a cam roller 166 which is mounted on a roller lever 168 which can pivot around an axis 170 attached to the frame and running parallel to the control shaft 154.
On a shaft 172 which is rotatably mounted on the frame 158 parallel to the axis 170 a shaping part 176 is seated freely rotatable, being loaded by a return spring and having a fork and a slideway in which a sliding block engages which is mounted freely rotatable on the roller lever 168 and can be displaced by means of an adjustment spindle; see Figure 4 of our co-pending application. This spindle makes it possible to adjust the pitch tool 140 while the machine is running, which involves apparatus parts which will now be named. On a shaft 186 which is mounted rotatably on the frame 158 parallel to the shaft 172, a fork lever 188 is seated, on which one end of a rod 190 is articulated, the other end of this being articulated on the fork of the shaping part 176.
Between an arm 191 seated on the shaft 186 and the carriage 144forthe pitch tool 140 there is a short gear component 192 which is articulated on the two parts 144 and 191. This completes the kinematic chain between the control cam gear 164 - 166 and the carriage 144, so that the control shaft 154 and the return spring loading the shaping part 176 can move the pitch tool 140 to control it and to return it respectively.
The drive for the control device 118 is composed of a worm gear 194, which directly drives the control shaft 154, and an electro-hydraulic torque amplifier 240 with an electromotor M2' which can be controlled, via an electric proportional amplifier 244 which is described in detail below, by a tachogenerator 246, and can be regulated by means of a tachogenerator 242, the generator 246 being driven by a toothed belt gear 250 connected to an intake shaft 248, and itself actuating a servo-valve 252 which controls a hydromotor 254 for the gear 194, the normal hydraulic supply and draining of which is not shown in more detail.
On the control shaft 154 two contact-free switches 256 and 258 are seated, fixed to the frame, being actuated by means of the successively effective teeth of a toothed disc 260, or by a switching element 262 which is effective only once per revolution of the shaft, both which are seated rotationally-fixed on the control shaft 154. The multiple switching device 260 256 controls amongst other things the electricallyactuated coupling 238 for switching over between the two gears of the wire intake 114. The single switching device 262-258 is used to determine the "first" tooth of the toothed disc 260, with which the initial and terminal rotary positions 0 or 360" of the control shaft 154 correspond during one revolution in the case when a single cam is being used.With the twofold cam 164.2 the angles amount to 0 and 1804 and 1800 and 360" respectively.
The auxiliary control device 120 has the auxiliary control shaft 200, which can be braked, and a cam 202 seated thereon, which moves a connecting rod 204, the free end of which is articulated on a guide arm 206 which is seated loosely on the shaft 186.
In addition, at the articulation point of the connecting rod 204 one end of a rod 208 is articulated on the guide arm 206, having its other end articulated on a lever 210 which is seated on the shaft 172. A short gear component 212 which is articulated both on an arm 211 seated on the shaft 172 and also on the carriage 146 of the cutting tool 142 completes the kinematic chain from the auxiliary control shaft 200 to the cutting tool 142.
The drive 126 for the auxiliary control device 120, which corresponds to the roller drive 122 from the electromotor M1' up to the larger cogwheel of the pair 226, also has a switchable coupling 264 which is seated on the auxiliary control shaft 200 between the frame 158 and the larger cogwheel of the pair 226 which is connected rotationally-fixed to one half of the coupling. The other half of the coupling 264 is connected rotationally-fixed to the auxiliary control shaft 200 and can be braked to stop this shaft. The electrically-actuated coupling 264 is connected up by an impulse counter/switch 266 which is connected to an impulse generator 268 driven, via the toothed belt gear 250, by the intake shaft 248. The impulse counter/switch 266 also controls the coupling 238, as will be shown later.
The electrical proportional amplifier 244 for translating the rotary speed of the intake shaft 248 into the rotary speed of the main control shaft 154 has on the input side a parallel switch 270 which is connected to the direct current producing intake tachogenerator 246 and consists of five potentiometers R1 to R5, the centretappings of which are connected to an electronic switch-over switch 272 actuated via a switching control mechanism 274 which is connected to the switch 256 and which, by means of calculated or programmed control signals, allows through or blocks the control impulses of the switch 256, which are generally aperiodic, owing to the irregular rotation of the control shaft 154.Beside the centre tappings a constant current generator 276 is connected to the switch-over switch 272, equipped with an impedance transformer 278 with a feed-back look 280, an electrical network 282 for adjusting the regulating action of the torque amplifier 240, and an electrical servo-amplifier 284, in that order. The servo-amplifier 284, the electro-motor M2' which is similarly current-controlled by it and the direct current producing tachogenerator 242 appertaining to it form a control circuit, the behaviour of which is determined, as indicated, by the network 282 which makes it possible to influence the acceleration of the rotary speed of the control shaft 154.
By adjusting the potentiometers R1 to R5 it is possible to determine which angular speeds of the control shaft 154 are obtained in high-speed or low-speed operation of the wire intake 114 at specific points in time and during specific phases of the production of the spring. The generator 276 supplies a constant direct current which is independent of the gearing and which ensures a constant angular speed of the control shaft 154 during the cutting process.
The main parts of the impulse counter/switch 266 are two wire-length meters P1 and P2 appertaining to the wire intake 114, which measure and indicate digitally the length of the wire drawn in during the high-speed operation of the wire intake, or the length of wire drawn in during the whole of the spring production process, thus during low-speed operation as well, respectively, together with a programme control to which the control switching mechanism 274 belongs. This can be equipped with a computer which selects a suitable programme according to the characteristic spring data fed into it, calculates and supplies the adjustment values for the two wire-length meters P1 and P2 and for the potentiometers R1 to R5, and carries out the control by continuous amendment of the adjustment values.
To prepare the machine for operation the following steps have to be carried out:
- adjustment of the winding tools 138 to the desired spring diameter or, with changing diameter, to the initial diameter,
- adjustment of the cutting tool 142 and the projection 152 to the cutting point,
- selection of the control cam 164 by the axial displacement of the cam carrier, as shown in Figure 2, until the desired cam is effectively connected with the cam roller 166,
- adjustment of the pitch tool 140 to the desired pitch or, with changing pitch, to the initial pitch,
- selection of one of several programmes for producing tension springs, compression springs with different numbers of windings, and special springs, each with larger, medium and smaller diameters,
- adjustment of the potentiometers R1 to R5to computer or tabular values which are based on the characteristic spring data and determine when or after what length of wire has been drawn in the angular speed of the main control shaft 154 undergoes a change in a specific way,
- adjustment of the wire-length meters P1 and P2 for switching purposes,
- test run to produce one spring which is measured and can result in amendment of the adjustments according to the spring shape and length obtained.
The automatic control of the embodiment of the apparatus according to the invention described above and set up for long-term operation, is as follows, when, for example, the spring shown in
Figure 5 is to be produced with this machine, having a single initial winding a with a constant minimum pitch, three adjoining windings b with increasing pitch, three and a half adjoining windings c with a constant pitch, one adjoining winding d with decreasing pitch, and finally three terminal windings e with a constant minimum pitch:
It is assumed that the machine is in the state in which the electromotor M1' is running, the coupling 262 is disconnected, the coupling 238 has not engaged either the high-speed gear or the low-speed gear, and the electro-motor M2' is running.
Accordingly, the hydromotor 254 rotates the main control shaft 154 first of all at a constant angular speed 276, until the first tooth on the disc 260, determined by the switch 258, gives the starting signal at the time point t = 0 by actuation of the switch 256; this signal actuates the coupling 238 to engage the low-speed gear at the wire intake 114 and also actuates the switch-over switch 272 via the control switching mechanism 274 to switch in the potentiometer R1.This actuation has the final effect that the wire D' is drawn in during the time tl at the speed v1,5.2 and the control shaft 154 is rotated at the angular speed coR1 through the angle 1, where tl = cp1ftoR1. During the time to the chosen twofold cam 164.2, which ensures the production of two springs per revolution of the control shaft, is still not effective.At the end of the time to, which coincides with the beginning of the time t2, the initial winding a is produced, and by means of the multiple switching device 260 - 256 the coupling 238 is again actuated, but this time to engage the wire intake 114 with the high-speed gear, and, via the control switching mechanism 274, the switch-over switch 272 is also actuated to switch in the potentiometer
R2. Accordingly, the wire D' is drawn in during the time t2 at an increased speed v2-5.1, and the control shaft 154 is rotated at the increased angular speed coR2 through the angle cup2, where t2 = (p2ioR2.
During the time t2 in which the windings bare produced, a rising flank on the twofold cam 164.2 and the cam roller 166 co-act so that the pitch tool 140 is displaced approximately linearly in the direction of increasing pitch. During the times t3, t4 and t5.1 which have still to be described, the high-speed operation of the wire intake 114 is maintained, so that the wire speed continues to amount to v2-5.1. At the beginning of the time t3, which coincides with the end of the time t2, the potentiometer R3 is switched in so that the control shaft 154 is now rotated at the angular speed (oR3 lying between oR2 and coR1 ,through the angle (p3, where t3 = (p3/wR3.
During the time t3 the cam roller 166 runs over the arc of a circle, concentric to the control shaft 154, on the two fold cam 164.2, so that the setting of the pitch tool 140 remains unchanged and therefore the pitch of the windings c remains constant. At the
beginning of the time t4, which coincides with the end of the time t3, the potentiometer R4 is switched in so that the control shaft 154 now rotates at the
maximum angular speed (oR4 through the angle 4, where t4 = (p4/oR4. During the time t4 the cam roller
166 runs radially inwards along the downwardssloping flank symmetrical to the above-mentioned
rising flank, on the twofold cam 164.2, which means that the path of the pitch tool 140 during the time t2 is reversed approximately linearly. During this time the winding d is produced.At the beginning of the time t5.1, which coincides with the end of the time t4, the potentiometer R5 is switched in so that the control shaft 154 is rotated further relatively slowly, at the angular speed oR5.1 lying between wRi and wR3, without the pitch tool 140 being displaced, until at the transition from the time t5.1 to the time t5.2 the wire-length meter P1 of the impulse counter switch 266 actuates the coupling 238 to engage the
low-speed gear again, so that the control shaft 154 is
now rotated further at the minimum angular speed oR5.2. During the times t5.1 and t5.2 = t5 the angle
(p5 is covered, where t5 = qu5/;;;E In the times t5.1
and t5.2 the production of the two penultimate windings and the last of the terminal windings e
occurs, respectively.
The reducing of the angular speed of the control shaft 154 from toR5.1 to coR5.2, which is proportional to the ratio of the wire intake speeds v1,5.2 and v2-5.1, can be effected by means of a switching
process in the multiple switching device 260 - 256, the switch 256 of which is connected moreover to the coupling 238, instead of by means of the wire-length meter P1.
At the end of the time t5.2, irrespective of the
rotary position of the control shaft 154, the wire
length meter P2 first switches the coupling 238 to
idling of the coupling shaft 232, whereupon the wire
intake 114 is braked sharply by a brake (not shown)
on the intake shaft 248, secondly, it switches in the
constant current generator 276 instead of the potentiometer R5 which was last effective, whereupon the
control shaft 154 runs on considerably faster, at the
angular speed w276 corresponding, for instance, to wR2, and thirdly, it switches in the coupling 264,
whereupon the cutting tool 142 is actuated and the
wire D' is cut through.
The cutting process must be finished before the
end of the time tS, the beginning of which coincides
with the end of the time t5.2. During the time tS the
control shaft 154 rotates through the angle çS, where tS = + S/co276. In the given example, the condition 91 + 92 + 3 + 4 + 5 + (pS = 180 is fulfilled. lfthethreefold cam 164.1 were being used, then instead of 1800, 1200 would be inserted. Thereafter, the next cam involved is taken into operation, by means of which the pitch is varied within a spring.
Before the end of the time tS, which coincides with t = 0,so that two276 can bypass cho154 = 0 and move directly to oR1 when mass production is being carried out, as described above, the toothed disc 120 is rotated until the emission of the starting signal, into its initial rotary position (Pt = 0, until, according to the type of the cam, 0" = 360" (single cam), 180" or 0 = 360" (twofold cam), or 1200 or 240 or 0 = 360" (threefold cam) is reached.
The spring shown in Figure 5 is cylindrical. If a so-called shaped spring is to be produced, e.g. a conical, waisted or barrel-shaped spring, then instead of a circular disc, the shaping cam 156 is required which controls the winding tools 138.
Claims (10)
1. A process for producing helical springs, for example a spring winding process, in which i) at least one rotatable displacement means for displacing a pitch rool and/or at least one shaping tool are or is programme-controlled and wire is drawn in slip-free; ii) the speed at which the wire is drawn in is preselected and, if required, regulated in such a way that it is different, and for example less, during the production of the spring ends than it is during the production of the spring body between the ends; iii) each displacement means is used as a mechanical control means, controlling at least one pitch and/or shaping tool; iv) the displacement and control are carried out continuously; and v) the rotary speed of the displacement and control means is preselected and, if required, regulated, characterised in that, for drawing in the wire, coupling means are used which can be connected up to operate the wire intake and disconnected to stop it, with follow-through control, if required, and that the rotation of the displacement and control means is proportionally regulated at preselectable ratios to the speed of the wire intake and to compensate for the running on of the disconnected wire intake due to inertia, the displacement and control means are rotated further synchro nouslyto correspond with this running on.
2. A process according to Claim 1 in which the wire is cut off at the spring ends, characterised in that the rotation of the displacement and control means is continued during the cutting off process after the wire intake has been stopped, to return the pitch and/or shaping tool to its starting position.
3. A process according to Claim 1 or 2, characterised in that control signals for the selection of one of the preselected ratios for the proportional control are derived from the rotation of the displacement and control means.
4. Apparatus for producing helical springs, for example a helical spring winding machine, with a pitch tool (140) and at least one shaping tool (138) which can be displaced mechanically by means of at least one displacement shaft (154), with a first electromotor drive (122) for rollers (130) of a slip-free wire intake (114), and a second drive (124) for each independently displaceable pitch or shaping tool (140 or 138), with an electrically-controlled electromotor (M2'), and with a programme control (274) for one (124) of the two drives 122 and 124), wherein each displacement shaft is provided as a control shaft (154) which introduces into at least one cam gear (164 - 166) of a second drive (124) a torque which is maintained during the control period, and wherein the drive (122) of the wire intake rollers (130) can be controlled and, if required, regulated, characterised in that the first drive (122) has a continuously-running electromotor (M1') and a coupling (238) which can be remotely switched and, if required, controlled throughout, between the said motor and the wire intake rollers (130), and that a tachogenerator (246) is connected between the coupling (238) and the intake rollers (130), and between the said generator and the electromotor (M2') of the second drive (124) a proportional amplifier (244) is connected, for which a plurality of values for the amplification factor can be preselected and selected via the programme control.
5. Apparatus according to Claim 4, for carrying out the process according to Claim 2, characterised in that connected to the amplifier (244) there is a constant current generator (276) which can be switched on by an intake length meter (P2) when the required length of wire has been attained.
6. Apparatus according to Claim 4 or 5, with an auxilliary control shaft (200 which controls and, if required, actuates at least one cutting tool (142), and with a drive (126) for the auxiliary shaft (200) which has a constantly rotating electromotor (M1') and can be controlled, characterised in that the auxiliary control shaft (200) is connected to the electromotor (M1') of the first drive (122) via a coupling (264) which can be remotely switched and, if required, controlled throughout.
7. Apparatus according to one of Claims 4 to 6, for carrying out the process according to Claim 3, characterised in that each displacement and control shaft (154) has a multiple switch (256 - 260) associated with it, the individual switches of which select preselected amplification factors, and can be actuated successively, according to the rotary position of this shaft.
8. Apparatus according to Claim 7, characterised in that the programme control (274) activates and/or suppresses the individual switches according to a programme dependent on the spring and/or productivity in such a way that only specific preselected amplification factors and/or preselected amplification factors at displaced time points are selected.
9. Apparatus according to one of Claims 4 to 8, characterised in that each second drive (124) for a displacement and control shaft (154) has a torque amplifier (240), the electromotor (M2') of this drive being combined with a servo-valve (252) and a hydrn-motor(254)toform a unit.
10. Apparatus according to one of Claims 7 to 9, characterised in that the drive (122) for the wire intake (114) has gearing (222) with a low-speed gear and a high-speed gear which can be changed selectively by actuation of two individual switches in the multiple switch (256 - 260), by a wire-length meter (P1) associated with the wire intake (114).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19792946656 DE2946656C2 (en) | 1979-11-19 | 1979-11-19 | Method and machine for producing coil springs from endless wire by means of spring coils |
| DE19803006913 DE3006913A1 (en) | 1980-02-23 | 1980-02-23 | Helical spring winding machine - with separate drives for slip free wire feed and shaping tools each with electrically controlled motor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| GB2063123A true GB2063123A (en) | 1981-06-03 |
Family
ID=25782050
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8033761A Withdrawn GB2063123A (en) | 1979-11-19 | 1980-10-20 | Process and apparatus for producing helical springs |
Country Status (4)
| Country | Link |
|---|---|
| DD (1) | DD154587A6 (en) |
| FR (1) | FR2469965A2 (en) |
| GB (1) | GB2063123A (en) |
| IT (1) | IT1134306B (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0095027A1 (en) * | 1982-05-24 | 1983-11-30 | Schenker Maschinen AG | Spring winding machine |
| US4873854A (en) * | 1987-10-30 | 1989-10-17 | Sleeper & Hartley Corp. | Computer controlled coiling machine |
| EP0369173A2 (en) * | 1988-10-17 | 1990-05-23 | SLEEPER & HARTLEY CORP. | Computer controlled coiling machine |
| US4934165A (en) * | 1988-10-17 | 1990-06-19 | Sleeper & Hartley Corp. | Computer controlled coiling machine |
| FR2660222A1 (en) * | 1990-03-30 | 1991-10-04 | Tc Hp Sa | Machine for manufacturing helically wound springs |
| US5259226A (en) * | 1992-07-24 | 1993-11-09 | Kabushiki Kaisha Itaya Seisaku Sho | Mechanism for forming spring pitch |
| US6142002A (en) * | 1998-08-21 | 2000-11-07 | Kabushiki Kaisha Itaya Seisaku Sho | Spring manufacturing apparatus and tool selection apparatus |
| US6151942A (en) * | 1998-08-21 | 2000-11-28 | Kabushiki Kaisha Itaya Seisaku Sho | Spring manufacturing apparatus |
| US7984872B2 (en) | 2006-10-03 | 2011-07-26 | Georgia-Pacific Consumer Products Lp | Automated sheet product dispenser |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4030327A (en) * | 1976-06-16 | 1977-06-21 | Torin Corporation | Spring coiling machine with improved drive means |
-
1980
- 1980-10-20 GB GB8033761A patent/GB2063123A/en not_active Withdrawn
- 1980-11-17 IT IT26027/80A patent/IT1134306B/en active
- 1980-11-17 DD DD80225266A patent/DD154587A6/en not_active IP Right Cessation
- 1980-11-17 FR FR8024329A patent/FR2469965A2/en active Granted
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0095027A1 (en) * | 1982-05-24 | 1983-11-30 | Schenker Maschinen AG | Spring winding machine |
| US4873854A (en) * | 1987-10-30 | 1989-10-17 | Sleeper & Hartley Corp. | Computer controlled coiling machine |
| EP0369173A2 (en) * | 1988-10-17 | 1990-05-23 | SLEEPER & HARTLEY CORP. | Computer controlled coiling machine |
| US4934165A (en) * | 1988-10-17 | 1990-06-19 | Sleeper & Hartley Corp. | Computer controlled coiling machine |
| EP0369173A3 (en) * | 1988-10-17 | 1991-01-09 | SLEEPER & HARTLEY CORP. | Computer controlled coiling machine |
| US5117668A (en) * | 1988-10-17 | 1992-06-02 | Sleeper & Hartley Corp. | Computer controlled coiling machine |
| FR2660222A1 (en) * | 1990-03-30 | 1991-10-04 | Tc Hp Sa | Machine for manufacturing helically wound springs |
| US5259226A (en) * | 1992-07-24 | 1993-11-09 | Kabushiki Kaisha Itaya Seisaku Sho | Mechanism for forming spring pitch |
| US6142002A (en) * | 1998-08-21 | 2000-11-07 | Kabushiki Kaisha Itaya Seisaku Sho | Spring manufacturing apparatus and tool selection apparatus |
| US6151942A (en) * | 1998-08-21 | 2000-11-28 | Kabushiki Kaisha Itaya Seisaku Sho | Spring manufacturing apparatus |
| US7984872B2 (en) | 2006-10-03 | 2011-07-26 | Georgia-Pacific Consumer Products Lp | Automated sheet product dispenser |
Also Published As
| Publication number | Publication date |
|---|---|
| DD154587A6 (en) | 1982-04-07 |
| FR2469965B2 (en) | 1982-08-27 |
| IT8026027A0 (en) | 1980-11-17 |
| IT1134306B (en) | 1986-08-13 |
| FR2469965A2 (en) | 1981-05-29 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |