US2145081A - End coil reducing machine - Google Patents

Description

Jan. 24, 1939.

GQGAN 2,145,081

END COIL REDUCING MACHINE Filed Nov. 15, 1937 4 Sheets-Sheet l INVENTOR. JQSEPH G064 Jan. 24, 1939. J. GOGAN END COIL REDUCING MACHINE 4 Sheets-Sheet 2 Filed Nov. 15, 1937 ATTORNEYfi J. GOGAN END COIL REDUCING MACHINE Jan. 24, 1939.

4 Sheets-Sheet 3 INVENTOR. JoJEP/I .Gacmw Filed Nov. 15, 1937 Patented Jan. 24, 1939 I UNITED STATES PATENT OFFICE 10 Claims.

This invention relates to the manufacture of springs and more particularly to a machine for reducing the end convolution of helical wire springs.

In the manufacture of helical springs it has heretpfore been customary to grind the end convolutions to provide the spring ends with flat bearing surfaces lying in planes substantially perpendicular to the spring axis. For various reasons, such squaring of the spring ends by grinding operations is a costly step in the manufacture of coiled springs. It has been found that this grinding operation can be eliminated and a satisfactory seating surface provided in the spring ends by reshaping, preferably reducing in size,

the extreme end convolutions of the spring. The present invention has to do with a machine for carrying out such an end-coil reducing operationr It is, therefore, an object of my invention to provide a novel machine for reshaping or reducing the end convolutions of a helical spring whereby squared ends can be rapidly and economically formed on such springs, without need of grinding operations.

Another object of my invention is to provide a machine, of the type referred to, having cooperating relatively movable die rolls adapted to engage the end coil of a helical spring and to reshape or reduce such end coil by a rolling operation.

Still another object of my invention is to provide a machine, of the type referred to, having a pair of anvil rolls adapted to be engaged by the end coil of a helical spring and a die roll which is movable to engage such end coilat a point between the anvil rolls and to deflect the end coil into the bight between such anvil rolls.

A further object of my invention is to provide a machine, of the type mentioned, in which means is provided for driving the anvil rolls, and cam means driven proportionately with the anvil rolls controls the extent of movement of the die roll into the bight, to thereby determine the shape to be imparted to the end coil.

Still another object of my invention is to provide an improved machine, of the type mentioned,

having control means whereby the movement of the die roll into the bight and the rotation of the anvil rolls can be made to take place in succession.

It is also an object of my invention to provide a machine having cooperating rolls adapted to operate on the end coil of a helical spring and novel work supporting-means adjacent such rolls.

My invention may be further briefly summarized as consisting in certain novel combinations and arrangements of parts hereinafter described and particularly set out in the appended claims.

In the accompanying sheets of drawings,

Fig. 1 is a side elevation, with portions broken 5 away, showing an end-coil reducing machine embodying my invention;

Fig. 2 is a plan view thereof;

Fig. 3 is a front or end View of the machine, with parts broken away, the view being taken looking toward the cooperating rolls;

Fig. 4 is a partial end View, on a larger scale, looking toward the rolls as indicated by line 4& of Fig. 1;

Fig. 5 is a similar partial end View, but showing a spring being acted upon by the rolls;

Fig. 6 is a partial vertical sectional view taken as indicated by line 6-6 of Fig. 1 and looking toward the cooperating rolls;

, Fig. 7 is a partial plan view showing the work holder with a spring thereon and also showing the rolls acting on the end coil of such spring;

Fig. 8 is a detached perspective view showing the die roll and the carrier therefor;

Fig. 9 is a detached perspective view illustrating the construction and operation of the clutch actuating lever;

Fig. 10 is a side view of a helical spring showing the same after the end coils have been reduced by my machine and prior to a flattening or squaring operation to be subsequently performed;

Fig. 11 is an end View thereof; and g Fig. 12 is an end View of a similar spring, but showing the same before the end coils have been reduced.

More detailed reference will now be made to the drawings for the purpose of explaining the construction and operation of my end-coil reducing machine, but before proceeding with such detailed description it should be understood that the drawings are to be regarded as being mainly illustrative and. that the invention may be embodied in various other machines and devices of this character.

' As shown in the drawings, my end-coil reducing machine, is provided with a suitable frame H] which supports the various parts of the machine, including a device ll comprising die and anvil rolls l2 and I3 which cooperate in reshaping or 50 reducing the end coil of a helical spring S by a rolling operation. The frame l0 maybe constructed with an elongated substantially horizontal upper bench or table part M, which is supported by suitable legs l5 and which carries 5 longitudinally spaced blocks or mounts I6, I71, and I8. The block I8 forms a mount for the die device II and for a work holder l8 adjacent thereto, which will be described more in detail hereinafter. The blocks I! and I8 form mounts respectively for bearing units or brackets 28 and 2 I. The block I 6 may also carry an arch 22 which forms a support for the cylinder of a fluid pressure responsive device to be described hereinafter. A brace or bracket 22 carried by the frame and connected with the arch, as by welding, stiffens and reinforces the latter.

The anvil rolls |3 may comprise a pair of disklike rolls which are carried respectively by laterally spaced substantially parallel rotary shafts 23 and 24 and are disposed to lie in a transverse plane extending at substantially right angles to the axes of such shafts. The anvil rolls are provided with peripheral grooves of arcuate cross section in which the end convolution of the spring S engages when the spring is supported in the Work holder IS. The shafts 23 and 24 extend longitudinally of the frame of the machine and have their forward ends journaled in a bearing bracket 25, which is mounted on the block I 6, and their rear ends journaled in the bearing bracket 28. The rear ends of these shafts project beyond the bearing bracket 20 and carry gears 25 and 21 which mesh with a driving pinion 28.

The die roll I?! is preferably of smaller diameter than the anvil rolls l3 and is arranged above and between the latter rolls, that is tosay, in substantially the same transverse plane as the anvil rolls and above the bight or triangular space 29 formed between the latter. This die roll is carried by a shaft 30 which is mounted on a carrier 3|, the latter being shiftable in a vertical plane for moving the die roll toward and away from the anvil rolls. The die roll l2 also has a peripheral groove in which the end coil of the spring engages when this roll is moved toward the anvil rolls. The shaft 38 may be mounted on the carrier 3| by providing the latter with longitudinally spaced bearings 33 and 34 in which such shaft is journaled. The bearing 33 may be formed as a part of a head 35 which is vertically slidable in a guideway 38 formed between the upwardly projecting laterally spaced arms 37 of the bearing bracket 25. The rear end of the carrier 3| may be pivoted on the bearing bracket 2| by means of a transverse pivot 38, which permits vertical swinging movement of the carrier whereby the die roll l2 may be moved to engage the end convolution of the spring, at a point between the anvil rolls 3, and todeflect such end convolution into the bight 29. After the die roll has closed on the spring, the anvil rolls are driven, as will be presently explained, and the end coil of the spring is rolled and thereby reshaped to a convolution R, of smaller diameter than the main portion of the spring.

For actuating the carrier 3|, to move the die roll- |2 toward the anvil rolls, I provide power means, preferably in the form of a. fluid pressure responsive device 39, and for lifting or retracting the carrier and die roll I provide the compression spring 48. The fluid pressure responsive device 39 may comprise a cylinder 4| supported on the arch 22 and a piston 42 operable in such cylinder with a piston rod 43 extending downward therefrom and engaging the carrier 3|. The lower end of the piston rod 43 may be connected with the carrier or, as shown in this instance, may have a rounded end which engages in a correspondingly shaped depression 44 in the top of the carrier. Fluid pressure delivered from a. source to be described hereinafter may be supplied to the top of the cylinder 4| through a pipe connection or conduit 45.

The pinion 28, which, as mentioned above, meshes with the gears 21 for driving the shafts 23 and 24 and the anvil ro-lls carried thereby, is mounted on a longitudinally extending clutch shaft 41 which is adapted to be driven whenever the clutch 48 is actuated or engaged. The shaft 41 extends through the clutch 48 and has its forward and rear ends journaled respectively in the brackets 28 and 2|. The clutch 48 may comprise a clutch gear 49 and a clutch drum 58, both of which are mounted on the shaft 41 between the driving pinion 28 and the bearing bracket 2|. on this shaft and meshes with a main pinion 5| which is carried by a countershaft 5| mounted in bearings 5| and 5|. This countershaft is adapted to be driven from an electric motor 52 through a reductiongearing 53. The clutch drum 50 is keyed to the shaft 41 and is adapted to be intermittently connected with the gear 49 when the anvil rolls |3 are to be driven thereby.

Although any suitale clutch may be employed for connecting the driving pinion 28 with the source of power, the clutch 48 illustrated in this instance is of the type which disengages itself automatically after the pinion 28 has rotated through the desired angular distance, such as one complete revolution. A clutch operating lever 54, pivoted at an intermediate point on a fulcrum shaft 54 cooperates with mechanism in the clutch drum 58 to cause engagement of the clutch whenever the outer end of this lever is swung downwardly about the fulcrum shaft.

For causing engagement of the clutch 48 in timed relation to the shifting of the die roll |2, I may provide a fluid pressure responsive device 55, which cooperates with the outer end of the clutch actuating lever '54. This fluid pressure responsive device may comprise a double acting cylinder 58 and a piston 51 reciprocablyoperable therein. Fluid pressure connections 58 and 59 lead, respectively, into the upper and lower ends of the cylinder 58. A piston rod '68 extends upwardly from the piston 51 and is connected with a vertically movable latch 6|, which is slidable in. a guide bracket 62. The clutch actuating lever 54 has an extension link 63 hinged to its outer end, which carries a roll 64 adapted to be engaged by the finger 65 of the latch during downward movement of the latter. A projection 86 of the lever 54 forms a stopagainst which the link, 63 bears when the latter is pulled downwardly by the latch 8| to thereby cause the lever tofbe swung on its pivot 54 and cause engagement of the clutch whenever the piston 5'! is moved downwardly in its cylinder 56. The link 63 is; adapted to be swung away from the projection 66 by the latch 5|, during upward movement of the latter, and this swinging of the link permits the finger 85 of the latch to pass above the roller 84 preparatory to the next swinging of the lever 54 to cause engagement of the clutch.

For controlling the shifting of the die roll |2 relative to the anvil rolls 13, to thereby determine the shape to be imparted to the end "convolution of the spring S and to center the reduced end convolution R with respect to the spring axis, I provide a pair of cams 68 and 69 on the shafts 23 and 24 of the anvil rolls and a cam follower 70 on the shaft 38"of the die roll 12. These cams are connected with the shafts 23 and The clutch gear 49 rotates freely 24 to be rotated thereby and have a contour such that during the rotation of the anvil rolls the die roll [2 will be permitted to shift downwardly into the bight 29, to deflect and reshape the end coil of the spring, and will be gradually lifted during the rolling operation to cause the reduced coil B, being formed on the end of the spring, to be centered with respect to the spring axis. The cam follower 79 may be in the form of a roller which is mounted on the shaft 39, preferably by means of a self-aligning bearing H. This selfaligning bearing permits rocking of the follower relative to the shaft 30, so that the follower may bear properly against the surfaces of the cams during swinging of the carrier}! on thepivot shaft 38. 7

During the rolling operation the end convolution of the spring S is clamped against the anvil rolls l3 by the die roll l2 and isreshaped to form the end coil R, which is of relatively smaller diameter and is centered on the spring axis. Since the spring is clamped against anvil rolls l3, it will be rotated by the latter during this rolling operation. The spring may be supported in various ways for the reducing operation, but for this purpose I prefer to provide the work holder IS with a cradle or trough-like member 12 which is so disposed that when the spring is received therein, one of its ends will be adjacent the rolls. To facilitate the rotation of the spring during the rolling operation I provide the cradle 12 with rollers 13, which extend longitudinally thereof and on which the spring rests when it is laid in the cradle. During the rolling operation, the spring S may also be subjected to more or less tilting and, to readily permit this movement of the spring, I provide the cradle 12 with a trunion mount comprising the member 74 and the horizontal pivots vl5. After the end convolution at one end of the spring has been reduced by the die rolls, the spring is reversed, that is, shifted end for end, so that the convolution at the other end of the spring can be reduced in a similar manner. To facilitate this shifting of the spring, I provide the trunnion mount 14 with a vertical pivot shaft or stem 15, which extends into a bearing iii of the base plate 11. The horizontal pivots 15 of the trunnion mount 74 and the vertical pivot 16 are located substantially in the transverse midplane of the cradle 12, so that swinging of the cradle on the vertical pivot will reverse the spring ends and swinging of the cradle on the horizontal pivots 15 will permit tilting of the spring regardless of which end thereof is being acted upon by the die rolls.

Because of the pitch of the spring S, it is desirable to provide for adjustment of the work holder so that the cradle 12 may assume a corresponding angular or canted position relative to the axis of the die roll l2, as shown in Fig. '7. When the spring is permitted to lie with its axis in this relatively inclined position, the end convolution will engage properly in the grooves of the die and anvil rolls. For this purpose, I provide the base plate H with slots 18, which permit relative lateral movement between the plate and the mount l6 of the machine frame. If desired, the plate 11 may be provided with a gauge pointer 19 which cooperates with indications 89 on an adjacent part of the frame of the machine for facilitating adjustment of the Work holder to accommodate springs of different pitches.

For locating the spring with respect to the die rolls so that the end convolution will be engaged at the proper point by the roll I2, I provide a gauge stop 82 against which the operator causes the end of the end convolution to abut, as shown in Figs. 5 and '7, when he places the spring on the work holder. The gauge stop 82 may be a suitably shaped bar or other member mounted on the bearing bracket 25 above and to the right of the die roll 12.

Fluid pressure for operating the fluid pressure responsive devices 39 and 55 may be supplied from any suitable source such as a pump 83, which may be connected with the motor 52 to be driven thereby. This pump has a suction connection 84 extending down into a reservoir 86 which contains a supply of oil or other suitable fluid, and has a discharge connection 81 leading to a pressure relief valve 88. A main fluid pressure delivery conduit 89 connects with the conduit 81 through the pressure relief valve and leads to a manually operable control valve 99. Another conduit 9|, leading from the relief valve 88, returns fluid to the reservoir 86 when the pressure at which the relief valve is set, such as a desired maximum working pressure, is exceeded. I

The manually operable control valve 99 may be of any form or construction suitable for controllingthe operation of fluid pressure responsive devices 39 and 55 in the desired manner, for example it may comprise a housing and a valve element movable therein. A pedal 92 may be connected with the movable valve element by linkage 93 to shift the same in the housing, in this instance downward, to cause pressure fluid to be supplied to the cylinder 4| and tothe top of cylinder 55. A tension spring 94 may be arranged to retract the valve element, when the pedal is released, to cause the fluid, including that previously supplied to the cylinder 4| and to the top of cylinder 55, to be returned to the reservoir 88. The valve housing has appropriate ports and openings with which the various conduitsare connected, including an inlet opening with which the pressure fluid supply conduit 89 is connected. A conduit 95 leads from a discharge opening of the valve 98 for supplying pressure fluid to the upper end of the clutch actuating cylinder 58 and through the branch conduit 45 to the upper end of the cylinder 4|. A conduit .96 connected with another discharge opening of the valve leads to the lower end of the clutch actuating cylinder 56. A pressure relief valve 91 disposed in the conduit 96 limits the pressure of the fluid in thelower end of the cylinder 55 to a desired predetermined value. A return conduit 98, connected with the pressure relief Valve 91, returns fluid to the reservoir 36 through the relief manifold 99 whenever the pressure of the fluid in the conduit or in the lower end of the cylinder 56 exceeds the value for which the relief valve is set. Another return conduit I90 connects a discharge or relief opening of the valve 99 with the manifold 99 for returning fluid to the reservoir when the valve element of the valve 90 has been moved to its retracted position by the spring 94.

The pressure relief valves 88 and 91 may be referred to respectively as high pressure and low pressure relief valves because the valve 88 is set to return fluid to the reservoir when a certain desired maximum working pressure is exceeded, and the valve 91 is set at a relatively lower discharge pressure. The setting of the latterrelief valve is preferably such that sufficient back pressure will be maintained in the lower end of the clutch actuating cylinder 56, to prevent downward movement of the piston 5'! until after the piston 42 of the main cylinder 4| has been actuated by the pressure of the fluid. This sequence of operation is desirable so as to cause the die roll |2 to engage the end convolution of the spring and clamp the same against the anvil rolls before the clutch 48 is engaged to cause rotation of the anvil rolls. A check valve 0| located in the conduit 96, between the valve 98 and the relief valve 91, permits pressure fluid to be supplied to the lower end of cylinder 56, but checks the flow of exhaust fluid therefrom so that it must pass through the check valve 91 and the desired back-pressure can be maintained in the lower end of this cylinder.

When a spring has been placed in the cradle 12, with its end coil resting on the anvil rolls l3, the pedal 92 is depressed to shift the movable element of the valve downward, whereby the passages leading to the conduit 96 and the return conduit 00 are closed, and pressure fluid is then supplied to the upper ends of the cylinders 4| and 56 to cause actuation of the carrier 3-| and the clutch 48 in succession, as explained above. Upon completion of the rolling operation, the pedal 92 is released to permit the element of valve 90 to be moved to its retracted position, whereupon the upper end of the main cylinder 4| and the upper end of the clutch actuating cylinder 56 are connected with the reservoir 8-8, through the return conduit I00, so that the fluid pressure previously supplied to these cylinders can be released or exhausted and the carrier 3| and the piston 42 can be lifted by the spring 46 to release the work. With the movable element of the valve 90 in this position, the fluid pressure being supplied through the conduit 89 by the pump enters the lower end of the cylinder '56, through the conduit 96, and lifts the piston 5! and the latch 6| of the actuating means for the clutch 48. The excess fluid over that required to lift the piston 51 is discharged through the pressure relief valve 9! and returns to the reser voir through the conduit -98. Fluid which leaks past the piston 42 of the main cylinder 4-|- may be returned to the reservoir by means of a -suit able drain connection H12.

After the reducing operations have been performed on the ends of the spring S, as explained above, the spring has substantially the shape illustrated in Figs. 10 and 11. An additional operation is then needed to flatten down the reduced end coils to substantially the position represented by the broken line I03.

Although the rolling operations performed by my machine, in reducing the end coils of the spring S, are preferably carried out with the metal of the spring in a heated condition, it should be understood that my invention is not limited to a machine for hot-rolling, but-includes similar machines. adapted for cold-rolling.

From the foregoing description and the accompanying drawings, it will now be readily understood that I have provided a novel machine for reshaping or reducing the end convolution of a helical spring, so that the spring end may be adapted to seat properly without need for a grinding operation thereon, as has heretofore been required. It will be understood further that this end-coil reducing machine embodies a novel arrangement of die rolls, as well as other mechanisms for causing the die rolls to perform the desired operation on the end convolutions of the spring. Inv addition, it will be seen that I have provided novel control means for obtaining the desired sequence of operation of the different mechanisms of the machine, and have also provided a novel work support which permits rotation of the spring during the rolling operation and also permits the spring to be readily reversed or swung end for end.

While I have illustrated and described-my endcoil reducing machine in a somewhat detailed manner, it will be understood, of course, that I do not wish to be limited to the precise construction and arrangements of parts herein disclosed, but regard my invention as including such changes and modifications as do not constitute a departure from the spirit of the invention and the scope of the appended claims.

Having thus described my invention, I claim:

1. In amachine of'the character described, a pair of anvil rolls, means adjacent thereto for rotatably supporting a helical spring with an end convolution thereof engaging said anvil rolls, a die roll shiftable to engage said end convolution between said anvil rolls and adapted to cooperate with the latter for reshaping such end convolution, means for causing such shifting of said die roll comprising a hinged carrier having a shaft on which said die roll is mounted, cam means adapted to be driven proportionately with said anvil rolls, a self-aligning bearing on said shaft and engageable with said cam means for controlling the shifting of said die roll, and means for causing rotation of the anvil rolls and spring.

2. In a machine of the character described, a pair of anvil rolls, means adjacent said rolls for rotatably supporting a coiled spring with an end coil thereof engaging said rolls, a die roll movable to engage said end coil and to deflect the same into the bight between said anvil rolls, means operable to cause rotation of the anvil rolls and spring, and cam means adapted to be driven proportionately to the rotation of said anvil rolls for varying the extent of movement of the die roll into the bight to thereby control the shape to be imparted to said end coil.

3. In a machine of the character described, a pair of rolls adapted to be engaged by the end coil of a helical spring, a die roll adapted to be shifted to engage said end coil and deflect the same into the bight between said anvil rolls, a power device operable to cause such shifting of the die roll, means for driving said anvil rolls including a clutch, and control means operable to cause actuation of said power device and said clutch in succession 4. In a machine of the character described, a pair of spaced rotary shafts, anvil rolls carried by said shafts and having peripheral grooves adapted to receive the end coil of a helical spring, a grooved die roll, a movable carrier for said die roll, power means for actuating said carrier to cause said die roll to deflect said end coil into the bight between said anvil rolls, means for causing rotation of said shafts and anvil rolls, and cam means actuated by said shafts for controlling the extent of movement of said die roll into the bight during such rotation to thereby determine the shape to be imparted to said end coil.

5. In a machine of the character described, a pair of anvil rolls adapted to be engaged by the end coil of a helical spring, a die roll adapted to be shifted to engage said end coil and deflect the same into the bight between said anvil rolls, a power device operable to cause such shifting of the die roll, means for driving said anvil rolls including a clutch, cam means adapted tocontrol the extent of movement of said die roll into the bight during operation of the rolls, and control means operable to cause actuation of said power device and said clutch in succession.

6. In a machine of the character described, a pair of anvil rolls adapted to be engaged by the end coil of a helical spring, a die roll adapted to be shifted to engage said end coil and deflect the same into the bight between said anvil rolls, a fluid pressure responsive device operable to cause such shifting of the die roll, driving means for said rolls including a clutch, a fluid pressure responsive device for actuating said clutch, a source of fluid pressure, and means controlling said fluid pressure responsive devices to cause such shifting of said die roll and actuation ofsaid clutch.

'7. In a machine of the character described, a pair of anvil rolls, a holder for supporting a helical spring with an end coil thereof engaging said rolls, a die roll adapted to be shifted to deflect said end coil into the bight between said anvil rolls, means for causing such shifting of said die roll, and means for driving said anvil rolls, said holder being pivoted to permit relative shifting of the spring.

8. In a machine of the character described, a pair of anvil rolls, a holder for supporting a helical spring with an end coil thereof engaging 'to engage the end coil and cooperate with said anvil rolls in reshaping said end coil, means for driving said anvil rolls, and means pivoting said holder at an intermediate point to permit both tilting of the spring and swinging of the same end for end.

10. In a machine of the character described, a

pair of relatively movable Work engaging devicesadapted to act on a convolution of a helical spring to reshape the same comprising respectively a pair of rolls engageable with the outside of such convolution and a roll engageable with the inside of such convolution at a point between the spaced rolls, fluid pressure responsive means operable to cause such relative movement and to press said devices against said convolution with a predetermined force, and means for causing rotation of said rolls.

JOSEPH GOGAN.

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