US2669278A - Tube corrugating machine - Google Patents

Description

Patented Feb. 16, 1954 I 2,669,278 TUBE CORRUGATING MACHINE Raymond 0. Andersen, Lombard, 111., assignor to Corporation, Maywood,

Chicago Metal Hose 11]., a corporation of II linois Application March s, 1948, swarm. 13,412

3 Claims. 153-73) This invention relates to apparatus and methods for making corrugated tubing, and concerns particularly means and methods for making tubing of the one piece annularly corrugated type.

It is an object of the invention to provide improved methods and apparatus for making annularly corrugated tubing. More specifically stated it is an objectof the invention to provide improved means and methods for making annularly corrugated tubing wherein a preformed cylindrical blank is first annularly grooved at predetermined spaced intervals, the tubing wall sections between the grooves being thereafter collapsed or compressed to form the juxtaposed flexible annular corrugations.

. One of the principal objects of the invention is to provide improved means and methods for effecting the annular grooving operations, which are faster and more reliable in operation, and impart a more uniform and accurately controlled contour to the tubing walls.

A further object of the invention is to provide, in tube making apparatus of the type defined, improved means and methods for correlating and controlling the grooving and tube wall compressing apparatus, and for effecting the continuous operation thereof to provide the finished flexible tubing wall section.

Various other objects, advantages and features of the invention will be apparent from the following specification, when taken in connection with the accompanying drawings, wherein a preferred embodiment is set forth for purposes of illustration.

In the drawings, wherein like reference numerals refer to like parts throughout:

Fig. 1 is a side elevation of a tube making apparatus constructed in accordance with and embodying the principles of the invention, in accordance with one preferred embodiment thereof; certain parts being broken away or illustrated in section to show the details ofthe apparatus;

Fig. 2 is a plan view of the structure of Fig. 1 with certain parts broken away and sectioned for clarity of illustration;

Fig. 3 is a transverse section of a part of the tube wall compressing apparatus, taken as indi cated by the line 33 of Fig. 1;

Fig. 4 is a transverse sectional view of another part of the tube wall compressing apparatus, taken as indicated by the line 4-4 of Fig. 1;

Fig. 5 is an enlarged longitudinal sectional view of the grooving apparatus;

Fig. 61s a sectional detail view of one of the grooving slides and associated parts, taken as indicated by the line 5 -'6'0f Fig. 5; I

Fig. 7 is an exploded view of certain of the parts of the grooving slide assembly;

Fig. 8 is a front view of the support plate of the grooving apparatus, showing several of the grooving fingers;

Fig. 9 is an illustrative view, more particularly 2 showing the correlative action of the grooving and wall compressing mechanisms;

Figs. 10-14 are illustrative views showing successive steps in the operation of the parts of Fig. 9; and

Fig. 15 is a view of the completed tubing as made by the apparatus of the invention.

Referring more particularly to the drawings, and first to Figs. 1 and 2, the tube making apparatus shown comprises a grooving mechanism,

generally indicated by numeral l0, and a mechanism l2 for compressing or collapsing the wall sections of the grooved tubing, said mechanisms being carried by a main base or frame [4 of the machine.

The mechanism for compressing or collapsing the tubing wall sections, after the grooving operations, is best shown in Figs. 1-4 and will be first described. As indicated in Fig. 9, the function of this mechanism is to compress the wall sections of the previously grooved tubing so as to provide deep and closely spaced flexible annular convolutions. Referring to Figs. 1-4, it will be seen that the compressin apparatus comprises two sets of jaws as indicated respectively at |6l8 and 20- 22. Jaws l6--|8 are shiftable relative to each other transversely of the tubing axis, so as to clampthe tubing convolutions; whereas the jaws 20-22 are shiftable both transversely and axially of the tubing axis to effect a clamping of the tubing and also the compressing thereof in conjunction with the clamping or holding action of the jaws l6-l8.

Referring to Figs. 1 and 3, it will be seen that the jaws l6 and I8 are transversely shiftable along trackways '24 formed in the frame of the machine, there being a pair of compression springs 26 and 28 acting between the jaws to normally urge them into separated position. To effect the inward or gripping movement of the jaws onto the tubing, they are provided with rollers as indicated at 30 and 32 cooperable with and actuated by cams as indicated at 34 and 36. The cam 34 is fixed to a shaft 38 journalled in the frame of the machine on one side of the tubing axis, whereas the cam 36 is secured to a shaft 40 similarly journalled on the machine frame on the opposite side of the tubing axis.

It will be seen that upon rotation of the shafts 38 and 40 a predetermined timed reciprocation willbe imparted to the jaws I3 and I8, against the action of the compression springs, whereby to effect the sequential clamping and unclamping of the convolutions of the tubing, indicated at 42, which is arranged for central disposition between the jaw members.

The structure and action of the jaws 23-22 will 'be best understood by reference to Figs. 1, 2 and 4. As shown in Figs. 1 and 4, the jaws 20 and 22 are transversely reciprocable along tracks as indicated at 44, these tracks being formed in a rectangular frame structure 46 disposed in a plane-transversely of the tubing axis.

The frame 46 .isinturn reciprocable longitudinally of the tubing axis along tracks 48 formed in the main frame of the machine. The jaws 20 and 22 are normally urged away from each other by means of a pair of compression springs 60 and 52, Fig. 4, whereas the rectangular frame 40 is normally urged axially of the tubing away from the clamping jaws Iii-I8 by a set of compression springs 54, there being four such springs provided in the particular embodiment shown.

To effect the clamping. movement of the jaws 20 and 22 relatively toward each other, against the action of the compression springs 50-5-2, shafts 38 and 40 are provided respectively with a pair of cams 56 and 58 engageable with abutment rollers carried by the jaws and operable to effect the shifting of the jaws toward each other in a similar manner as previously described in reference to the jaws I'6--I8. Toefiect the. reciprocation of the frame 40, axially of the tubing, the frame is provided at its opposite sides with a pair of yoke projections 60 which, as best shown in Fig. 1, are connected respectively to the upper ends of pivot arms 52 pivotally mounted at their lower ends upon the main frame of the machine. The arms 62 carry rollers adapted for engagement, respectively, by cams 64 and 66 fixed to a cross shaft 68 extending transversely of the tubing slightly below the tubing axis.

It will be seen that .by reason of the structures provided, upon operation of the shafts 3'8 and 40, the earns 56 and 58 will effect the periodic opening and closing of the jaws 20-42, whereas operation of the shaft 68 will cause the cams 6'4 and 66 to effect axial reciprocation of the frame 46 andv of the jaws 20-42 carried thereby, whereby to impart both transverse and axial reciprocative movements to the jaw members. The sequential operating steps of. the jaws, in effecting the collapsing of the tubing wall sections, will be later described with reference to Figs. 10-14.

It will be noted that the cams 56 and 58 are sufiiciently wide so that operating contact with the jaw rollers is maintained at all times during the reciprocation of the frame 46.

The structures of the grooving mechanism are shown in Figs. 1, 2, 5, 6, '7 and 8. The main frame of the machine carries a housing I within which is journalled a drive sleeve I2, Fig. by means of a pair of roller bearings 14 and I8. Means is provided for driving; the sleeve comprising a worm gear 13, secured thereto by means of a lock nut I9 and. arranged to bedriven by a worm 80. This worm is driven by a shaft 8-2, Fig. 2, powered from an electric motor 84, there being a speed variator mechanism as indicated at 86 for controlling the speed of operation of the drive.

Referring further to Fig. 5, it will be seen that a stationary sleeve 88 lies within the rotatable drive sleeve 12, this stationary sleeve being adjustably held in fixed. position. by threaded engagement with a disc member 90, carried by the housing I0, and a lock nut 92.. The forward or leftward end of the rotatable drive sleeve 12 has a bushing 94 press fitted therein, the bushing being rotatable upon the forward. end of the stationary sleeve 88. The stationary sleeve interiorly of its forward end carries a collar or bushing 96 accurately sized tothe diameter of the tubing blank and within which the tubing blank is longitudinally slidable with a close slid ing fit.

p The forward endof further secured thereto the hub portion 98 of a head plate I00 arranged to carry a series of slides I02, there being six such slides, Fig. 8, in

"the particular embodiment illustrated, in three symmetrically disposed pairs.

A sleeve I04, Fig. 5, is mounted upon the plate hub 90, said sleeve being arranged for rotation with the hub and for limited axial movement in respect thereto between the limits indicated by the full and dotted lines let. A collar I08 is rotatably carried on the sleeve 904 by means of a pair of anti-friction bearings H0 and I I2, said collar having a pair of oppositely projecting pins as indicated at H4- and H6. The pins H4 and III; engage, respectively, within slots formed in a pair of yoke arms H8 and I20. These arms which are bowed to collectively embrace the collar I33, are pivotally mounted at one end upon the frame of the machine, as indicated at I22, and secured together at their opposite ends for movement as a unit, by bolts I24. The ends of the arms, adjacent the bolts I24, rotatably carry a roller member the function of which will be presently described. It will be seen that by reason of the connections provided, as the arms H8 and IEt are pivotally actuated, for example by the roller I25, corresponding motion will be imparted to the sleeve I34 longitudinally of the tubing axis, the sleeve at the same time being freely rotatable for movement with the main drive sleeve M.

The axial movements of the sleeve I04 are employed to control the movements of the grooving slides I02, the latter being radially shiitable onthe face plate I00 to eiiect the tube grooving operation. More particularly, referring to Figs. 5, 6, 'Z and 8, it will be seen that the face plate is provided, at circumfercntially spaced interval with pairs of ears I28 forming the pivot mounting means for a plurality of rocker levers 23%, there being one lever for each grooving slide. One arm of the levers I30 projects radially inwardly for engagement within a recess of the sleeve IM, whereas the other arm of the lever projects forwardly to provide a lug or extension member I32. Each lug I32 carries a screw I34 held in adjusted position by mean of a lock nut I36, the end of the screw being adapted to bear against a hardened abutment piece I28 carried in the upperend of the grooving slide I02. Each slide is guided for movement radially of the face plate by means of a pair of guide members I40 suitably bolted to the plate by screws I42. A bridge piece HM is adjustably carried by the innermost screws I42, and a compression spring I46 reacts between this bridge piece and a projecting portion I48 of the grooving slide so as to normally hold the slide radially outwardly of the face plate. The inner end of each grooving slide carries a grooving tool- I50 replaceably held in position by means of a screw I52.

It will be seen that by reason or" the connectionsprovided, as the sleeve I04 is shifted longitudinally of the tubing axis, simultaneous movement will be imparted to the several grooving slides I02 and the grooving tools carried thereby, radially oi the face plate structure, the several rocker levers I30 effecting movement of the slides against the action of the compression springs I453. It will be seen that the spring tension may be adjusted by the adjustable positioning of the bridge members I44, and that the position of each slide is readily independently adjusted by the adjustment of the screws I34 and the drive sleeve]: has; their associated loch nuts I36.

Particular attention is directed to the action of the several grooving tools, in effecting the grooving of the tubing blank. It will 'be seen that the inner end of each tool is provided with a curved spinning face lat which engages the tubing and spins a groove therein as the several slides I02 are actuated radially inwardly. The provision of a plurality of slides and tools, simultaneously actuated and in balanced disposition, produces a balanced structure permitting high speed operation of the face plate I89, whereby to facilitate a rapid grooving operation. Furthermore, the several simultaneously operating grooving or spinning tools impart a uniform contour to the grooves I88 formed in the tubing, even though the grooving slides may be reeiprocated relatively rapidly to produce a maximum number of grooving operations for any given time interval of machine operation. This uniform contour, thus imparted to the grooves I56, facilitates the proper placement and operation of the jaws Iii-I8 and 2823, forming a part of the tube wall collapsing mechanism previously described. The degree of penetration of the spinning tools into the tubing blank may be readily controlled by the screws I 34, as previously described, and substitution of proper spinning tools in accordance with the requirement of a particular tubing blank may be readily effected by means of the screws I52 without replacement or substitution of the slide structures.

Means is provided for effecting the timed actuation of the grooving tools in relation to the operation of the clamping jaws Iii-I8 and 20--22 of the tube wall compressing mechanism I2, the jaws 20-22 thus acting as means for feeding the tubing blank in respect to the spinning mechanism I0. Referring to Figs. 1 and 2, it will be seen that there is provided a drive motor I58 operating through a change speed gearing or speed variator mechanism I60 to actuate the helical drive gear I62. This gear meshes with and drives a helicoid gear lt l secured to the shaft of the tube wall compressin'g mechanism, previously described. Shaft 40 is interconnected with cross shaft 68 by means of a pair of helicoid gears I66, and shaft 68 is in turn interconnected with the cam shaft 38 by means of helicoid gears as indicated at I68. Cam shaft 40 is extended past the main drive gear and carries on its end a bevel gear I10 arranged to mesh with and drive a bevel gear I12 fixed to a stub shaft which carries a cam I'M engageable with and arranged to actuate the roller I 26 carried by the arms H8 and I20 of the grooving mechanism, previously described. By reason of the connections thus provided the several actuating earns 34, 36, 86, 58, 54, 66 and I14 are all operated in synchronized relation so that the grooving and wall collapsing mechanisms may be continuously operable upon a common tubing blank.

The action of the tools will be best understood by reference to Figs. 9 and 1014. Referring to Fig. 9, it will be seen that the several jaws of the tube compressing mechanism carry tools as indicated at I16 and I19, shaped to conform to the desired contours of the tubing convolutions. Referring to Figs. 10-14, in Fig. 10 the tools I15 and I18 are shown in engagement with the tubing, and the spinning tool I50 retracted. In Fig. 11 the tool I16 is holding the tubing while the tool I18 is-retracted and moving rightwardly so as to engage into a new tubing groove I56b. During this interval of operation the spinning tool I50 moves inwardly and eifects the spinning of the tubing groove.

In Fig. 12 the tool I18 has reached its new position and the tool I50 has been retracted. In Fig. 13 the tool I16 has been retracted and the feeding tool I18 has moved partially toward the left, so as to bring a new tubing groove as indicated at I56a into position. in alignment with the tool I16.

In Fig. 14 the tool I16 has moved into engagement with the tubing, after which the tool I18 continues its motion to the left, to the position of Fig. 10, to collapse the tubing wall and complete the cycle of operation.

The completed tubing blank is shown in Fig. 15. As will be understood, the formed tubing may be used in longer lengths, as hose, or in shorter lengths, as bellows, or otherwise as desired to provide a fluid-tight flexible tubing structure.

It is obvious that various changes may be made in the specific embodiments set forth without departing from the spirit of the invention. The invention is accordingly not to be limited to the particular embodiments shown and described, but only as indicated in the following claims.

The invention is hereby claimed as follows:

1. Apparatus for making flexible metal tubing and comprising a rotatable tool support, a plurality of grooving tools mounted on the tool support with the operative ends thereof disposed adjacent and peripherally around the space in which a tubular work piece is positioned, means for supporting the work piece, said means including a fixed collar adjacent the grooving tools and engaging the workpiece with a close sliding fit, and said means acting to prevent material rotation of the work piece but permitting positive axial feeding of the work piece through said collar; means for simultaneously reciprocating the grooving tools to progressively engage the work piece for effecting the complete grooving thereof to a predetermined depth upon each stroke of the grooving tools into engagement with the tubular work piece, and means independent of the grooving tools and spaced therefrom for compressing the work piece wall sections between adjacent grooves and including an axially reciprocable compressing member effective to feed the work piece axially of the space within the operative ends of the grooving tools upon their withdrawal from engagement with the work piece.

2. Apparatus as claimed in claim 1, wherein the rotating means for the tool support includes a hollow rotatable shaft within which said collar is positioned adjacent the operative ends of the grooving tools.

3. Apparatus as claimed in claim 1, wherein the grooving tools are each individually adjustable relative to the work support.

RAYMOND C. ANDERSEN.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,605,194 Kopf Nov. 2, 1926 1,750,784 Petersen Mar. 18, 1930 1,810,342 Bulger June 16, 1931 1,982,369 Brinkman Nov. 27, 1934 2,027,018 Brinkman Jan. '1, 1936 2,092,873 Brinkman Sept. 14, 1937 2,486,830 Farrar et al Nov. 1, 1949 FOREIGN PATENTS Number Country Date 14,944 Great Britain 1887

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