US2953799A - Pipe cleaning machine and cable feeding mechanism therefor - Google Patents

Description

Sept. 27, 1960 J. D. ARNOLD PIPE CLEANING MACHINE AND CABLE FEEDING MECHANISM'THEREFOR Filed March 25, 1959 2 Sheets-Sheet v INVENTOR. J/MM/E D. flR/VOLD 14 TTOF/V E Y5 Sept. 27, 1960 xJAD. ARNOLD 2,953,799

I PIPE CLEANING MACHINE AND CABLE FEEbI'Nc MECHANISM THEREFOR Filed March 23, 1959 v A fi 'E t 2 INVENTOR. J/ngy/E D. ARA/01.0

82 H6. 7. ATTORNEYS PIPE CLEANING MACHINE AND CABLE FEEDENG MECHANISM THEREFOR Jimmie D. Arnold, 1986 W. Kentucky Ave., Denver, Colo. Filed Mar. 23, 1959, Ser. No. 801,229 Claims. (61. -1043) This invention relates to pipe cleaning apparatus and, more specifically, to a cable feeding mechanism of a type particularly suited for use in winding flexible cable onto and off of rotaring cage reels.

Underground pipe lines, especially sewer lines, oftentimes become clogged with waste materials and even tree roots that grow through minute fissures or leaks commonly found at the bell joints. Only rarely, however, is it necessary to dig up the line as it is usually possible to open a clean-out tap at some accessible point and insert a suitable tool of a type adapted to remove the obstruction. One of the most popular pipe cleaning machines is that which utilizes a plurality of spring cutters or knives affixed to the end of a flexible cable and fed therein while being rotated. Such a machine usually includes a cagetype reel with the flexible cable wound on the inside thereof in position to be fed axially in and out of the pipe to be cleaned. The reel is operatively connected to a motor which turns the reel and cable wound thereon so that the cutters will sweep the interior of the pipe removing any obstructions therein.

Unfortunately, however, the rotation of the reel merely turns the cable and is of no significance whatsoever in feeding it in either direction, the latter being accomplished by hand. A number of attempts have been made to solve this bothersome problem, but without notable success. Some machines incorporate a drive mechanism separate from the reel drive and an appropriate gear reduces operative to feed the cable on and off the reel. A machine of this type is quite expensive, complicated and difficult to move from place to place thus rendering them somewhat impractical for the ordinary household sewer-cleam ing operations.

Another machine for this purpose depends upon a screw principle for feeding the cable. It includes a fixed element adapted to engage the helically-Wound casing of the cable feeding it in or out of the pipe as it turns in the manner of a bolt within a nut. Here, however, the rate of feed of the cable is so slow as to be entirely impractical for most pipe-cleaning operations. Also, the reel must include a reversible and relatively high-speed drive if the cable is to be fed automatically in both directions. Other problems arise in connection with excessive cable wear, high friction loading and slippage.

Other machines incorporate various and sundry complex and expensive reel-drive and cable-feed mechanisms functioning both separately and in combination with one another. specialized pipe cleaning operations such as scaling, rust removal and polishing, they are of little or no value for general purpose use.

The instant cable-feeding mechanism, on the other hand, overcomes these many deficiencies in the prior art devices for this purpose. First of all, it requires no separate drive as it derives its power from therotational movement of the reel. Secondly, the rate of feed into the pipe is rapid enough to accomplish the cleaning operation in a relatively short time while the rate of withdrawal is even faster. Third, the unit includes a neutral position that is especially useful when stubborn obstructions are encountered.

Also, the feed mechanism is extremely compact and lightweight so that it does not detract appreciably from While several are effective and widely used in the portability of the unit as a whole. The feed is positive in either direction resulting in little cable wear, low friction loading and substantial cutter thrust. In addi= tion, the apparatus described and claimed herein is Ver satile and adaptable to many different types and styles of pipe cleaning equipment.

It is, therefore, the principal object of the present invention to provide a novel and improved pipe cleaning machine which includes an automatic feed mechanism capable of operation in forward, reverse and neutral.

Another object is the provision of a pipe cleaning machine of the type described which is extremely versatile and effective for the purpose intended while requiring only a single operator even to carry it from place to place.

Still another objective of the instant invention is the provision of a flexible cable feed mechanism that is easily adapted for use with a wide variety of types and styles of pipe cleaning machines without requiring extensive or expensive modification thereof. 7

Additional objects are to provide a flexible cable type pipe cleaner and associated feed mechanism that is simple to operate, relatively inexpensive, compact, lightweight, rugged, foolproof and safe to use.

Other objects will be in part apparent and in part pointed out specifically hereinafter in connection with the description of the drawings that follow, and in which:

Figure 1 is a side elevation to an enlarged scale showing the pipe cleaning machine and associated cable feed mechanism of the present invention, portions thereof having been broken away or presented in section for purposes of clarity;

Figure 2 is a section taken along line 2-2 of Figure 1 showing the cage-type cable reel and cable housing;

Figure 3 is a side elevation showing the automatic cable feeding mechanism with the cover removed and portions in section;

Figure 4 is a section taken along line 44 of Figure 3;

Figure 5 is a section taken along line 55 of Figure 3;

Figure 6 is a section taken along line 66 of Figure 3;

Figure 7 is a section taken along line 77 of Figure 3; and,

Figure 8 is a fragmentary section taken along line 88 of Figure 7.

Referring now to the drawings, and in particular to Figures 1 and 2 thereof, it will be seen that the pipe cleaning machine of the present invention includes a frame 10 having a base 12 with uprights 14 at the front and rear ends thereof. At the rear end is mounted a motor 16 and a speed reducer 18 supported above the motor on the uprights. The speed reducer and motor are operatively interconnected by a'belt and pulley drive 20. The low speed shaft 22 of the reducer extends forwardly therefrom where it forms a support for the axle 24 of cagetype cable reel 26 that is journalled thereon of relative rotational movement. The driving connection between the reel and reducer, however, is accomplished by means of L-shaped arm 28 attached to the low speed shaft for rotation therewith and positioned to engage one of the spokes 30 of the reel.

The reel 26 comprises a hub 32 journalled on axle 24 for rotational movement relative thereto. Spokes 30 extend radially from the hub in angularly spaced relation to one another but only on the rear'face of the reel where they are supported by inclined struts 34 in order to leave the front face of the reel open. The spokes and struts cooperate to support a rim 36 having flanges 38 extending inwardly therefrom on the front and rear faces that define a'channel adapted to receive the flexible cable 40 coiled the axis of rotation of the reel where it is journalled for" Patented Sept. 27, 1960' rotation within bearings 44 supported on front uprights 14 as shown. A curved tubular cable guide 46 intersects housing 42 and is adapted to receive the coils of cable from inside the reel and direct them forward axially as they unwind. The cable feed mechanism, indicated in a general way by numeral 48, which forms the principal novel feature of the present invention is attached to housing 42 immediately ahead of curved cable guide 46 for rotation therewith. Control lever 50 of the cable feeding mechanism, on the other hand, does not rotate therewith but is mounted for relative axial movement on a sleeve 52 that slides back and forth along housing 42 which turns inside thereof. The control lever is prevented from turning by handle 54 that depends therefrom and bears against one of the front uprights 14 which forms a stop as the reel turns in the direction of the arrow in Figure 2.

Before proceeding with a detailed explanation of the cable feeding mechanism in connection with the remaining figures of the drawing, it will be well to examine a few other features shown only in Figures 1 and 2. The low speed shaft 22 of the reducer 18 and the arm 28 turn together but may rotate either slower or faster than axle 24. Thus, the reel 26 is turned by arm 28 at the same speed as low speed shaft 22 but at a different speed than axle 24 because of the relative rotational movement possible between the axle and reel hub 32. Now, when the flexible cable 40 is not being fed on or off the reel 26 but is only being turned thereby, the cable, hub, axle, low speed shaft, cable guide, arm and feed mechanism all rotate at substantially the same speed and in the same direction. If, however, the cable is being stripped off the reel either by hand or by means of the cable feeding mechanism of the present invention, the axle, housing, cable guide and feed mechanism all turn at a slower rate of speed than the low speed shaft, arm, reel and hub. On the other hand, if the cable is being wound onto the reel, the opposite is true and the housing, cable guide, axle and feed mechanism all turn faster than the reel, hub, arm and low speed shaft. All of the aforementioned elements of the assembly turn in the same direction and at the same speed determined by the motor and reducer; however, the direction of movement of cable 40 is changed within feed mechanism 48 in a manner to be described presently by moving control lever between the dotted line and full line positions of Figure 1.

Now, with reference to Figures 3 through 8 of the drawings, the details of the cable feeding mechanism 48 will now be described. The feed mechanism is contained within a gear housing that includes front and rear end walls 56 and 58, respectively, sidewalls 60 and 62, and an intermediate wall 64 positioned between the front and rear walls. The cable housing 42 extends through the front and rear walls of the gear housing and is attached thereto so that these elements will rotate as a unit. Openings 66 and 68 are provided in the walls of the cable housing on opposite sides thereof and within the rear portion of the gear housing. A pair of substantially parallel shafts 70 and 72 are journalled for rotation between the sidewalls 60 and 62 of the gear housing on opposite sides of the cable housing and adjacent the openings 66 and 68 therein. Shaft 70 has a feed roller 74 having a concave serrated or toothed edge mounted thereon for rotational movement within opening 68 in the cable housing as shown most clearly in Figures 3, 4 and 7. Shaft 72, on the other hand, carries a idler 76 which rotates therewith and extends into opening 66 in the cable housing in position to engage the cable 40 forcing it into engagement with the concave edge of feed roller 74. Therefore, tuming feed roller clockwise as viewed in Figure 4 will wind cable 40 onto the reel, whereas, turning it counterclockwise will unwind it therefrom.

Referring for the moment to Figure 8 of the drawing, it can be seen that the bearings 78 in which shaft 72 is journalled are attached to the sidewalls 60 and 62 of the gear housing by pins 80 which permit pivotal movement thereof about an axis eccentric to the shaft axis. In other words, the bearings 78, shaft 72 and idler 76 are mounted for swinging movement toward and away from the cable 40 so that it can be released from engagement with feed roller 74 if necessary. The dotted line position of Figure 8 is the released position while the full line position is the engaged one.

The bearings 78, shaft 72 and idler 76 are releasably held in engaged position by a pair of dogs 82 attached to a third shaft 84 mounted between sidewalls 60 and 62 of the gear housing for rotational movement. One end of shaft 84 extends through wall 62 in position to receive crank 86 which is used to rotate the shaft and dogs between engaged and disengaged positions. When turned into engaged position, the dogs function to pivot the bearings 78 and shaft 72 until the idler 76 forces the cable 40 into contact with the feed roller 74. The free end 88 of each dog is curved concavely to receive and lock against the bearings in engaged position as shown by full lines in Figure 8.

InFigures 3 through 7, it will be seen that the shaft 70 also carries a worm wheel 90 that meshes with a worm 92 mounted on a shaft 94 which is journalled for rotation between the front and rear walls of the gear housing and to the rear of intermediate wall 64. In addition to worm 92, shaft 94 carries a spur gear 96 mounted adjacent intermediate wall 64 but in the front portion of the gear housing. This spur gear 96 meshes with a stationary gear or clutch-forming means 98 carried for axial movement relative to cable housing 42 on sleeve 52.

When the control lever 50, sleeve 52 and stationary gear 98 are shifted all the way to the rear as indicated by full lines in Figure 3, the cable feeding mechanism is in reverse which winds the cable 40 onto the reel in the following manner. As aforementioned, gear 98 and sleeve 52 do not rotate by reason of the control lever 50 engaging in the front uprights of the frame. Therefore, if

.the stationary gear is meshed with the spur gear 96 and the gear housing is turning counter-clockwise as viewed in Figure 6, shaft 94 and worm 92 will also be turning counter-clockwise as seen in Figure 7. Clockwise rotation of the worm as viewed from the rear end of shaft 94 will produce clockwise rotation of shaft 70 and worm wheel 90 in Figures 4 and 5 causing the feed roller 74 to turn in the same direction and push the cable back through guide tube 46 winding it onto the reel. Of course, shaft 70 and idler 76 will also be turning counter-clockwise as viewed in Figure 4 when the cable is drawn rearwardly across the surface of the idler.

Now, to change the direction of cable feed from rcverse to forward, it is only necessary to slide sleeve 52 ahead by means of control lever 50 until stationary gear 98 occupies the dotted line position of Figure 3. In forward position, stationary gear 98 is disengaged from spur gear 96 but is meshed with a second spur gear 100 mounted on a stub shaft 102 that is journalled for rotation between intermediate wall 64 and front wall 56 of the gear housing. Stub shaft 102 also includes a pinion 104 that meshes directly with spur gear 96 (Figures 5 and 6) in all positions of the stationary gear 98; however, when the stationary gear is in the rear or reverse position indicated by full lines in Figure 3, the pinion 104, shaft 102 and spur gear 100 are functionally inactive although they turn by reason of their connection with spur gear 94. On the other hand, when the stationary gear 98 is in the forward position indicated by dotted lines in Figure 3, elements 100, 102 and 104 cooperate therewith to reverse the direction of rotation of spur gear 96 in the manner which will now be explained.

Here again, the gear housing and associate elements will be turning counter-clockwise as viewed in Figure 6. Now, however, stationary gear 98 is meshed with spur gear 100 instead of gear 96 which means that gear 100, stub shaft 102 and pinion 104 are also going to be turning counter-clockwise while gear 96 is turning clockwise by virtue of its connection with the pinion. Shaft 94 will turn the worm clockwise in Figure 7 and the worm wheel 90 counter-clockwise in Figure 5. As the worm wheel 90 turns counter-clockwise in Figure 5, it will turn shaft 70 and feed roller 74 counter-clockwise in Figure 4 feeding the cable forwardly out the end of cable housing 42 and unwinding it from the reel.

It is also worthy of note that the pinion 104 is preferably substantially smaller than spur gear 96; whereas, gears 94, 96 and 100 are substantially the same size. In other words, there is about a 2:1 reduction in speed between forward and reverse which allows the cable to be fed into the pipe slowly and withdrawn quickly when there is no load thereon.

Finally, in Figure 3 of the drawings, it will be seen that the spur gears 96 and 100 are spaced apart axially a distance somewhat greater than the thickness of stationary gear 98. This, of course, permits the stationary gear to be shifted into an intermediate or neutral position between gears 96 and 100 where the feed mechanism becomes inoperative functionally to move the cable in either direction. Such a neutral position has not been illustrated but would correspond with a position wherein the control lever was located between the full and dotted line representations of Figures 1 and 3.

Having thus described the several useful and novel features of the pipe cleaning apparatus and associated cable feeding mechanism of the present invention, it will be apparent that the many worthwhile objectives for which they were designated have been achieved. Although but a single specific embodiment of the invention has been illustrated and described in connection with the accompanying drawings, I realize that certain changes and modifications therein may occur to those skilled in the art within the broad teaching hereof; hence, it is my intention that the scope of protection afforded hereby shall be limited only insofar as said limitations are expressly set forth in the appended claims.

What is claimed is:

1. In a cable-feeding machine, a frame, a substantially straight tubular housing mounted on the frame for rotational movement about an axis extending from front to rear thereof, said housing having at least one opening in wall thereof intermediate the front and rear ends, an open-faced cage-type reel mounted on the rear end of the tubular housing for coaxial rotational movement relative thereto, drive means operatively connected to the reel for rotating same in one direction, a curved tubular element having the front end thereof intersecting the tubular housing substantially axially ahead of the reel and the rear end opening substantially tangentially inside said reel in opposed relation to the direction of rotation thereof, a length of flexible cable coiled inside the reel with a free end thereof threaded forwardly through the curved tubular element and straight tubular housing to form a driving connection between the latter and said reel, and cable feeding means carried by the tubular housing ahead of the curved element operative upon actuation to feed the cable into and out of the reel, said feeding means comprising, a gear housing mounted on the tubular housing for rotational movement therewith, a first shaft journalled for rotation within the gear housing adjacent the opening in the tubular housing, a feed roller mounted on the first shaft and positioned to engage the cable through the opening in the tubular housing, a clutch-forming means journalled on the tubular housing for axial movement relative thereto between a first operative position and a second operative position, first gear train means operatively interconnecting the first shaft with the clutch-forming means when in first operative position and adapted to turn the feed roller in a direction to wind the cable into the reel, and second gear train means operatively interconnecting the first gear train means with the clutch-forming means when in second 6 operative position and adapted to reverse the direction of rotation of said first gear train means and feed roller to unwind the cable from inside the reel.

2. The machine as set forth in claim 1 in which the first gear train means comprises, a second shaft journalled for rotation in the gear housing with the axis of rotation thereof located in spaced substantially parallel relation to the axis of rotation of the tubular housing and in spaced substantially normal relation to the axis of rotation of the first shaft, a worm and worm wheel operatively interconnecting the first and second shafts, and a spur gear mounted on the second shaft in position to co-act with the clutch-forming means when in its first operative position.

3. The machine as set forth in claim 1 in which the tubular housing includes two openings arranged in opposed relation to one another, a third shaft is journalled for rotation in the gear housing in spaced substantially parallel relation to the first shaft and adjacent the second opening in the tubular housing, and an idler is mounted on the third shaft in position to engage the cable through the second opening in the tubular housing holding said cable in engagement with the feed roller.

4. The machine as set forth in claim 1 in which the feed roller has a continuous concave groove around the peripheral edge thereof adapted to receive the cylindrical surface of the cable.

5. The machine as set forth in claim 2 in which the second gear train means comprises a fourth shaft journalled for rotational movement in the gear housing in spaced substantially parallel relation to the second shaft, a pinion meshed with the spur gear mounted on the second shaft, and a second spur gear mounted on the fourth shaft in position to co-act with the clutch-forming means when located in its second operative position.

6. The machine as set forth in claim 2 is which the clutch-forming means comprises a third spur gear meshed with the spur gear of the first gear train means in at least the first operative position of the clutch-forming means, and means operative in the first operative position of the clutch-forming means to hold the third spur gear in stationary position while the spur gear of the first gear train means turns therearound to form a driving connection.

7. The machine as set forth in claim 3 in which the third shaft is attached to the gear housing for pivotal movement about an axis lying in spaced substantially parallel relation to the axis of rotation thereof between a first position in which the idler is engaged with the cable and a second position wherein said idler is disengaged therefrom.

8. The machine as set forth in claim 5 in which the clutch-forming means comprises a third spur gear meshed with the second spur gear of the second gear train means in at least the second operative position of the clutchforming means, and means operative in the second operative position of the clutch-forming means to hold the third spur gear in stationary position while the second spur gear of the second gear train means turns therearound to form a driving connection.

9. The machine as set forth in claim 5 in which the ratio of the size of the gears in the second gear train relative to one another are selected such that the second shaft turns more slowly with the clutch-forming means in its second operative position than in its first operative position.

10. The machine as set forth in claim 7 in which means comprising a latch is mounted on the gear housing operative upon actuation to releasably lock the third shaft in first position.

Rolland Dec. 21, 1937 I

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