US2582987A - Power winch or hoist - Google Patents

Description

Jan. 22, 1952 D. HAGENBooK 2,582,987

POWER WINCH 0R HoIsT i Filed Jan. 26, 1950 5 Sheets-Sheet l l f m 4 N -o Si N 6U E Q N l L I1 N u lllllll wa Q ia Qu M l V m 1 r kl j u) L N @S u) `1 r l A e l I N VEN TOR.

rronA/EY Jan. 22, 1952 D, HAGENBOOK 2,582,987

u POWER WINCH OR HOIST FiledJan. 26, 1950 5 Sheets-Sheet 2 1N V EN TOR.

Hag enboo @Mig ATTORNEY Jan. 22, 1952 D. HAGENBooK 2,582,987

` v POWER WINCH 0R HoIsT Filed Jan. 2e, 195o S sheets-sheet 3 1N VEN TOR.

ATTORA/Ey Jan. 22, 1952 l.. D. HAGENBooK 2,582,987

POWER WINCH 0R HoIsT Filed Jan. 26, 195o 5 sheets-sheet 4 TTORNEY L. D. HAGENBOQK POWER WINCH 0R HoIsT Jan. 22, 1952 5 Sheets-Sheet 5 Filed Jan. 26, 1950` IN V EN TOR.

Patented jan. 22, 1952 UNITED STATES PATENT OFFICE POWER WINCH on. Hols'r Loy D.- Hag'enbook, Chicago, Ill., assignor to' Goodman Manufacturing Company, Chicago, Ill., a corporation of Illinois a Application January 26, 1950, Serial No.- 140,673

Claims.

This invention relates to improvements in power winches or hoists.

Among the objects of the invention is to provide means for preventing shock loads on the cable or rope wound on the drum of the winch.

A further object is to provide means for maintaining the cable under yielding tension between predetermined loads.

Still another object is to provide a simple and effective means for driving the drum through a spring, together with means for preloading the spring at a predetermined value so as to provide an unyielding pull on the cable until the preloaded value is exceeded.

Another object is to provide means for automatically relieving the driving torque on the drum when the load reaches a predetermined value.

Other objects of the invention will appear from time to time as the following description proceeds:

The invention may best be understood by reference to the accompanying drawings, in which:

Figure l is a plan view in part diagrammatic showing a pair of power Winches or hoists constructed in accordance with my invention, as used in a loading operation in a mine for swiveling the loading end of a reciprocable conveyor trough to various laterally adjusted positions in a mine room or entry;

Figure 2 is an enlarged side view, as seen along line 2 2 of Fig. 3, of one of the power Winches shown in Figure l with parts of the gear casing removed to show details of the drive gearing;

Figure 3 is an end view of one of the Winches,

taken along the line 3--3 of Fig. 1, with parts broken away to show the details of the gearing and brake mechanism thereof;

Figure 4 is a detailed view of the brake mechanism taken on a slightly larger scale than Figure 3;

Figure 5 is an enlarged detailed section taken generally along the axis of the winding drum;

Figure 6 is a detailed section taken generally along line 6--6 of Figure 5 and showing the drive spring tension adjusting mechanism in position wherein the drive spring is fully unwound;

Figure 7 is a View similar to Figure 6 in which the drive spring adjusting mechanism has been set to preload the drive spring by adjusting one end thereof through an angle of approximately 221/2 degrees from its fully unwound position shown in Figure 6;

Figure 8 is a view 'similar to the preceding figures but in which the drive spring adjusting Figure l0 is a detailed section taken on line Iii-i0 of Figure 5 showing part of the cam means for automatically disconnecting the drive between the winch motor and the drum when the cable reaches a predetermined value considerably in excess of the preloaded tension on the drive spring; and

Figure 11 is a detailed longitudinal section of the driving end of the drum showing the cam means in clutch disengaging position corresponding to that shown in Figure 10.

Referring now to details of the embodiment of my invention illustrated in the drawings, Figure l illustrates an especially effective manner in which my improved form of power winch or hoist may be utilized for controlling the lateral swinging movement of a reciprocating loading conveyor in a, mine.

in illustrative form of application shown herein, a reciprocating conveyor is indicated at I0, having a trough section II at its forward end with Ya swiveled connection I2. An extensible loading head or trough section I3 is telescopicaily mounted with respect to the forward trough section II, with a widened shovel Ill at its front end for loading material on the conveyor. The main trough section II is driven by a suitable shaker drive (not shown) usually disposed at the remote or unloading end of said conveyor.

The reciprocable loading conveyor, with its swivel I2 and extensible loading section i3, as shown herein, are all old and well known in the art so need not be described in greater detail.

Referring now more particularly to the power winch which forms the principal subject matter of the present invention, a pair of such power Winches l5, I5, each constructed in accordance with my invention, are provided for controlling the lateral swiveling movement of the loading head I3 about the swivel connection I2. Said Winches are usually anchored closely adjacent the side walls or ribs IE of the room or entry which is being mined out, along a working face I'I at the end of said room or entry. The means for'anchoring the Winches are more fully disclosed and claimed in my copending application, Serial Number 135,890, filed December 30, 1949.

Each power winch I5 includes a base I8 with a suitable horizontal plate I9, on which the several parts of the winch are supported. A winding drum, indicated generally at 20, is rotatably mounted between upright spaced supports 2| and 22 on a shaft 23 iixed at opposite ends to said supports. A drive sprocket 25, driven from an electric motor 26 through suitable drive mechanism to be hereinafter more fully described, is keyed or otherwise secured to a hub 21 journalled at the right end of the shaft 23, as seen in Figure 5. The hub 21 is formed integrally with an enlarged cup-shaped drive member 30, including a radial web 3l and a flanged periphery 32 extending toward the left end of the drum, as seen in Figure 5. A plurality of clutch rings, here two in number and indicated at 33, 33a, have serrated outer edges engaged in corresponding notches 34 formed about the inner face of the flanged periphery 32 of drive member 30 adjacent its inner end. These clutch rings are interleaved with similar clutch rings 35, 35a having their inner peripheries serrated and engaged with corresponding notches 38 formed about a clutch backing ring 40, which is keyed or otherwise xed on a second hub member 4|, which is integral with an end plate 41.

The hub member 4| and said end plate 41 are ljournalled on the shaft 23 independent of the Erst-named hub 21. The hub 4| has a reduced portion 42 which extends into the cup-shaped drive member and has a radially flanged collar 45 secured thereon, as by threads 46. The flanged collar 45 retains an abutment 45a for a plurality of compression springs 48, 48, the opposite ends of which engage the proximate clutch plate 33 tending to force the clutch plates 33 and 33a into frictional driving engagement with the interleaved clutch plates 35, a carried on the clutch collar 40. The backing ring includes a radially extending ring portion 49 forming a stop member for the adjacent clutch plate 35.

The clutch springs 48 are normally under compression tending to maintain the clutch in operative engagement at all times, excepting when the clutch is positively disengaged through operation of a plurality of rocking arms 50 which extend radially through and are pivotally mounted on f `outer ends of the arms 50 have rollers 53 normally engaging a cam ring 54 secured within an enlarged bore 54a in the housing 65. The operation of the rocking arms 50 and the cam ring for .disconnecting the clutch will presently be more fully described.

The main cable carrying body of the drum 20 consists of a hollow cylindrical housing 55, herein provided with a spirally grooved outer surface for spooling-engagement by a cable 51. One end of said cable carrying body is rotatably mounted on the shaft 23 as by an end plate 58 secured to the drum periphery as by bolts 59 and having an anti-friction bearing 60 engaged with a reduced end portion 5| of the shaft 23. The opposite end of the drum 20 has a hollow cylindrical housing integral with, but of greater diameter than, the cable carrying housing 55. This enlarged housing 65 forms an enclosure for the clutch mechanism previously described, and is rotatably supported at its outer end relative to the `shaft 4 23 by an end plate 66 rotatably supported on the outer periphery of hub 01 of the drive sprocket 25 by an anti-friction bearing 61a. The end plate 55 may be detachably connected to the enlarged housing 85 of the drum as by bolts 69.

The drum 20 is connected for yieldable driving engagement from the driven hub member 4| and end plate 41 through a helical spring 10 having its outer end abutting an end block 12 fixed to the end plate 58 as by a bolt 1|. The opposite end of the spring 10 abuts a similar end block 15 connected by a bolt 16 to the end plate 41.

As a preferred arrangement, the drum is driven through the clutch mechanism in a direction which tends to unwind or open the spring 10 under driving torque; but, for some purposes, the spring can be arranged for contraction instead of expansion under driving torque.

Means are provided for preloading the initial tension of the spring 10 as follows:

A tension adjusting ring is rotatably mounted at the inner end of a bore 8| formed in the enlarged housing 65. An anchor ring 82 is disposed in the bore 8| next to the tension adjusting ring 80 and is xed to the housing 65 as by bolts 83, 83. Within the anchor ring is fitted a radially extending anchor disc 85 having a plurality of notches 86, 86 in its periphery, interfitted with lugs 81, 81 formed integrally with the anchor ring 82.

As will be seen from Figure 5, the inner periphery of the anchor ring 82 terminates adjacent the hub of the backing ring 40 and retains thereagainst on annular sealing member 88. The anchor disc 85 has a stop 90 xed thereon and projecting axially toward the adjacent tension adjusting ring 90 in position to register with an inwardly extending stop lug 9| on said ring when said stop and lug are moved into engagement with each other. Said adjusting ring also has two adjusting inwardly projecting bearing lugs 93 and 94 disposed at opposite sides of the stop lug 9|. These bearing lugs 93 and 94 support opposite ends of a threaded adjusting screw 95 in position so that said adjusting screw is disposed on a chord of approximately 45 degrees with respect to the drum, with said adjusting screw extending between the outer periphery of the driven hub member 4| and the stop lug 9| on the adjusting ring 80.

A bifurcated lug 95 is carried by the driven end plate 41 and projects radially from its hub 4| in position to engage a pair of pins 98, 90 on opposite sides of a block 99 threaded on the adjusting rod 95. I

A squared end |00 of the threaded rod 95 may be reached by a removable socket wrench |02 through an aperture |93 formed in the housing 65 when the latter aperture is in alignment with a socket |04 formed on the outer periphery of the adjusting ring 80. The parts are arranged so that the aperture |83 and the socket |04 will register with each other when the stop 90 on the anchor disc 85 is engaged at one side of the stop lug 9| of ring 80, as shown in Figures 6, 7 and 8. As will presently appear, the adjusting ring 80 is normally maintained in this angular relation to said anchor disc and drum, excepting under unusual operative conditions.

The adjusting screw 95 is employed to impart a preloaded tension to the driving spring l0 in the manner best illustrated in Figures 6, 'l and 8, as follows:

When the parts of the drum are originally assembled., the two end blocks 12 and 15 of the drive spring are connected to the end plates 41 and 58, respectively, in an unwound condition, in which case, the end blocks 12 and y15 may slightly overlap each other, with the ends of the spring approximately in longitudinal alignment with each other, as indicated in Figure 6. In this initial assembling position of the parts, the bifurcated lug 9B on the end plate 41 is arranged at an angle toward the right end of the screw 95, with the pins 98 on block 99 in the lug 96. The stop 90 on the anchor disc 85 is also engaged with the right-hand side of the stop lug 9| on the tension adjusting ring 80, all as seen in Figure 6. The socket |04 in bearing lug 94 of ring 80 is also in alignment with the aperture |03 in the housing 65 so that the socket wrench |02 can be applied to engage the squared head |02 for turning the adjusting screw 95.

In order to impose an initial tension or preload on the drive spring 10, the screw 95 may be rotated, to move the hub 4| with its flange 11 in a clockwise direction as indicated, for instance, in Figure 7, where the lug 90 is moved to a substantially vertical position. This adjustment is accomplished without disturbing the initial angular relation of the drum and the adjusting ring 80. This adjustment, however, causes movement of the end plate 41 to which the end block of spring '|0 is connected, in a direction to unwind the spring, thereby placing said spring under a predetermined degree of expansion, depending upon the amount of angular adjustment provided by the screw 95. In Figure 6, the angular adjustment referred to is approximately 221/2 degrees. With knowledge of the characteristics of the spring 10, therefore, the amount of preloading imposed on said spring can be determined with reasonable exactness by the amount of angular adjustment provided through the screw 95.

It will be understood that, while preloading the spring, the stop 90 on the anchor disc 85 will remain in engagement with the stop lug 9| under gradually increasing pressure, corresponding to the -amount of expansion of the spring 10. Although in the preferred arrangement herein described the drive spring 10 is actually preloaded by expanding or untwisting said spring from its normal unloaded condition, this preloading of the spring may, for convenience, be referred generally herein as placing the spring under tension.

Figure 8 shows a View similar to Figure '1 but in which the angular movement of adjustment and corresponding expansion of the spring 10 is increased to approximately 45 degrees from the initial position shown in Figure 6. For illustrative purposes, it may be assumed, therefore, with a 221/2-degree adjustment shown in Figure 7, the drive spring '|0 may be preloaded to approximately 250 pounds compression while, in

igure 8, the same spring is adjusted to 45 degrees to impose a preloading of approximately 500 pounds.

Accordingly, in the case of the degree of adjustment illustrated in Figure 7, it will be understood that, when the drum as a whole is driven through sprocket 25 in its normal counter-clockwise direction, as seen in the several figures, power from the sprocket 25 will be transmitted through the cup-shaped drive member 30 to the clutch discs 33, 33a carried thereby. As long as the clutch springs 48 are permitted to function without interference ,from the rocking arms 50, 50,

as shown in Figure 5, said clutch springs willy maintain the clutch rings 33, 33a in driving engagment with the clutch rings 34, 34a to com-- plete a driving connection through the clutch backing ring 40, hub member 4| and end flangeI 41 and the spring 10 to the drum 20.

It will be understood further that, in the event that the spring 10 is not preloaded, but the spring is in its initial unwound condition as illustrated, the drum will be subject to yielding movement relative to the driving mechanism as soon as any load is encountered sufficient to overcome the initial unloaded tension on the driving spring. On the other hand, when the spring is preloaded to any predetermined value, such as illustrated in Figures 1 and 8, the drum will not have any relative yielding movement, excepting when the load on the cable exceeds the preloaded tension on the drive spring'.

In the event that the load on the cable drum exceeds the preloaded value of the drive spring l0, the spring l0 will then begin to yield, but under constantly increasing compression, depending upon the excessive load imposed thereon. In such case, the stop will be moved in a counter-clockwise direction away from the stop lug 9| through an angle dependent upon the amount of expansion imposed on the drive spring. The stop 9G is short enough to pass the bearing lug 93 on the adjusting ring 80, as indicated in Figure 9. As soon as the excessive loadon the drum is relieved, however, the stop 90 will return to engagement with the stop lug 9| to maintain the spring under the same predetermined compression to which it is adjusted.

The rocking arms 50 and rollers 53 cooperate with the cam ring 54 to provide an automatic means for disconnecting the clutch from driving engagement with the spring whenever the pulling load on the drum exceeds a predetermined value which may be considered unsafe for the drive spring, cable or any parts operated by the latter. As shown in Figure 10, the cam ring 54 has a pair of interiorly raised cam surfaces |59 which are disposed in positions Within the drum 65 at points where the rollers 53 of rocking arms 50 will be rocked downwardly, as shown in Figure 11, so as to Withdraw the outer clutch disc 33 against the compression of the clutch plates 48. Such withdrawal of the outer clutch disc will automatically dsengage the driving connection to the drum as long as the overload is imposed on the drum. As soon as this overload is relieved, however, the clutch plates Will again become automatically engaged to continue the drive connection to the drum.

Referring now to the means for driving and controlling the drum 20, Figures 2 and 3 show one form of operative connection between the motor shaft |20a and the drive sprocket 25. This connection consists of a motor pinion 200 meshing with a gear 20|. The latter is mounted on the same shaft as a pinion 202 whichimeshes with the gear 203. Gear '203 drives a shaft The shaft ||1 carries a sliding clutch member |20 which is feathered thereon as by means of key Illa. The clutch member |29 has teeth IIS engaged with similar teeth ||8 on drive sprocket I6. For convenience in reference, the gear train from the pinion 200 to the gear 203, inclusive, isV

referred to generally by the numeral |2|. The chain ||5 connects the sprocket H6 to the sprocket 25 as shown in Fig. 2.

I also provide brake means for controlling the rotation of the drum 20 when desired. The brake` mechanism shown herein consists of la brake drum 125fixed on one end ofthe motor shaft |20a and .engaged by a brake band 21 operated by any suitable brake applying mechanism, herein vincluding a solenoid [27a acting through brake aaalying leverage means, indicated generally at The use and operation ofthe power Winch with its preloading mechanism may now be described in lits application to a loading conveyor in mines, as shown in Figure l.

To `similar power winches i5, l of the kind hereinabove described are disposed adjacent opposite side walls 16,16 of the mine, and cables 51, 51 will lead forwardly from the drums 20, 20 of said Winches about pulleys I 26 and are connected at 'their free ends to the forward portions |28, |28 of the swiveling loading section of the gathering conveyor. In conveyor installations of the kind shown herein, it is particularly advantageous to keep a uniform tension on the cables 51, 5T to hold the loading conveyor in proper angular position during loading operations. It will also be understood that the opposed tension on the cables 51, 51, connected as shown to opposite sides of the loading head, will be varied somewhat during the normal reciprocal operation of the loading head as a whole. Hence, it is particularly advantageous to permit yielding movement of the cables while maintaining substantially uniform opposed tension thereon.

My improved structure provides an especially simple and effective means of adjusting the winch drums so as to preload each of the drums at predetermined values, thereby making it possible to maintain substantially equal yielding tension on both cables, depending upon varying operating conditions. Each winch is also provided with automatic unclutching means, as heretofore described in detail, so as to protect the Winches, as well as the loading mechanism to which they are connected, against damage due to excessive loads which may be imposed upon them.

It will be observed that the automatic unclutching means, including the rocking arms 58 and roller 53 which engage the cam ring 54 will be operative to release the clutch regardless of Whether the dr-um is beingpositively driven lby the motor at any particularly instance, or the drive gearing is being held stationary by the brake applied to the motor shaft.

It will be observed that, while my improved form of Winches is particularly adapted for use with a conveyor loader of the kind herein described, the novel features of the winch will by no means be limited to such use but can be einployed advantageously in numerous other fields.

I claim as my invention:

1. In a winch, a winding drum, a driving means for said drum including a coaxial drive member and a drive spring normally permitting yieldable relative rotation of said drum and drive member, a spring loading member rotatably mounted on said drum and having stop means' cooperating with stop means carried by the drum, permitting limited angular movement of said spring loading member and said drum, said spring loading member having circumferentially adjustable means thereon connected to said drive member for preloading said spring when said stop means are in engagedlpo'sitio'n in one direction, but permitting relative 'yielding rotation of said drum `'relative to said drive meinberlin' the opposite direction when the load ion said drum exceeds 'the preloaded value imposed onsaid spring.

l2. 'A winch structure in accordance with claim 1, wherein the drive 'spring consists of 'a coil Spring vmounted coaxially within the drum, with one end in xed relation to said drum, and the other endxed to `van e'n'd plate rotatable Within said drum, and the circumferentially adjustable means includes 'a threaded `screw rotatably 'supported at opposite ends on the rotatable spring loading member and having a threaded nut adjustable 'therealo'ng lbyrotation of said screw for adjusting said end plate through a predetermined angle relative to said 'spring loading member.

3. vA winch structure in accordance with claim 2, wherein the spring loading member includes a ring rotatably supported Awithin said drum, and the periphery of said drum has an aperture therethrough aiording access to one end of said threaded screw for rotation thereof to various positions of adjustment, when said stop means are in the mutually engaged position.

4. In a winch, a winding drum, driving means for said drum including a coaxial drive member and a drive spring normally permitting yieldable relative rotation of said drum and drive member, a spring loading member rotatably mounted on said drum and having stop means cooperating with stop means carried by the drum, permitting limited angular movement of said spring loading member relative to said drum, said spring loading member having circumferentially adjustable means thereon connected to said drive member for preloading said spring when said stop means are in engaged position in one direction, but permitting relative yielding rotation of said drum relative to said drive member in the opposite direction when the load on said drum exceeds the preloaded value imposed on said spring, and a load limitclutch coaxial with said drive member normally adjustable to relieve driving torque on said drum when the load on said drum substantially exceeds the preloaded value imposed on the driving spring.

5. A winch structure in accordance with claim 4, wherein the load limit clutch comprises a multiple disc clutch assembly including clutch members with cooperating friction discs, spring means carried on one of said clutch members for normally maintaining said discs in engaged position, cam means ycarried bysaid drum, and rocking arms carried on one of said last-named clutch members and engageable with said cam means for disengaging said friction discs when said drum is rotated to a predetermined position of angular displacement relative to its drive member.

LOY D. HAGENBOOK.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,076,599 Miller Oct. 21, 1913 2,468,193 Goi Apr. 26, 1949

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